CN104153881B - The differential drive mechanism of internal combustion engine - Google Patents

The differential drive mechanism of internal combustion engine Download PDF

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Publication number
CN104153881B
CN104153881B CN201410376095.7A CN201410376095A CN104153881B CN 104153881 B CN104153881 B CN 104153881B CN 201410376095 A CN201410376095 A CN 201410376095A CN 104153881 B CN104153881 B CN 104153881B
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gear
shaft
tooth
partial
piston
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CN201410376095.7A
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CN104153881A (en
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熊薇
唐仁杰
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熊薇
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Abstract

The invention discloses the differential drive mechanism of a kind of internal combustion engine, piston connects the pitman shaft of the first tooth bar by piston pin, and the spur gear of the first switching gear shaft and the helical rack of the first tooth bar engage;And first the incomplete umbrella tooth of sector gear and the first partial gear of switching gear shaft engage;The straight-tooth of the first partial gear inner circumferential and the engagement of two first planet gears;Central gear is loaded between two first planet gears and engages, and output gear engages with shaft end gear, and oval gear B engages with the oval gear A of the first row carrier gear.The present invention can significantly reduce engine consumption, improves fuel economy, improves engine exhaust emission.The scavenging efficiency of electromotor can be improved, improve the limit speed of electromotor, thus the power to weight ratio of electromotor is greatly improved;The smoothness of operation of electromotor can be improved, reduce engine luggine and noise, increasing service life of engine.

Description

The differential drive mechanism of internal combustion engine

Technical field

The present invention relates to IC engine transmission system technical field, particularly to the differential drive mechanism of internal combustion engine.

Background technology

Internal combustion engine mainly includes fuel feed system, ignition system, cooling system, lubricating system, drive system etc..In Hyundai Motor, shipping and various power-equipment, the internal combustion engine of crankshaft connecting rod type drive system is used the most extensive.Since application in 1898 Christian eras existing over one hundred year history so far.Its basic operation principle does not become, it is simply that the gases at high pressure that piston is burnt in cylinder promote and move up and down, and is rotated by connecting rod band dynamic crankshaft.Piston from top dead centre to lower dead center (or bent axle rotation turnback) is called a stroke.Quartastroke engine includes following work process: intake stroke, compression stroke, power stroke, exhaust stroke.

For the internal combustion engine of existing crankshaft connecting rod type drive system, engine power output is that the crankshaft connecting rod type drive system by piston, connecting rod and bent axle triplicity completes.This internal combustion engine mainly has the disadvantage that

1, in igniting work done in an instant, the gas blow-through power in cylinder is rapidly reached maximum, owing to piston is near top dead center, the pressure that now bearing portion of bent axle bears is maximum, frictional resistance is maximum, and thus the mechanical power of loss is also big, reduces the service life of crankshaft bearing simultaneously.

2, when the gas blow-through power in cylinder reaches near maximum, owing to piston is near top dead center, now the power output arm of force of crankshaft connecting rod system is little, gaseous-pressure in cylinder can not be fully converted into merit output, thus significantly reducing the heat energy-mechanical power conversion efficiency of internal combustion engine, have impact on the power per liter of internal combustion engine and oil consumption performance.

3, crankshaft connecting rod system is not axial symmetry parts, and the vibration caused by crankshaft connecting rod system in internal combustion engine operation process is big, noise is big;Crankshaft connecting rod system has much difficulty in healing weighing apparatus, and its manufacturing process is more complicated, and cost is high;In use, piston, crankshaft connecting rod system etc. are easy to wear, and maintenance cost is high;The internal combustion engine limit speed adopting crankshaft-link rod is low, seriously constrains the raising of electromotor power to weight ratio.

4, in adopting the operation process of internal combustion engine of four-stroke crankshaft connecting rod type drive system, piston is in a kind of reciprocating motion state all the time, during air inlet, piston quickly enters again compression travel in lower dead center moment, thus there is no the more fresh mixed oil gas of more time inspiration when cylinder body volume is maximum, during aerofluxus, piston quickly enters again suction stroke to top dead centre moment, so that not having the more time to allow waste gas farthest discharge time volume of cylinder is minimum, these situations finally all affect more fresh mixed oil gas and enter cylinder, thus causing that engine breathing efficiency is low, the raising making engine power is subject to certain restrictions.For two-stroke internal-combustion engine, its inlet and outlet all carry out at lower, but there is also same problem.

5, in the cylinder of internal-combustion engine of crankshaft connecting rod type drive system, gaseous mixture is maximum at pressure, volume is minimum, burning time is short, and piston is now descending, makes incomplete combustion, and exhaust gas concentration is high, and work doing efficiency is low.The internal combustion engine of existing crankshaft connecting rod type drive system is in order to improve engine performance, before upper dead canter advanced ignition in various degree or oil spout is all arrived at piston, in order that allow gaseous mixture burn faster when combustion chamber volume is minimum, more complete, it is thus possible to obtain bigger power output, and reduce the discharge exhaust gas concentration of electromotor, but do so also creates certain negative interaction: because of advanced ignition, in-cylinder pressure sharply raises, block piston stroking upward, add compression negative work, and be prone to cause combustion knock phenomenon.This contradiction exists all the time in the internal combustion engine of existing crankshaft connecting rod type drive system.

6, in the internal combustion engine operation process of crankshaft connecting rod type drive system, the connecting rod force direction periodically-varied to piston, and when engine power output is maximum, the active force of piston is also reached near maximum by connecting rod along cylinder wall surface normal direction, thus cause the frictional power loss between piston and cylinder very big, and the damage being easily caused between piston and cylinder surface and causing because of friction.

Another kind is referred to as the internal combustion engine of triangle rotor type electromotor and also obtain relatively broad application.The drive system of triangle rotor type electromotor adopts gear drive, and drive mechanism axial symmetry is better, and Engine Limit rotating speed is high, and power is outstanding compared with the internal combustion engine of crankshaft connecting rod type drive system with weight ratio, but there is also very big deficiency.Such as cylinder combustion burning is insufficient, oil consumption is excessive, and output shaft torque is too small, cylinder seal difficulty etc..Because the bulbs of pressure that rotary polygonal piston engine cylinder combustion gas acts on rotor side surface are divided into two power, try hard to recommend dynamic output shaft for one and rotate, and another power points to output shaft center, thus causing that the output moment of torsion of complete machine is too small;Make combustion rate too low because its cylinder is long and narrow, excessive oil consumption;Because using the cylinder of special shape, result in cylinder processing and manufacturing and difficulty that cylinder seal manufactures and designs.The problems that above-mentioned triangle rotor type electromotor exists, cause that it is difficult to promote the use of on a large scale.

The problems that internal combustion engine in order to solve crankshaft connecting rod type drive system exists, Chinese patent " has the internal combustion engine of opposed pistons ", and (publication number: CN1074083C) have employed multi-blade cam drive system to replace the crankshaft connecting rod type drive system of crankshaft connecting rod type drive system internal combustion engine, so that adopt the internal combustion engine of this multi-blade cam drive system significantly to relax the friction between piston and cylinder, and there is comparatively compact structure, but this patent yet suffers from " 1, in igniting work done in an instant, gas blow-through power in cylinder is rapidly reached maximum, owing to piston is near top dead center, the pressure that now bearing portion of bent axle bears is maximum, frictional resistance is maximum, thus the mechanical power of loss is also big, reduce the service life of crankshaft bearing simultaneously;2, when the gas blow-through power in cylinder reaches near maximum, owing to piston is near top dead center, now the power output arm of force of crankshaft connecting rod system is little, gaseous-pressure in cylinder can not be fully converted into merit output, thus significantly reducing the heat energy-mechanical power conversion efficiency of internal combustion engine, have impact on the power per liter of internal combustion engine and oil consumption performance." etc. problem.

Summary of the invention

It is an object of the invention to provide a kind of differential drive mechanism that can be applicable to internal combustion engine, adopt differential gearing form to realize the power output of internal combustion engine, can significantly reduce engine consumption, improve fuel economy, improve engine exhaust emission;The scavenging efficiency of electromotor can be improved, improve the limit speed of electromotor, thus the power to weight ratio of electromotor is greatly improved;The smoothness of operation of electromotor can be improved, reduce engine luggine and noise, increasing service life of engine.

The present invention takes techniques below scheme to realize above-mentioned purpose, first technical scheme of the present invention: the differential drive mechanism of internal combustion engine, including piston, piston pin and the first tooth bar, it is characterized in that, one end of first tooth bar is pitman shaft and the centre bore with piston matches, pitman shaft is provided with the through hole mated with piston pin, and the both sides of the other end are provided with helical rack;Piston connects the pitman shaft of the first tooth bar by piston pin, and the first switching gear shaft is formed by spur gear and sector gear tandem compound, and the spur gear of the first switching gear shaft and the helical rack of the first tooth bar engage;First partial gear is pot peviform, and it is provided centrally with axis hole, and periphery is incomplete umbrella tooth, and inner circumferential is provided with straight-tooth;First switching gear shaft is spaced substantially equidistant around the first partial gear periphery, and the incomplete umbrella tooth engagement of the sector gear of the first switching gear shaft and the first partial gear;One end of the first row carrier gear is oval gear A, and the other end is support, and support is in " Π " shape and is symmetrically arranged with planetary gear axle, is provided with axis hole, the planetary gear axle of support is separately installed with first planet gear in support;The straight-tooth of the first partial gear inner circumferential and the engagement of two first planet gears;One end of first sun gear shaft is equipped with central gear, the other end is equipped with shaft end gear, first sun gear shaft is threaded onto in the axis hole of support and the first partial gear, and central gear is loaded between two first planet gears and engages, output gear shaft is provided with oval gear B and output gear, output gear engages with shaft end gear, and oval gear B engages with the oval gear A of the first row carrier gear.

The reticule angle of described first tooth bar both sides helical rack tooth top is 90 °.

Continuous umbrella tooth and the radial symmetric that incomplete umbrella tooth is the numbers of teeth such as multistage of described partial gear, every section of continuous umbrella tooth engages with the first sector gear transferring gear shaft successively, and the half of the number that hop count is the first switching gear shaft of the incomplete umbrella tooth of partial gear.

Described first planet gear is parallel with the axis of rotation of the first sun gear shaft.

Second technical scheme of the present invention: the differential drive mechanism of internal combustion engine, including piston, piston pin and the second tooth bar, one end of second tooth bar is connecting rod and the centre bore with piston matches, connecting rod is provided with the through hole mated with piston pin, and the other end lateral symmetry of the second tooth bar is provided with spur rack and corresponding parallel;Piston connects the connecting rod of the second tooth bar by piston pin, second switching gear shaft is provided with coordination gear and driving gear, coordination gear engagement on the spur rack of the second tooth bar and the second switching gear shaft, the second switching gear shaft is spaced substantially equidistant around the second partial gear periphery;Second partial gear be provided centrally with axis hole, the periphery of the second partial gear is provided with incomplete straight-tooth, and inner circumferential is provided with straight-tooth;Driving gear and the incomplete straight-tooth of the second partial gear periphery on second switching gear shaft engage;One end of the first row carrier gear is oval gear A, and the other end is support, and support is in " Π " shape and is symmetrically arranged with planetary gear axle, is provided with axis hole, the planetary gear axle of support is separately installed with first planet gear in support;The straight-tooth of the second partial gear inner circumferential and the engagement of two first planet gears;One end of first sun gear shaft is equipped with central gear, the other end is equipped with shaft end gear, first sun gear shaft is threaded onto in the axis hole of support and the second partial gear, and central gear is installed between two first planet gears and engages, output gear shaft is provided with oval gear B and output gear, output gear shaft engages with shaft end gear, and oval gear B engages with the oval gear A of the first row carrier gear.

The continuous straight-tooth that incomplete straight-tooth is the numbers of teeth such as multistage of described partial gear and radial symmetric, every section of continuous straight-tooth engages with the second driving gear transferring gear shaft successively, and the half of the number that the hop count of the incomplete straight-tooth of partial gear is the second switching gear shaft.

Described first planet gear is parallel with the axis of rotation of the first sun gear shaft.

3rd technical scheme of the present invention: the differential drive mechanism of internal combustion engine, including piston, piston pin and the second tooth bar, one end of second tooth bar is connecting rod and the centre bore with piston matches, connecting rod is provided with the through hole mated with piston pin, and the other end lateral symmetry of the second tooth bar is provided with spur rack and corresponding parallel;Piston connects the connecting rod of the second tooth bar by piston pin, second switching gear shaft is provided with coordination gear and driving gear, coordination gear engagement on the spur rack of the second tooth bar and the second switching gear shaft, the second switching gear shaft is spaced substantially equidistant around the 3rd partial gear periphery;3rd partial gear be provided centrally with axis hole, the periphery of the 3rd partial gear is coaxially set side by side with incomplete straight-tooth and bevel gear;Driving gear and the incomplete straight-tooth of the 3rd partial gear on second switching gear shaft engage;Central shaft one end of second planet carrier gear is provided with A gear, and the other end is provided with the second planetary gear axle of the central axis with A gear, and the two ends of the second planetary gear axle are provided with the second planetary gear;Second sun gear shaft is constituted by spur gear and bevel gear coaxially arranged side by side and is provided centrally with axis hole, the central shaft of A gear is threaded onto in the axis hole of the 3rd partial gear and the second sun gear shaft, and the bevel gear of the 3rd partial gear and the bevel gear of the second sun gear shaft engage each other connection by the second planetary gear;Being provided with oval gear B and output gear on output gear shaft, the spur gear of the second sun gear shaft engages with the output gear of output gear shaft, and the oval gear B of output gear shaft and the A gear of the second planet carrier gear engage.

The continuous straight-tooth that incomplete straight-tooth is the numbers of teeth such as multistage of described 3rd partial gear and radial symmetric, every section of continuous straight-tooth engages with the second driving gear transferring gear shaft successively, and the half of the number that the hop count of the incomplete straight-tooth of partial gear is the second switching gear shaft.

Described second planetary gear is vertical with the axis of rotation of the second sun gear shaft.

Three technical schemes of summary, tooth bar is affixed on piston by piston pin, makees as a whole along the reciprocating motion of cylinder-bore axis direction.By rack and pinion engagement transmission between switching gear shaft and tooth bar, it is achieved the power between multiple tooth bars is transmitted and motor coordination.The incomplete gear teeth of partial gear (being incomplete umbrella tooth in the first technical scheme, second and the 3rd is incomplete straight-tooth in technical scheme), the circumference for the continuous gear teeth of the numbers of teeth such as some sections is uniformly distributed.The continuous gear teeth of every section of partial gear successively with switching gear shaft engaged transmission, it is achieved cylinder combustion gas to the work done of piston institute by tooth bar to partial gear export.The complete gear teeth of partial gear, with planetary gear engaged transmission.Planetary gear and sun gear shaft engaged transmission.Output gear shaft and sun gear shaft by circular gear engaged transmission, simultaneously output gear shaft with and planet carrier gear by oval gear engaged transmission, the rotation of partial gear, planet carrier gear, sun gear shaft coaxial line.Thus, a kind of differential gear transmissions relation is constituted between partial gear and output gear shaft, thus realizing piston merit from partial gear to the output of output gear shaft.

Piston and tooth bar are fixedly connected into a black box by piston pin;Also can cancel piston pin, directly piston be shaped with tooth bar overall processing manufacture.

Difference according to relative space relation, between the axis of rotation of switching gear shaft adjacent between two, angle can be 90 ° (such as first technical schemes), can also be 0 ° (as second and the 3rd technical scheme), correspondingly, the both sides flank profil tooth top reticule angle β of tooth bar is 90 ° or 0 °.

Planetary gear and the axis of rotation of sun gear shaft can parallel (such as the first and second technical schemes), constitute the plane differential gear train that planetary gear axis is parallel with centre wheel axis;The axis of rotation of planetary gear and sun gear shaft also can intersect vertically (such as the 3rd technical scheme), constitutes the space differential gear train that planetary gear axis intersects vertically with centre wheel axis.

A kind of differential drive mechanism that can be applicable to internal combustion engine provided by the present invention, adopts differential gearing form to realize the power output of internal combustion engine, has following beneficial effect:

1, can significantly reduce engine consumption, improve fuel economy, improve engine exhaust emission.

2, the scavenging efficiency of electromotor can be improved, improve the limit speed of electromotor, thus the power to weight ratio of electromotor is greatly improved.

3, the smoothness of operation of electromotor can be improved, reduce engine luggine and noise, increasing service life of engine.

4, engine structure relative compact, compared with the internal combustion engine of existing crankshaft connecting rod type drive system, the drive mechanism that the present invention uses is all gear drive so that engine structure relative compact.

5, owing to the drive system of the internal combustion engine just for crankshaft connecting rod type drive system carries out technological innovation, the internal combustion engine of existing main flow I. C. engine crankshaft link-type drive system other technologies except drive system still can be used, it is thus achieved that the maximum possible of existing internal-combustion engine technology is inherited.

6, engine power output is steadily.

Accompanying drawing explanation

Fig. 1 is the perspective view of the present invention the first technical scheme.

Fig. 2 is the perspective view of piston and the first rack combination in the present invention the first technical scheme.

Fig. 3 is the first rack shaft direction view in the present invention the first technical scheme.

Fig. 4 is the three-dimensional view of the first switching gear shaft in the present invention the first technical scheme.

Fig. 5 is the three-dimensional view of the first partial gear in the present invention the first technical scheme.

Fig. 6 is the A direction view of the first partial gear in Fig. 5.

Fig. 7 is the stereochemical structure view of first planet gear in the present invention the first technical scheme.

Fig. 8 is the perspective view of the first row carrier gear in the present invention the first technical scheme.

Fig. 9 is the perspective view of the first sun gear shaft in the present invention the first technical scheme.

Figure 10 is the perspective view of output gear shaft in the present invention the first technical scheme.

Figure 11 is the B direction view of output gear shaft in Figure 10.

Figure 12 is the perspective view of the present invention the second technical scheme.

Figure 13 is the perspective view of the second tooth bar in the present invention the second technical scheme.

Figure 14 is the perspective view of piston and the second rack combination in the present invention the second technical scheme.

Figure 15 is the perspective view of the second switching gear shaft in the present invention the second technical scheme.

Figure 16 is the three-dimensional view of the second partial gear in the present invention the second technical scheme.

Figure 17 is the perspective view of the present invention the 3rd technical scheme.

Figure 18 is the three-dimensional view of the 3rd partial gear in the present invention the 3rd technical scheme.

Figure 19 is the second planetary three-dimensional view in the present invention the 3rd technical scheme.

Figure 20 is the three-dimensional view of the second sun gear shaft in the present invention the 3rd technical scheme.

Figure 21 is the perspective view of the second planet carrier gear in the present invention the 3rd technical scheme.

Figure 22 is the C direction view of the second planet carrier gear in Figure 21.

Figure 23 is cylinder numbers schematic diagram in the embodiment of the present invention 1.

Figure 24 is cylinder numbers schematic diagram in the embodiment of the present invention 2.

Figure 25 is planet carrier gear to the instantaneous transmission ratio schematic diagram of output gear shaft the rotational angle of even rotating speed output gear shaft (abscissa be).

Figure 26 is the internal combustion engine movement velocity performance diagram rotational angle of even rotating speed output shaft (abscissa be) of crankshaft connecting rod type drive system.

Figure 27 is partial gear to the instantaneous transmission ratio schematic diagram of output gear shaft the rotational angle of even rotating speed output gear shaft (abscissa be).

In figure: 1. piston, 2. piston pin, 3. the first tooth bar, 3a. the second tooth bar, 4. the first switching gear shaft, 41. spur gear, 42. bevel gear, 4a. second transfers gear shaft, 4a1. coordinates gear, 4a2. driving gear, 5. the first partial gear, 5a. the second partial gear, 5b. the 3rd partial gear, 6. first planet gear, 6a. the second planetary gear, 7. the first row carrier gear, 71. oval gear A, 72. support, 721. planetary gear axle, 7a. the second planet carrier gear, 7a1. the second planetary gear axle, 7a2.A gear, 8. the first sun gear shaft, 81. central gear, 82. shaft end gear, 8a. the second sun gear shaft, 9. output gear shaft, 91. oval gear B, 92. output gear, β. reticule angle, α. central angle.

Detailed description of the invention

Below in conjunction with drawings and Examples, the present invention is described further.First technical scheme of the present invention: referring to Fig. 1 to Figure 11, the differential drive mechanism of internal combustion engine, including piston 1, piston pin 2 and the first tooth bar 3, one end of first tooth bar 3 is pitman shaft 31 and the centre bore with piston 1 matches, pitman shaft 31 is provided with the through hole mated with piston pin 2, and the both sides of the other end of the first tooth bar 3 are provided with helical rack 32;Piston 1 connects the pitman shaft 31 of the first tooth bar 3 by piston pin 2, and the first switching gear shaft 4 is formed by spur gear 41 and sector gear 42 tandem compound, and the spur gear 41 of the first switching gear shaft 4 engages with the helical rack 32 of the first tooth bar 3;First partial gear 5 is in pot peviform, and it is provided centrally with axis hole, and periphery is incomplete umbrella tooth, and inner circumferential is provided with straight-tooth;First switching gear shaft 4 is spaced substantially equidistant around the first partial gear 5 periphery, and the sector gear 42 of the first switching gear shaft 4 engages with the incomplete umbrella tooth of the first partial gear 5;One end of the first row carrier gear 7 is oval gear A71, and the other end is support 72, and support 72 is in " Π " shape and is symmetrically arranged with planetary gear axle 721, is provided with axis hole, the planetary gear axle 721 of support 72 is separately installed with first planet gear 6 in support 72;Straight-tooth and the two first planet gears 6 of the first partial gear 5 inner circumferential engage;One end of first sun gear shaft 8 is equipped with central gear 81, the other end is equipped with shaft end gear 82, first sun gear shaft 8 is threaded onto in the axis hole of support 72 and the first partial gear 5, and central gear 81 is loaded between two first planet gears 6 and engages, output gear shaft 9 is provided with oval gear B91 and output gear 92, output gear 92 engages with shaft end gear 82, and oval gear B91 engages with the oval gear A71 of the first row carrier gear 7.

The reticule angle β of described first tooth bar 3 both sides helical rack 32 tooth top is 90 °.

Continuous umbrella tooth and the radial symmetric that incomplete umbrella tooth is the numbers of teeth such as multistage of described partial gear 5, every section of continuous umbrella tooth engages with the first sector gear 42 transferring gear shaft 4 successively, and the half of the number that hop count is the first switching gear shaft 4 of the incomplete umbrella tooth of partial gear 5.

Described first planet gear 6 is parallel with the axis of rotation of the first sun gear shaft 8.

Piston 1 and the first tooth bar 3 can be a monolithic molding structure.

Second technical scheme of the present invention: referring to Figure 12 to Figure 16, the differential drive mechanism of internal combustion engine, including piston 1, piston pin 2 and the second tooth bar 3a, one end of second tooth bar 3a is connecting rod and the centre bore with piston 1 matches, connecting rod is provided with the through hole mated with piston pin 2, and the other end lateral symmetry of the second tooth bar 3a is provided with spur rack and corresponding parallel;Piston 1 connects the connecting rod of the second tooth bar 3a by piston pin 2, second switching gear shaft 4a is provided with coordination gear 4a1 and driving gear 4a2, coordination gear 4a1 engagement on the spur rack of the second tooth bar 3a and the second switching gear shaft 4a, the second switching gear shaft 4a is spaced substantially equidistant around the second partial gear 5a periphery;Second partial gear 5a is provided centrally with axis hole, and the periphery of the second partial gear 5a is provided with incomplete straight-tooth, and inner circumferential is provided with straight-tooth;Driving gear 4a2 and the incomplete straight-tooth of the second partial gear 5a periphery on second switching gear shaft 4a engage;One end of the first row carrier gear 7 is oval gear A71, and the other end is support 72, and support 72 is in " Π " shape and is symmetrically arranged with planetary gear axle 721, is provided with axis hole, the planetary gear axle 721 of support 72 is separately installed with first planet gear 6 in support 72;Straight-tooth and the two first planet gears 6 of the second partial gear 5a inner circumferential engage;One end of first sun gear shaft 8 is equipped with central gear 81, the other end is equipped with shaft end gear 82, first sun gear shaft 8 is threaded onto in the axis hole of support 72 and the second partial gear 5a, and central gear 81 is installed between two first planet gears 6 and engages, output gear shaft 9 is provided with oval gear B91 and output gear 92, output gear 92 engages with shaft end gear 82, and oval gear B91 engages with the oval gear A71 of the first row carrier gear 7.

The continuous straight-tooth that incomplete straight-tooth is the numbers of teeth such as multistage of described partial gear 5 and radial symmetric, every section of continuous straight-tooth engages with the second driving gear 4a2 transferring gear shaft 4a successively, and the half of the number that the hop count of the incomplete straight-tooth of partial gear 5 is the second switching gear shaft 4a.

Described first planet gear 6 is parallel with the axis of rotation of the first sun gear shaft 8.

Piston 1 and the second tooth bar 3a can be a monolithic molding structure.

3rd technical scheme of the present invention: referring to Figure 17 to Figure 22, the differential drive mechanism of internal combustion engine, including piston 1, piston pin 2 and the second tooth bar 3a, one end of second tooth bar 3a is connecting rod and the centre bore with piston 1 matches, connecting rod is provided with the through hole mated with piston pin 2, and the other end lateral symmetry of the second tooth bar 3a is provided with spur rack and corresponding parallel;Piston 1 connects the connecting rod of the second tooth bar 3a by piston pin 2, second switching gear shaft 4a is provided with coordination gear 4a1 and driving gear 4a2, coordination gear 4a1 engagement on the spur rack of the second tooth bar 3a and the second switching gear shaft 4a, the second switching gear shaft 4a is spaced substantially equidistant around the 3rd partial gear 5b periphery;3rd partial gear 5b is provided centrally with axis hole, and the periphery of the 3rd partial gear 5b is coaxially set side by side with incomplete straight-tooth and bevel gear;The incomplete straight-tooth engagement of driving gear 4a2 and the three partial gear 5b on the second switching gear shaft 4a;Central shaft one end of second planet carrier gear 7a is provided with A gear 7a2, and the other end is provided with the second planetary gear axle 7a1 of the central axis with A gear 7a2, and the two ends of the second planetary gear axle 7a1 are provided with the second planetary gear 6a;Second sun gear shaft 8a is constituted by spur gear and bevel gear coaxially arranged side by side and is provided centrally with axis hole, the central shaft of A gear 7a2 is threaded onto in the axis hole of the 3rd partial gear 5b and the second sun gear shaft 8a, and the bevel gear of the 3rd partial gear 5b and the bevel gear of the second sun gear shaft 8a engage each other connection by the second planetary gear 6a;Being provided with oval gear B91 and output gear 92 on output gear shaft 9, the spur gear of the second sun gear shaft 8a engages with the output gear 92 of output gear shaft 9, the A gear 7a2 engagement of the oval gear B91 and the second planet carrier gear 7a of output gear shaft 9.

The continuous straight-tooth that incomplete straight-tooth is the numbers of teeth such as multistage of described 3rd partial gear 5b and radial symmetric, every section of continuous straight-tooth engages with the second driving gear 4a2 transferring gear shaft 4a successively, and the half of the number that the hop count of the incomplete straight-tooth of partial gear 5b is the second switching gear shaft 4a.

Described second planetary gear 6a is vertical with the axis of rotation of the second sun gear shaft 8a.

Piston 1 and the second tooth bar 3a can be a monolithic molding structure.

Embodiment 1:First technical scheme of the present invention, referring to Fig. 1 to Figure 11.The differential drive mechanism of internal combustion engine, including piston 1, piston pin the 2, first tooth bar the 3, first switching gear shaft the 4, first partial gear 5, first planet gear 6, the first row carrier gear the 7, first sun gear shaft 8 and output gear shaft 9.

Internal combustion engine adopts four stroke operation modes, and total cylinder A, cylinder B, cylinder C and tetra-cylinders of cylinder D, cylinder-bore axis is parallel to each other, and the circumferentially equidistant distribution of cylinder-bore axis.In internal combustion engine operation process, each cylinder is sequentially carried out air-breathing in the direction of the clock, compression, work done, exhaust stroke.In each cylinder, the first tooth bar 3 is affixed on piston 1 by piston pin 2, makees as a whole along the reciprocating motion of cylinder-bore axis direction, and the first tooth bar 3 has two straight-sided flanks, and becomes 90 degree of angles between two straight-sided flanks.Realized power transmission and motor coordination by the first engaged transmission effect transferring gear shaft 4 between each two the first tooth bar 3, first tooth bar 3 one has four, correspondingly, first switching gear shaft 4 also one has four, the mutual alignment relation of the first tooth bar 3 and the first switching gear shaft 4 is (as shown in Figure 23): when cylinder A starts intake stroke, cylinder A inner carrier 1 starts from top dead centre descending, starting compression stroke with the cylinder B of cylinder A clockwise adjacent, the piston 1 in cylinder B starts from lower dead center up.In like manner, power stroke is started with the cylinder D of cylinder B clockwise adjacent, cylinder D inner carrier 1 starts descending from top dead centre, exhaust stroke is started with the cylinder C of cylinder D clockwise adjacent, cylinder C inner carrier 1 starts up from lower dead center, the first such alternate cycles of tooth bar 3 that each cylinder is corresponding moves back and forth, and by the engaged transmission effect of the first switching gear shaft 4 between each first tooth bar 3, it is achieved motor coordination and power between the first tooth bar 3 are transmitted.

Owing to the first gear shaft 4 one of transferring has four and uniform, therefore, the incomplete gear teeth of the first partial gear 5, be two sections about quarter turn bore the circumference of tooth continuously and be uniformly distributed, the central angle alpha that every section of continuous cone tooth is corresponding is 70 °~90 °.When certain cylinder enters power stroke, piston starts descending from top dead centre, drive the first switching gear shaft 4(of corresponding first tooth bar 3 correspondence clockwise), the about quarter turn that this first switching gear shaft 4 initially enters with the first partial gear 5 bores engaging of tooth continuously, piston merit starts export the first partial gear 5 and drive the rotating speed of the first partial gear 5 to start from scratch acceleration, it is achieved the output of piston merit.When this cylinder power stroke proceeds to about half, corresponding first switching gear shaft 4 drives the first partial gear 5 to accelerate to maximum (top) speed.Afterwards, work done cylinder this first switching gear shaft 4 corresponding is still driving the first partial gear 5, but next cylinder (clockwise) compression stroke required horsepower increases, therefore the first partial gear 5 reduces speed now, and terminate at this cylinder power stroke, when piston 1 arrives lower dead center, the rotating speed of the first partial gear 5 is also reduced to zero.The first switching gear shaft 4 that this cylinder is corresponding exits and the engaged transmission of the first partial gear 5, next cylinder power stroke starts, the first switching gear shaft 4 that next cylinder is corresponding initially enters and the engaging of the first partial gear 5, first partial gear 5 starts again the one direction speed ripple process of zero-turn speed-acceleration-maximum speed-deceleration-zero-turn speed of a new round, thus starting new piston merit output procedure.

The complete gear teeth on first partial gear 5, for complete Cylinder Gear, and with incomplete gear teeth coaxial line.In the speed ripple process of the first partial gear 5, its complete gear teeth all the time with planetary gear 6 engaged transmission.Planetary gear 6 is parallel with the axis of rotation of sun gear shaft 8, constitutes the plane differential gear train that planetary gear axis is parallel with centre wheel axis.

The pulsation rotating speed of the first partial gear 5 and the uniform rotation transformational relation of output gear shaft 9, adopt reverse thinking mode, from the at the uniform velocity rotating speed of output gear shaft 9 to the pulsation rotating speed transformational analysis of the first partial gear 5, it is easier to understand.Assume output gear shaft 9 has rotating speed n0, inertia due to electromotor and load, it is believed that the rotating speed n0 on output gear shaft 9 is even rotating speed, it it is stable drive ratio transmission between sun gear shaft 8 and output gear shaft 9, it it is the variable ratio transmission (as shown in figure 25) of oval gear pair between planet carrier gear 7 and output gear shaft 9, then according to differential gear train gear ratio calculation method, can draw by sun gear shaft 8, planet carrier gear 7, planetary gear 6, in the plane differential gear train of the first composition such as partial gear 5 grade, first partial gear 5 gear ratio to sun gear shaft 8, it is thus possible to calculate first partial gear 5 gear ratio (as shown in figure 27) to output gear shaft 9.If the stable drive ratio taken between sun gear shaft 8 and output gear shaft 9 is 2:1, and take the pitch radius of planetary gear 6 and the complete gear teeth of the first partial gear 5 of corresponding engagement than for 1:4, then correspondingly the eccentricity of oval gear B91 is 0.2, can obtain under this parameter of structure design meet " output gear shaft 9 moves with uniform velocity, first partial gear 5 does pulsation and rotates (minimum speed is zero), and first first partial gear 5 corner (that is corresponding one stroke of piston) of corresponding 90 ° of each pulsation rotation period of partial gear 5 " etc. the plane differential gear train design result that requires, thus realizing piston 1 to move back and forth the motion conversion to output gear shaft 9 uniform rotation and merit output.

From above-mentioned conversed analysis process, the plane differential gear train being made up of sun gear shaft 8, planet carrier gear 7, planetary gear 6, partial gear 5 etc., introducing output gear shaft 9 with sun gear shaft 8 by circular gear engaged transmission, and output gear shaft 9 with and after planet carrier gear 7 passes through oval gear engaged transmission, the transmission degree of freedom of plane differential gear train is changed into 1 from 2, achieve the power transmission between sun gear shaft 8 and planet carrier gear 7 and motor coordination, it is achieved thereby that piston merit exports to the merit of output gear shaft 9 through partial gear 5.

Embodiment 2:Second technical scheme of the present invention, referring to Figure 12 to Figure 16, the present embodiment is a kind of differential drive mechanism that can be applicable to internal combustion engine, and its differential gearing system is made up of piston 1, piston pin the 2, second tooth bar 3a, the second switching gear shaft 4a, the second partial gear 5a, first planet gear 6, the first row carrier gear the 7, first sun gear shaft 8 and output gear shaft 9.

Internal combustion engine adopts four stroke operation modes, and total cylinder A ', cylinder B ', cylinder C ', tetra-cylinders of cylinder D ', cylinder-bore axis is parallel to each other, and the rectangular array distribution of cylinder-bore axis.In internal combustion engine operation process, each cylinder cylinder A ' shown in Figure 24, cylinder B ', cylinder C ', cylinder D ' number order are sequentially carried out air-breathing, compression, work done, exhaust stroke, illustrate, when cylinder A ' starts intake stroke, cylinder B ' starts compression stroke, cylinder C ' starts power stroke, and cylinder D ' starts exhaust stroke, when cylinder A ' starts compression stroke, cylinder B ' starts power stroke, cylinder C ' starts exhaust stroke, and cylinder D ' starts intake stroke, so circulates.

In each cylinder, the second tooth bar 3a is affixed on piston 1 by piston pin 2, makees as a whole along the reciprocating motion of cylinder-bore axis direction, and each second tooth bar 3a has two straight-sided flanks, and parallel between two straight-sided flanks.

By the engaged transmission effect of the second switching gear shaft 4a between each two the second tooth bar 3a, it is achieved power transmission and motor coordination.Cylinder has four, and correspondingly, the second tooth bar 3a also one has four.So that the axial symmetry of the second partial gear 5a is good, take the incomplete gear teeth of the second partial gear 5a be two sections and circumference uniform, then the second switching gear shaft 4a also one has four.The mutual alignment relation of the second tooth bar 3a and the second switching gear shaft 4a is: as shown in figure 24, when cylinder A ' starts intake stroke, cylinder A ' inner carrier 1 starts from top dead centre descending, and the cylinder B ' adjacent with cylinder A ' starts compression stroke, and the piston 1 in cylinder B ' starts from lower dead center up.In like manner, the cylinder C ' relative with cylinder B ' starts power stroke, cylinder C ' inner carrier 1 starts descending from top dead centre, the cylinder D ' adjacent with cylinder C ' starts exhaust stroke, cylinder D ' inner carrier 1 starts up from lower dead center, the second such alternate cycles of tooth bar 3a that each cylinder is corresponding moves back and forth, and by the engaged transmission effect of the second switching gear shaft 4a between each second tooth bar 3a, it is achieved motor coordination and power between the second tooth bar 3a are transmitted.The space layout mode of four second switching gear shaft 4a is: the axis of the second switching gear shaft 4a is parallel to each other and vertical with cylinder-bore axis non-intersect, the axis of four second switching gear shaft 4a becomes square vertices position array, and this foursquare diagonal is parallel with cylinder-bore axis.

The incomplete gear teeth of the second partial gear 5a, are that the circumference of two sections of about quarter turn continuous cylinder teeth is uniformly distributed, and the central angle alpha that every section of incomplete gear teeth are corresponding is 70 °~90 °.When (shown in Figure 24) cylinder A ' enters power stroke, piston 1 starts descending from top dead centre, the second switching gear shaft 4a in outside is directly driven by corresponding second tooth bar 3a, and indirectly drive the second switching gear shaft 4a outside another, the second switching gear shaft 4a in outside to initially enter engaging of 1/4 week incomplete gear teeth with the second partial gear 5a;Piston merit starts export the second partial gear 5a and drive the rotating speed of the second partial gear 5a to start from scratch acceleration, it is achieved the output of piston merit.When cylinder A ' power stroke proceeds to about half, corresponding two second switching gear shaft 4a drive the second partial gear 5a to accelerate to maximum (top) speed, afterwards, the corresponding second switching gear shaft 4a of cylinder A ' is still driving the second partial gear 5a, but cylinder B ' compression stroke required horsepower increases, therefore the second partial gear 5a reduces speed now, cylinder A ' power stroke terminates, when piston 1 arrives lower dead center, the rotating speed of the second partial gear 5a is also reduced to zero, then two switching the second gear shaft 4a that cylinder A ' drives exit and the engaged transmission of the second partial gear 5a, cylinder B ' starts power stroke, cylinder B ' drives two the second switching gear shaft 4a(of inner side parallel with cylinder-bore axis by the planes determined of axis of these two the second gear shaft 4a that transfer by corresponding second tooth bar 3a) initially enter and the engaging of the second partial gear 5a, second partial gear 5a starts again the one-sided speed ripple process of zero-turn speed-acceleration-maximum speed-deceleration-zero-turn speed of a new round, thus starting new piston merit output procedure.

The complete gear teeth on second partial gear 5a be complete Cylinder Gear and with incomplete gear teeth coaxial line.In the speed ripple process of the second partial gear 5a, its complete gear teeth all the time with first planet gear 6 engaged transmission.The pulsation rotating speed of the second partial gear 5a is identical with embodiment 1 with the uniform rotation transformational relation of output gear shaft 9, and this is repeated no more.

Embodiment 3:3rd technical scheme of the present invention, referring to Figure 17 to Figure 22.The present embodiment is a kind of differential drive mechanism that can be applicable to internal combustion engine, and its differential gearing system is made up of piston 1, piston pin the 2, second tooth bar 3a, the second switching gear shaft 4a, the 3rd partial gear 5b, the second planetary gear 6a, the second planet carrier gear 7a, the second sun gear shaft 8a, output gear shaft 9.

Internal combustion engine adopts four stroke operation modes, have four cylinders, as shown in figure 24, power transmission between the second tooth bar 3a in the space arrangement of cylinder, the stroke order of cylinder, each cylinder and motor coordination mode and piston merit are to the way of output etc. of the 3rd partial gear 5b, identical with embodiment 2.

The complete gear teeth on 3rd partial gear 5b be complete circular cone tooth and with the incomplete gear teeth coaxial line on the 3rd partial gear 5b.In the speed ripple process of the 3rd partial gear 5b, its complete gear teeth all the time with the second planetary gear 6a engaged transmission.The axis of rotation of the second planetary gear 6a and the second sun gear shaft 8a intersects vertically, and constitutes the space differential gear train that planetary gear axis intersects vertically with centre wheel axis.

The pulsation rotating speed of the 3rd partial gear 5b and the uniform rotation transformational relation of output gear shaft 9, adopt reverse thinking mode, from the at the uniform velocity rotating speed of output gear shaft 9 to the pulsation rotating speed transformational analysis of the 3rd partial gear 5b, it is easier to understand.

Assume output gear shaft 9 has at the uniform velocity rotating speed n0, it is stable drive ratio transmission between second sun gear shaft 8a and output gear shaft 9, it it is the variable ratio transmission (as shown in figure 25) of oval gear pair between second planet carrier gear 7a and output gear shaft 9, then according to differential gear train gear ratio calculation method, can draw by the second sun gear shaft 8a, second planet carrier gear 7a, second planetary gear 6a, in the space differential gear train of the 3rd partial gear 5b composition, the 3rd partial gear 5b gear ratio to the second sun gear shaft 8a, it is thus possible to calculate the 3rd partial gear 5b gear ratio (as shown in figure 27) to output gear shaft 9.When the stable drive ratio taken between the second sun gear shaft 8a and output gear shaft 9 is 3:2, then correspondingly the eccentricity of oval gear B91 is 1/7, under this parameter of structure design, energy acquisition is satisfied, and " output gear shaft 9 moves with uniform velocity, 3rd partial gear 5b does pulsation and rotates (minimum speed is zero), and the 3rd the 3rd partial gear 5b corner (that is corresponding one stroke of piston) of corresponding 90 degree of each pulsation rotation period of partial gear 5b " etc. the space differential gear train design result of requirement, thus realizing piston 1 to move back and forth the motion conversion to output gear shaft 9 uniform rotation and merit output.

From above-mentioned conversed analysis process, by the second sun gear shaft 8a, second planet carrier gear 7a, second planetary gear 6a, the space differential gear train of the composition such as the 3rd partial gear 5b, in the stable drive ratio engaged transmission introduced between output gear 92 and the second sun gear shaft 8a, and after the variable ratio engaged transmission between oval gear B91 and the second planet carrier gear 7a, the transmission degree of freedom of plane differential gear train is changed into one from two, achieve the power transmission between the second sun gear shaft 8a and the second planet carrier gear 7a and motor coordination, it is achieved thereby that piston merit exports to the merit of output gear shaft 9 through the 3rd partial gear 5b.

In sum, the key point of the present invention:

1, the differential drive mechanism of internal combustion engine is made up of piston 1, piston pin 2, tooth bar, switching gear shaft, partial gear, planetary gear, planet carrier gear, sun gear shaft and output gear shaft 9.

2, by piston pin 2, piston 1 and tooth bar can be fixedly connected into a black box;Also can cancel piston pin 2, directly piston 1 be shaped with tooth bar overall processing manufacture.

3, internal combustion engine can have one or more cylinder, and in each stroke of internal combustion engine, the assembly that piston 1, piston pin 2, tooth bar etc. are constituted is along cylinder-bore axis direction reciprocating translatory.

4, switching gear shaft realizes the motor coordination between the corresponding tooth bar of multiple cylinder and power transmission.

5, when certain cylinder is in power stroke, engaged transmission between the tooth bar corresponding by this cylinder and switching gear shaft, piston merit passes to partial gear, and drive the rotating speed of partial gear from the zero to maximum, again by being up to zero, the above consecutive variations of rotating speed single order of partial gear, completes a speed ripple cycle of partial gear.

7, sun gear shaft, planet carrier gear, planetary gear and partial gear form plane or space differential gear train, and engage stable drive ratio transmission at the output gear introduced between output gear shaft 9 and sun gear shaft, and output gear shaft 9 with and planet carrier gear between oval gear engage variable ratio transmission after, the transmission degree of freedom of plane differential gear train is changed into one from two, achieve the power transmission between sun gear shaft and planet carrier gear and motor coordination, it is achieved thereby that the pulsation of partial gear rotates the definitiveness transmission to output gear shaft uniform rotation, achieve piston merit through the partial gear output to output gear shaft 9.

The present invention has following advantageous application effect:

A) can significantly reduce engine consumption, improve fuel economy, improve engine exhaust emission.The present invention realizes this application effect mainly by following technological approaches:

First, as can be seen from Figure 27, compared with the internal combustion engine movement velocity characteristic of existing crankshaft connecting rod type drive system (as shown in figure 26), under the differential gearing mode that the present invention adopts, corresponding to output gear shaft 9(power output shaft) uniform rotation, piston is in the process close to up/down stop, and the velocity variations process that piston 1 linear velocity (is equivalent to the rotating speed of partial gear 5) and converges to gradually 0 is mild.That is, compression stroke at piston 1 is about at the end, the line of motion speed of the piston 1 of the present invention becomes very slow, and what this was beneficial in cylinder combustible oil gas mixture is sufficiently mixed, and provides combustible oil gas mixture in cylinder and fully burn the required time.It is thus possible to allow the ignition advance angle of electromotor to be greatly reduced, substantially reduce compression negative work, add the circulation merit of electromotor.And when the power stroke of piston arrives, also due to the line movement velocity of piston 1 is to start to be slowly increased from 0, in cylinder, the burning of combustible oil gas mixture is more abundant, reach with pressure peak in the cylinder of internal-combustion engine of existing crankshaft connecting rod type drive system required for fuel delivery less, thus engine consumption can be reduced, improve the toxic emission of electromotor simultaneously.

Secondly, according to relevant information, friction loss between piston 1 and cylinder wall in existing crankshaft connecting rod type internal combustion engine inner carrier reciprocatory movement, consume the 10%-20% of cycle of engine merit, in piston 1 power stroke of the present invention, piston 1 be subject to differential drive mechanism counteracting force direction can all the time with cylinder-bore axis conllinear, the more existing crankshaft connecting rod type internal combustion engine of friction loss of piston 1 and cylinder wall surface is greatly reduced, thus substantially reducing engine consumption, improve fuel economy.

Again, in the piston power stroke of the present invention, the power output arm of force line of piston 1 remains the pitch circle common tangent of the partial gear of tooth bar, the power output arm of force of piston 1 is constant, when cylinder pressure arrives near maximum, the block bearing of each driving member of electromotor does not have excessive pressure, and engine operation process consumption compares the little of existing crankshaft connecting rod type internal combustion engine at the frictional work on bearing etc., it is thus possible to reduction engine consumption, improve fuel economy.

Finally, in the piston power stroke of the present invention, the power output arm of force line of piston 1 remains the pitch circle common tangent of the partial gear 5 of tooth bar, the power output arm of force of piston 1 is constant, when cylinder pressure arrives near maximum, the power output arm of force of the piston 1 of the present invention exports big many of the arm of force than the power of the piston 1 of existing crankshaft connecting rod type internal combustion engine, gaseous-pressure in cylinder can be fully converted into merit output, substantially increase the heat energy-mechanical power conversion efficiency of the present invention, thus substantially reducing engine consumption, improve fuel economy.

B) scavenging efficiency of electromotor can be improved, improve the limit speed of electromotor, thus the power to weight ratio of electromotor is greatly improved.The present invention realizes this application effect mainly by following technological approaches:

First, compared with the internal combustion engine movement velocity characteristic of existing crankshaft connecting rod type drive system (as shown in figure 26), under the differential gearing mode that the present invention adopts, piston linear velocity converges to the velocity variations process mild (as shown in figure 27) of 0 gradually.When cylinder is in exhaust stroke at the end, it is abundant that present invention piston linear velocity slowly is beneficial to aerofluxus, and reduces exhaust process windage loss;When cylinder is in intake stroke at the end, present invention piston linear velocity slowly is also beneficial to suck more fresh oil gas mixture, and reduces breathing process windage loss.This is beneficial to improve engine breathing efficiency, also to the raising of engine thermal cycle efficiency gain to some extent, improves the power per liter of electromotor, it is thus possible to improve the power to weight ratio of electromotor.

Secondly, compared with the internal combustion engine of existing crankshaft connecting rod type drive system, the assembly that the present invention is constituted except piston and tooth bar etc. is except straight reciprocating motion, and other driving member is all axialy symmetric part, thus allowing electromotor to have higher limit speed;From the efficiency of combustion of electromotor, inventive piston linear velocity characteristic (as shown in figure 27), it will help electromotor is maintained to higher efficiency of combustion at high speed.Therefore, can pass through to improve the limit speed of inventive engine, power to weight ratio and the power per liter of electromotor are greatly improved.

C) smoothness of operation of electromotor can be improved, reduce engine luggine and noise, increasing service life of engine.The present invention realizes this application effect mainly by following technological approaches:

First, compared with the internal combustion engine of existing crankshaft connecting rod type drive system, the drive mechanism major part of the present invention is axialy symmetric part, remaining non-axisymmetric parts is also straight reciprocating motion form, substantially reduce various vibrations and noise that each parts of drive system cause due to mass unbalance, it is thus possible to significantly improve the smoothness of operation of electromotor, reduce the running noise level of electromotor, and the service life of electromotor can be extended.

Secondly, it is continuous that each drive disk assembly motor process of electromotor of the present invention is all more than speed single order, without rigid shock, also without soft impulse, it is thus possible to improve the smoothness of operation of electromotor, reduces engine luggine and noise, increasing service life of engine.

Again, in the piston power stroke of the present invention, the power output arm of force line of piston 1 remains the pitch circle common tangent of tooth bar and partial gear, the power output arm of force of piston 1 is constant, when cylinder pressure arrives near maximum, the impulsive force that the parts such as the block bearing of each driving member of electromotor does not have excessive pressure, engine bearing bear is little, long service life.

Finally, in the piston power stroke of the present invention, piston 1 be subject to differential drive mechanism counteracting force direction can all the time with cylinder-bore axis conllinear, thus the more existing crankshaft connecting rod type internal combustion engine of frictional force of piston 1 and cylinder wall surface greatly reduces, especially when cylinder pressure arrives near maximum, piston 1 greatly reduces with the more existing crankshaft connecting rod type internal combustion engine of frictional force of cylinder wall surface, thus the abrasion reduced between piston 1 and cylinder wall surface, extend the service life of electromotor.

D) the engine structure relative compact of the present invention.Compared with the internal combustion engine of existing crankshaft connecting rod type drive system, the drive mechanism that the present invention uses is all gear drive so that engine structure relative compact.

E) due to the fact that the drive system just for crankshaft connecting rod type internal combustion engine carries out technological innovation, existing main flow I. C. engine crankshaft connecting rod type internal-combustion engine other technologies except drive system still can be used, it is thus achieved that the maximum possible of existing internal-combustion engine technology is inherited.

F) the engine power output of the present invention is steadily.The present invention realizes this application effect mainly by following technological approaches:

First, from Figure 27, near power stroke initial stage cylinder pressure spikes of the present invention goes out now, corresponding piston line movement velocity is slow, engine power output instantaneous value is made to be unlikely to higher, and when compression stroke later stage cylinder pressure of the present invention is higher, piston line movement velocity is slow, and it is less that compression consumes power, and these are all conducive to the power maintaining output gear shaft (power output shaft) to export steadily and rotating speed is steady.

Secondly, the differential drive mechanism that the present invention adopts, include multiple speed change rotatable parts such as piston 1, piston pin 2, tooth bar, switching gear shaft, partial gear, planetary gear, planet carrier gear, transmission components is many, slewing range is bigger, thus the equivalent moment of inertia of whole drive mechanism is big, the ability that melts rotating mechanical energy fluctuation is strong, thus being conducive to maintaining output gear shaft 9(power output shaft) rotating speed steady.

Claims (10)

1. the differential drive mechanism of internal combustion engine, including piston, piston pin and the first tooth bar, it is characterised in that one end of the first tooth bar is pitman shaft and the centre bore with piston matches, and pitman shaft is provided with the through hole mated with piston pin, and the both sides of the other end are provided with helical rack;Piston connects the pitman shaft of the first tooth bar by piston pin, and the first switching gear shaft is formed by spur gear and sector gear tandem compound, and the spur gear of the first switching gear shaft and the helical rack of the first tooth bar engage;First partial gear is pot peviform, and it is provided centrally with axis hole, and periphery is incomplete umbrella tooth, and inner circumferential is provided with straight-tooth;First switching gear shaft is spaced substantially equidistant around the first partial gear periphery, and the incomplete umbrella tooth engagement of the sector gear of the first switching gear shaft and the first partial gear;One end of the first row carrier gear is oval gear A, and the other end is support, and support is in " Π " shape and is symmetrically arranged with planetary gear axle, is provided with axis hole, the planetary gear axle of support is separately installed with first planet gear in support;The straight-tooth of the first partial gear inner circumferential and the engagement of two first planet gears;One end of first sun gear shaft is equipped with central gear, the other end is equipped with shaft end gear, first sun gear shaft is threaded onto in the axis hole of support and the first partial gear, and central gear is loaded between two first planet gears and engages, output gear shaft is provided with oval gear B and output gear, output gear engages with shaft end gear, and oval gear B engages with the oval gear A of the first row carrier gear.
2. the differential drive mechanism of internal combustion engine according to claim 1, it is characterised in that the reticule angle of described first tooth bar both sides helical rack tooth top is 90 °.
3. the differential drive mechanism of internal combustion engine according to claim 1, it is characterized in that, continuous umbrella tooth and the radial symmetric that incomplete umbrella tooth is the numbers of teeth such as multistage of described partial gear, every section of continuous umbrella tooth engages with the first sector gear transferring gear shaft successively, and the half of the number that hop count is the first switching gear shaft of the incomplete umbrella tooth of partial gear.
4. the differential drive mechanism of internal combustion engine according to claim 1, it is characterised in that described first planet gear is parallel with the axis of rotation of the first sun gear shaft.
5. the differential drive mechanism of internal combustion engine, including piston, piston pin and the second tooth bar, it is characterised in that one end of the second tooth bar is connecting rod and the centre bore with piston matches, connecting rod is provided with the through hole mated with piston pin, and the other end lateral symmetry of the second tooth bar is provided with spur rack and corresponding parallel;Piston connects the connecting rod of the second tooth bar by piston pin, second switching gear shaft is provided with coordination gear and driving gear, coordination gear engagement on the spur rack of the second tooth bar and the second switching gear shaft, the second switching gear shaft is spaced substantially equidistant around the second partial gear periphery;Second partial gear be provided centrally with axis hole, the periphery of the second partial gear is provided with incomplete straight-tooth, and inner circumferential is provided with straight-tooth;Driving gear and the incomplete straight-tooth of the second partial gear periphery on second switching gear shaft engage;One end of the first row carrier gear is oval gear A, and the other end is support, and support is in " Π " shape and is symmetrically arranged with planetary gear axle, is provided with axis hole, the planetary gear axle of support is separately installed with first planet gear in support;The straight-tooth of the second partial gear inner circumferential and the engagement of two first planet gears;One end of first sun gear shaft is equipped with central gear, the other end is equipped with shaft end gear, first sun gear shaft is threaded onto in the axis hole of support and the second partial gear, and central gear is installed between two first planet gears and engages, output gear shaft is provided with oval gear B and output gear, output gear shaft engages with shaft end gear, and oval gear B engages with the oval gear A of the first row carrier gear.
6. the differential drive mechanism of internal combustion engine according to claim 5, it is characterized in that, the continuous straight-tooth that incomplete straight-tooth is the numbers of teeth such as multistage of described partial gear and radial symmetric, every section of continuous straight-tooth engages with the second driving gear transferring gear shaft successively, and the half of the number that the hop count of the incomplete straight-tooth of partial gear is the second switching gear shaft.
7. the differential drive mechanism of internal combustion engine according to claim 5, it is characterised in that described first planet gear is parallel with the axis of rotation of the first sun gear shaft.
8. the differential drive mechanism of internal combustion engine, including piston, piston pin and the second tooth bar, it is characterised in that one end of the second tooth bar is connecting rod and the centre bore with piston matches, connecting rod is provided with the through hole mated with piston pin, and the other end lateral symmetry of the second tooth bar is provided with spur rack and corresponding parallel;Piston connects the connecting rod of the second tooth bar by piston pin, second switching gear shaft is provided with coordination gear and driving gear, coordination gear engagement on the spur rack of the second tooth bar and the second switching gear shaft, the second switching gear shaft is spaced substantially equidistant around the 3rd partial gear periphery;3rd partial gear be provided centrally with axis hole, the periphery of the 3rd partial gear is coaxially set side by side with incomplete straight-tooth and bevel gear;Driving gear and the incomplete straight-tooth of the 3rd partial gear on second switching gear shaft engage;Central shaft one end of second planet carrier gear is provided with A gear, and the other end is provided with the second planetary gear axle of the central axis with A gear, and the two ends of the second planetary gear axle are provided with the second planetary gear;Second sun gear shaft is constituted by spur gear and bevel gear coaxially arranged side by side and is provided centrally with axis hole, the central shaft of A gear is threaded onto in the axis hole of the 3rd partial gear and the second sun gear shaft, and the bevel gear of the 3rd partial gear and the bevel gear of the second sun gear shaft engage each other connection by the second planetary gear;Being provided with oval gear B and output gear on output gear shaft, the spur gear of the second sun gear shaft engages with the output gear of output gear shaft, and the oval gear B of output gear shaft and the A gear of the second planet carrier gear engage.
9. the differential drive mechanism of internal combustion engine according to claim 8, it is characterized in that, the continuous straight-tooth that incomplete straight-tooth is the numbers of teeth such as multistage of described 3rd partial gear and radial symmetric, every section of continuous straight-tooth engages with the second driving gear transferring gear shaft successively, and the half of the number that the hop count of the incomplete straight-tooth of partial gear is the second switching gear shaft.
10. the differential drive mechanism of internal combustion engine according to claim 8, it is characterised in that described second planetary gear is vertical with the axis of rotation of the second sun gear shaft.
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CN104727936B (en) * 2015-01-22 2017-03-08 唐仁杰 Double-piston rotary internal combustion engine
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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2039352U (en) * 1988-08-02 1989-06-14 四川石油管理局川东开发公司 Geared engine
CN101952569A (en) * 2008-02-13 2011-01-19 戈梅克赛斯股份有限公司 A reciprocating piston mechanism and a method of increasing internal EGR in an internal combustion engine
CN202125352U (en) * 2011-04-08 2012-01-25 周觉明 Queue type engine for planetary crankshaft cylinder
EP2454458B1 (en) * 2009-07-15 2013-05-29 Lambertus Hendrik De Gooijer A reciprocating piston mechanism
CN204060931U (en) * 2014-08-02 2014-12-31 熊薇 The differential transmission mechanism of internal-combustion engine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT6292U1 (en) * 2002-06-19 2003-07-25 Avl List Gmbh Modular combustion engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2039352U (en) * 1988-08-02 1989-06-14 四川石油管理局川东开发公司 Geared engine
CN101952569A (en) * 2008-02-13 2011-01-19 戈梅克赛斯股份有限公司 A reciprocating piston mechanism and a method of increasing internal EGR in an internal combustion engine
EP2454458B1 (en) * 2009-07-15 2013-05-29 Lambertus Hendrik De Gooijer A reciprocating piston mechanism
CN202125352U (en) * 2011-04-08 2012-01-25 周觉明 Queue type engine for planetary crankshaft cylinder
CN204060931U (en) * 2014-08-02 2014-12-31 熊薇 The differential transmission mechanism of internal-combustion engine

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