CN104153881A - Differential drive mechanism of internal combustion engine - Google Patents
Differential drive mechanism of internal combustion engine Download PDFInfo
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- CN104153881A CN104153881A CN201410376095.7A CN201410376095A CN104153881A CN 104153881 A CN104153881 A CN 104153881A CN 201410376095 A CN201410376095 A CN 201410376095A CN 104153881 A CN104153881 A CN 104153881A
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 85
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- 230000002146 bilateral effect Effects 0.000 claims description 6
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- 239000000446 fuel Substances 0.000 abstract description 10
- 239000002912 waste gas Substances 0.000 abstract description 3
- 230000003247 decreasing effect Effects 0.000 abstract 1
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- 239000007789 gas Substances 0.000 description 14
- 238000006243 chemical reaction Methods 0.000 description 10
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- 230000029058 respiratory gaseous exchange Effects 0.000 description 3
- 230000002000 scavenging effect Effects 0.000 description 3
- 230000001133 acceleration Effects 0.000 description 2
- 238000004364 calculation method Methods 0.000 description 2
- 239000000567 combustion gas Substances 0.000 description 2
- 230000002028 premature Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
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- 238000007599 discharging Methods 0.000 description 1
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- 238000012423 maintenance Methods 0.000 description 1
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Abstract
The invention discloses a differential drive mechanism of an internal combustion engine. Pistons are connected with connecting rod shafts of first racks through piston pins. Straight gears of first switch gear shafts are meshed with oblique gears of the first racks. Sector gears of the first switch gear shafts are meshed with incomplete umbrella teeth of a first incomplete gear. Straight teeth of the inner periphery of the first incomplete gear are meshed with two first planet gears. A sun gear is arranged between the first planet gears and meshed with the same. An output gear is meshed with a shaft end gear. An oval gear B is meshed with an oval gear A of a first planet carrier gear. By the use of the differential drive mechanism, fuel consumption of the engine is greatly reduced, fuel economy is improved, and waste gas exhaust of the engine is lowered; air exchange efficiency and limit speed of the engine are improved so as to remarkably enhance weight-power ratio of the engine; running stability of the engine is increased, vibration and noise of the engine is decreased, and service life of the engine is prolonged.
Description
Technical field
The present invention relates to IC engine transmission system technical field, particularly the differential transmission mechanism of internal-combustion engine.
Background technique
Internal-combustion engine mainly comprises fuel supply system, ignition system, cooling system, lubrication system, transmission system etc.In Hyundai Motor, shipping and various power equipment, the internal-combustion engine of crankshaft connecting rod type transmission system is used the most extensively.Since application in 1898 Christian eras existing over one hundred year history so far.Its basic working principle does not become, and is exactly that the pressurized gas that burnt in cylinder of piston promote to move up and down, and drives crankshaft rotating by connecting rod.Piston from top dead center to lower dead center (or crankshaft rotating 180 is spent) is called a stroke.Quartastroke engine comprises following working procedure: suction stroke, compression stroke, power stroke, exhaust stroke.
For the internal-combustion engine of existing crankshaft connecting rod type transmission system, engine power output is that the crankshaft connecting rod type transmission system forming by piston, connecting rod and bent axle triplicity completes.This internal-combustion engine mainly contains following shortcoming:
1, in igniting work done in an instant, the gas blow-through power in cylinder reaches rapidly maximum value, because piston is near top dead center, the pressure maximum that now bearing portion of bent axle bears, surface friction drag maximum, the mechanical work of loss is also large thus, has reduced the working life of crankshaft bearing simultaneously.
2, near the gas blow-through power in cylinder reaches maximum value time, because piston is near top dead center, the now power of the crankshaft & connecting output arm of force is little, gaseous-pressure in cylinder can not fully be converted into merit output, thereby obviously reduce heat energy-mechanical work conversion efficiency of internal-combustion engine, affected power per liter and the oil consumption performance of internal-combustion engine.
3, crankshaft & connecting is not axisymmetric parts, and the vibration that caused by crankshaft & connecting in internal combustion engine operation process is large, noise is large; The crankshaft & connecting weighing apparatus that has much difficulty in healing, its manufacturing process is more complicated, and cost is high; In use, piston, crankshaft & connecting etc. are easy to wear, and maintenance expenses is high; Adopt the internal-combustion engine limit speed of crankshaft-link rod low, seriously restricted the raising of motor power to weight ratio.
4, in the operation process of internal-combustion engine that adopts four-stroke crankshaft connecting rod type transmission system, piston is all the time in a kind of to-and-fro motion state, when air inlet, piston enters again compression stroke very soon in lower dead center moment, thereby in the time that cylinder body volume is maximum, there is no the more fresh mixed oil gas of more time inspiration, when exhaust, piston enters again intake stroke very soon to top dead center moment, thereby when making volume of cylinder minimum, do not have the more time to allow waste gas farthest discharge, these situations finally all affect more fresh mixed oil gas and enter cylinder, thereby cause engine breathing efficiency low, the raising of engine power is subject to certain restrictions.For two-stroke internal-combustion engine, its inlet and outlet are all carried out near lower dead center, but also have same problem.
5, in the cylinder of internal-combustion engine of crankshaft connecting rod type transmission system, mixed gas is short period of combustion in pressure maximum, volume minimum, 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 transmission system is in order to improve engine performance, all in premature ignition or the oil spout in various degree of piston arrives budc, object be for allow mixed gas in combustion chamber volume minimum, burn sooner, more complete, thereby can obtain larger power stage, and reduce the discharging waste gas concentration of motor, also produced certain negative effect but do like this: because of premature ignition, in-cylinder pressure sharply raises, block piston stroking upward, increase compression negative work, and be easy to cause combustion knock phenomenon.This contradiction exists all the time in the internal-combustion engine of existing crankshaft connecting rod type transmission system.
6, in the internal combustion engine operation process of crankshaft connecting rod type transmission system, the force direction periodically-varied of connecting rod to piston, and in the time that engine power output is maximum, connecting rod also reaches near maximum value along cylinder wall surface Normal direction the active force of piston, cause that thus the frictional power loss between piston and cylinder is very large, and easily cause the damage that between piston and cylinder, surface causes because of friction.
The internal-combustion engine that another kind is called as triangle rotor type motor has also obtained application comparatively widely.The transmission adopted gear drive of triangle rotor type motor, driving mechanism axial symmetry is better, and Engine Limit rotating speed is high, and power and weight ratio are outstanding compared with the internal-combustion engine of crankshaft connecting rod type transmission system, but there is also very large deficiency.Such as cylinder combustion burning is insufficient, oil consumption is excessive, output shaft torque is too small, cylinder seal difficulty etc.Be divided into two power because rotary polygonal piston engine cylinder combustion gas acts on the swelling pressure of rotor side surface, try hard to recommend moving output shaft rotation for one, and another power pointed to output shaft center, thereby cause the output torque of complete machine too small; Make rate of combustion too low because its cylinder is long and narrow, excessive oil consumption; Because use the cylinder of special shape, the difficulty that has caused cylinder manufacturing and cylinder seal to manufacture and design.The problems that above-mentioned triangle rotor type motor exists, cause it to be difficult to promote the use of on a large scale.
The problems that exist in order to solve the internal-combustion engine of crankshaft connecting rod type transmission system, Chinese patent " has the internal-combustion engine of opposed pistons ", and (publication number: CN 1074083C) adopted multi-blade cam drive system to replace the crankshaft connecting rod type transmission system of crankshaft connecting rod type transmission system internal-combustion engine, make thus to adopt the internal-combustion engine of this multi-blade cam drive system greatly to relax the friction between piston and cylinder, and there is comparatively compact structure, but this patent still exists " 1, in igniting work done in an instant, gas blow-through power in cylinder reaches rapidly maximum value, because piston is near top dead center, the pressure maximum that now bearing portion of bent axle bears, surface friction drag maximum, the mechanical work of loss is also large thus, reduced the working life of crankshaft bearing simultaneously, 2, near the gas blow-through power in cylinder reaches maximum value time, because piston is near top dead center, the now power of the crankshaft & connecting output arm of force is little, gaseous-pressure in cylinder can not fully be converted into merit output, thereby obviously reduce heat energy-mechanical work conversion efficiency of internal-combustion engine, affected power per liter and the oil consumption performance of internal-combustion engine." etc. problem.
Summary of the invention
The object of this invention is to provide a kind of differential transmission mechanism that can be applicable to internal-combustion engine, adopt differential gearing form to realize the power stage of internal-combustion engine, can significantly reduce engine consumption, improve fuel economy, improve engine exhaust emission; Can improve the scavenging efficiency of motor, improve the limit speed of motor, thereby significantly improve the power to weight ratio of motor; The smoothness of operation of motor be can improve, engine luggine and noise reduced, increasing service life of engine.
The present invention takes following technological scheme to realize above-mentioned purpose, the first technological scheme of the present invention: the differential transmission mechanism of internal-combustion engine, comprise piston, wrist pin and the first tooth bar, it is characterized in that, one end of the first tooth bar is pitman shaft and matches with the center hole of piston, pitman shaft is provided with the through hole mating with wrist 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 wrist pin, the first switching gear shaft is formed by spur gear and tooth sector tandem compound, and the spur gear of the first switching gear shaft engages with the helical rack of the first tooth bar; The first partial gear is a pot peviform, and its center is provided with axis hole, and periphery is incomplete umbrella tooth, and interior week is provided with straight-tooth; The first switching gear shaft is around the equidistant arrangement of the first partial gear periphery, and the first the switching tooth sector of gear shaft and incomplete umbrella tooth of the first partial gear engages; One end of the first planet carrier gear is oval gear A, and the other end is support, and support is " Π " shape and is symmetrically arranged with planet pin, is provided with axis hole in support, is separately installed with the first planetary pinion on the planet pin of support; In the first partial gear, the straight-tooth in week engages with two first planetary pinions; Sun gear is equipped with in one end of the first sun gear shaft, the other end is equipped with shaft end gear, the first sun gear shaft is threaded onto in the axis hole of support and the first partial gear, and sun gear is loaded between two first planetary pinions and engagement, oval gear B and output gear are installed on output gear shaft, output gear engages with shaft end gear, and oval gear B engages with the oval gear A of the first planet carrier gear.
The intersection line angle of described the first tooth bar both sides helical rack tooth top is 90 °.
Continuous umbrella tooth and the radial symmetric of the numbers of teeth such as the incomplete umbrella tooth of described partial gear is multistage, every section of continuous umbrella tooth engages with the tooth sector of the first switching gear shaft successively, and the hop count of the incomplete umbrella tooth of partial gear is the half of the number of the first switching gear shaft.
Described the first planetary pinion is parallel with the rotational axis of the first sun gear shaft.
The second technological scheme of the present invention: the differential transmission mechanism of internal-combustion engine, comprise piston, wrist pin and the second tooth bar, one end of the second tooth bar is connecting rod and matches with the center hole of piston, connecting rod is provided with the through hole mating with wrist pin, and the other end bilateral 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 wrist pin, on the second switching gear shaft, be provided with and coordinate gear and driving gear, the spur rack of the second tooth bar engages with the coordination gear on the second switching gear shaft, and the second switching gear shaft is around the equidistant arrangement of the second partial gear periphery; The center of the second partial gear is provided with axis hole, and the periphery of the second partial gear is provided with incomplete straight-tooth, and interior week is provided with straight-tooth; Driving gear on the second switching gear shaft engages with the incomplete straight-tooth of the second partial gear periphery; One end of the first planet carrier gear is oval gear A, and the other end is support, and support is " Π " shape and is symmetrically arranged with planet pin, is provided with axis hole in support, is separately installed with the first planetary pinion on the planet pin of support; In the second partial gear, the straight-tooth in week engages with two first planetary pinions; Sun gear is equipped with in one end of the first sun gear shaft, the other end is equipped with shaft end gear, the first sun gear shaft is threaded onto in the axis hole of support and the second partial gear, and sun gear is installed between two first planetary pinions and engagement, oval gear B and output gear are installed on output gear shaft, output gear shaft engages with shaft end gear, and oval gear B engages with the oval gear A of the first planet carrier gear.
Continuous straight-tooth and the radial symmetric of the numbers of teeth such as the incomplete straight-tooth of described partial gear is multistage, every section of continuous straight-tooth engages with the driving gear of the second switching gear shaft successively, and the hop count of the incomplete straight-tooth of partial gear is the half of the number of the second switching gear shaft.
Described the first planetary pinion is parallel with the rotational axis of the first sun gear shaft.
The 3rd technological scheme of the present invention: the differential transmission mechanism of internal-combustion engine, comprise piston, wrist pin and the second tooth bar, one end of the second tooth bar is connecting rod and matches with the center hole of piston, connecting rod is provided with the through hole mating with wrist pin, and the other end bilateral 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 wrist pin, on the second switching gear shaft, be provided with and coordinate gear and driving gear, the spur rack of the second tooth bar engages with the coordination gear on the second switching gear shaft, and the second switching gear shaft is around the equidistant arrangement of the 3rd partial gear periphery; The center of the 3rd partial gear is provided with axis hole, and the periphery of the 3rd partial gear is coaxially set side by side with incomplete straight-tooth and bevel gear; Driving gear on the second switching gear shaft engages with the incomplete straight-tooth of the 3rd partial gear; Central shaft one end of the second planet carrier gear is provided with A gear, and the other end is provided with second planet pin vertical with the central shaft of A gear, and the two ends of the second planet pin are provided with the second planetary pinion; The second sun gear shaft is by spur gear and coaxial bevel gear arranged side by side forms and center is provided 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 is connected by the second planetary pinion is intermeshing with the bevel gear of the second sun gear shaft; Oval gear B and output gear are installed on output gear shaft, and 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 engages with the A gear of the second planet carrier gear.
Continuous straight-tooth and the radial symmetric of the numbers of teeth such as the incomplete straight-tooth of described the 3rd partial gear is multistage, every section of continuous straight-tooth engages with the driving gear of the second switching gear shaft successively, and the hop count of the incomplete straight-tooth of partial gear is the half of the number of the second switching gear shaft.
Described the second planetary pinion is vertical with the rotational axis of the second sun gear shaft.
Comprehensive above-mentioned three technological schemes, wrist pin is affixed to tooth bar on piston, does as a whole along the to-and-fro motion of cylinder-bore axis direction.Between switching gear shaft and tooth bar, by rack and pinion engagement transmission, realize power transmission and motor coordination between multiple tooth bars.The incomplete gear teeth of partial gear (be incomplete umbrella tooth in the first technological scheme, second and the 3rd is incomplete straight-tooth in technological scheme) are being circumferentially uniformly distributed of the continuous gear teeth of the numbers of teeth such as some sections.Every section of continuous gear teeth of partial gear successively with switching gear shaft engagement driving, realize cylinder combustion gas the work done of piston institute exported to partial gear by tooth bar.The complete gear teeth of partial gear, with planetary pinion engagement driving.Planetary pinion and sun gear shaft engagement driving.Output gear shaft and sun gear shaft be by circular gear engagement driving, simultaneously output gear shaft with and planet carrier gear by oval gear engagement driving, partial gear, planet carrier gear, sun gear shaft coaxial line rotate.Thus, between partial gear and output gear shaft, form a kind of differential gear transmissions relation, thereby realize the output of piston merit from partial gear to output gear shaft.
Piston and tooth bar are fixedly connected into a whole assembly by wrist pin; Also can cancel wrist pin, directly piston and the manufacturing of tooth bar entirety are shaped.
According to the difference of relative space relation, between the rotational axis of adjacent switching gear shaft, angle can be 90 ° (as first technological schemes) between two, also can be 0 ° (as second and the 3rd technological scheme), correspondingly, the both sides flank profil tooth top intersection line angle β of tooth bar is 90 ° or 0 °.
The rotational axis of planetary pinion and sun gear shaft can parallel (as the first and second technological schemes), form the plane differential gear train of planet wheel axis and center-wheel arbor line parallel; The rotational axis of planetary pinion and sun gear shaft also can intersect vertically (as the 3rd technological scheme), forms the space differential gear train that planet wheel axis and central gear axis intersect vertically.
A kind of differential transmission mechanism that can be applicable to internal-combustion engine provided by the present invention, adopts differential gearing form to realize the power stage of internal-combustion engine, has following beneficial effect:
1, can significantly reduce engine consumption, improve fuel economy, improve engine exhaust emission.
2, can improve the scavenging efficiency of motor, improve the limit speed of motor, thereby significantly improve the power to weight ratio of motor.
3, the smoothness of operation of motor be can improve, engine luggine and noise reduced, increasing service life of engine.
4, engine structure relative compact, compared with the internal-combustion engine of existing crankshaft connecting rod type transmission system, the driving mechanism that the present invention uses is all gear transmission, makes engine structure relative compact.
5, because the transmission system of an internal-combustion engine for crankshaft connecting rod type transmission system is carried out technological innovation, the other technologies of the internal-combustion engine of existing main flow I. C. engine crankshaft linkage type transmission system except transmission system still can be used, thereby have realized the maximum possible of existing internal-combustion engine technology is inherited.
6, engine power output steadily.
Brief description of the drawings
Fig. 1 is the perspective view of the present invention's the first technological scheme.
Fig. 2 is the perspective view of piston and the first rack combination in the present invention's the first technological scheme.
Fig. 3 is the first tooth bar axial view in the present invention's the first technological scheme.
Fig. 4 is the three-dimensional view of the first switching gear shaft in the present invention's the first technological scheme.
Fig. 5 is the three-dimensional view of the first partial gear in the present invention's the first technological scheme.
Fig. 6 is that the A of the first partial gear in Fig. 5 is to view.
Fig. 7 is the first planetary stereochemical structure view in the present invention's the first technological scheme.
Fig. 8 is the perspective view of the first planet carrier gear in the present invention's the first technological scheme.
Fig. 9 is the perspective view of the first sun gear shaft in the present invention's the first technological scheme.
Figure 10 is the perspective view of output gear shaft in the present invention's the first technological scheme.
Figure 11 is that the B of output gear shaft in Figure 10 is to view.
Figure 12 is the perspective view of the present invention's the second technological scheme.
Figure 13 is the perspective view of the second tooth bar in the present invention's the second technological scheme.
Figure 14 is the perspective view of piston and the second rack combination in the present invention's the second technological scheme.
Figure 15 is the perspective view of the second switching gear shaft in the present invention's the second technological scheme.
Figure 16 is the three-dimensional view of the second partial gear in the present invention's the second technological scheme.
Figure 17 is the perspective view of the present invention's the 3rd technological scheme.
Figure 18 is the three-dimensional view of the 3rd partial gear in the present invention's the 3rd technological scheme.
Figure 19 is the second planetary three-dimensional view in the present invention's the 3rd technological scheme.
Figure 20 is the three-dimensional view of the second sun gear shaft in the present invention's the 3rd technological scheme.
Figure 21 is the perspective view of the second planet carrier gear in the present invention's the 3rd technological scheme.
Figure 22 is that the C of the second planet carrier gear in Figure 21 is to view.
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 the instantaneous transmission ratio schematic diagram (abscissa be the rotation angle of even rotating speed output gear shaft) of planet carrier gear to output gear shaft.
Figure 26 is the internal combustion engine movement velocity performance diagram (rotation angle that abscissa is even rotating speed output shaft) of crankshaft connecting rod type transmission system.
Figure 27 is the instantaneous transmission ratio schematic diagram (abscissa be the rotation angle of even rotating speed output gear shaft) of partial gear to output gear shaft.
In figure: 1. piston, 2. wrist pin, 3. the first tooth bar, 3a. the second tooth bar, 4. the first switching gear shaft, 41. spur gears, 42. bevel gears, 4a. second gear shaft of transferring, 4a1. coordinates gear, 4a2. driving gear, 5. the first partial gear, 5a. the second partial gear, 5b. the 3rd partial gear, 6. the first planetary pinion, 6a. the second planetary pinion, 7. the first planet carrier gear, 71. oval gear A, 72. supports, 721. planet pin, 7a. the second planet carrier gear, 7a1. the second planet pin, 7a2.A gear, 8. the first sun gear shaft, 81. sun gears, 82. shaft end gears, 8a. the second sun gear shaft, 9. output gear shaft, 91. oval gear B, 92. output gears, β. intersection line angle, α. central angle.
Embodiment
Below in conjunction with drawings and Examples, the present invention is described further.The first technological scheme of the present invention: referring to Fig. 1 to Figure 11, the differential transmission mechanism of internal-combustion engine, comprise piston 1, wrist pin 2 and the first tooth bar 3, one end of the first tooth bar 3 is pitman shaft 31 and matches with the center hole of piston 1, pitman shaft 31 is provided with the through hole mating with wrist pin 2, and the both sides of the other end of the first tooth bar 3 are provided with helical rack 32; Pitman shaft 31, the first switching gear shafts 4 that piston 1 connects the first tooth bar 3 by wrist pin 2 are formed by spur gear 41 and tooth sector 42 tandem compounds, and the first switching spur gear 41 of gear shaft 4 and the helical rack 32 of the first tooth bar 3 engage; The first partial gear 5 is a pot peviform, and its center is provided with axis hole, and periphery is incomplete umbrella tooth, and interior week is provided with straight-tooth; The first switching gear shaft 4 is around the equidistant arrangement of the first partial gear 5 periphery, and the first the switching tooth sector 42 of gear shaft 4 and incomplete umbrella tooth of the first partial gear 5 engages; One end of the first planet carrier gear 7 is oval gear A71, and the other end is support 72, and support 72 is " Π " shape and is symmetrically arranged with planet pin 721, in support 72, is provided with axis hole, is separately installed with the first planetary pinion 6 on the planet pin 721 of support 72; The straight-tooth in the first 5 interior weeks of partial gear engages with two first planetary pinions 6; Sun gear 81 is equipped with in one end of the first sun gear shaft 8, the other end is equipped with shaft end gear 82, the first sun gear shaft 8 is threaded onto in the axis hole of support 72 and the first partial gear 5, and sun gear 81 is loaded between two first planetary pinions 6 and engagement, oval gear B91 and output gear 92 are installed on output gear shaft 9, output gear 92 engages with shaft end gear 82, and oval gear B91 engages with the oval gear A71 of the first planet carrier gear 7.
The intersection line angle β of described the first tooth bar 3 both sides helical rack 32 tooth tops is 90 °.
Continuous umbrella tooth and the radial symmetric of the numbers of teeth such as the incomplete umbrella tooth of described partial gear 5 is multistage, every section of continuous umbrella tooth engages with the tooth sector 42 of the first switching gear shaft 4 successively, and the hop count of the incomplete umbrella tooth of partial gear 5 is the half of the number of the first switching gear shaft 4.
Described the first planetary pinion 6 is parallel with the rotational axis of the first sun gear shaft 8.
Piston 1 and the first tooth bar 3 can be a unitary moulding structure.
The second technological scheme of the present invention: referring to Figure 12 to Figure 16, the differential transmission mechanism of internal-combustion engine, comprise piston 1, wrist pin 2 and the second tooth bar 3a, one end of the second tooth bar 3a is connecting rod and matches with the center hole of piston 1, connecting rod is provided with the through hole mating with wrist pin 2, and the other end bilateral 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 wrist pin 2, on the second switching gear shaft 4a, be provided with and coordinate gear 4a1 and driving gear 4a2, the spur rack of the second tooth bar 3a engages with the coordination gear 4a1 on the second switching gear shaft 4a, and the second switching gear shaft 4a is around the equidistant arrangement of the second partial gear 5a periphery; The second partial gear 5a center is provided with axis hole, and the periphery of the second partial gear 5a is provided with incomplete straight-tooth, and interior week is provided with straight-tooth; Driving gear 4a2 on the second switching gear shaft 4a engages with the incomplete straight-tooth of the second partial gear 5a periphery; One end of the first planet carrier gear 7 is oval gear A71, and the other end is support 72, and support 72 is " Π " shape and is symmetrically arranged with planet pin 721, in support 72, is provided with axis hole, is separately installed with the first planetary pinion 6 on the planet pin 721 of support 72; In the second partial gear 5a, the straight-tooth in week engages with two first planetary pinions 6; Sun gear 81 is equipped with in one end of the first sun gear shaft 8, the other end is equipped with shaft end gear 82, the first sun gear shaft 8 is threaded onto in the axis hole of support 72 and the second partial gear 5a, and sun gear 81 is installed between two first planetary pinions 6 and engagement, oval gear B91 and output gear 92 are installed on output gear shaft 9, output gear 92 engages with shaft end gear 82, and oval gear B91 engages with the oval gear A71 of the first planet carrier gear 7.
Continuous straight-tooth and the radial symmetric of the numbers of teeth such as the incomplete straight-tooth of described partial gear 5 is multistage, every section of continuous straight-tooth engages with the driving gear 4a2 of the second switching gear shaft 4a successively, and the hop count of the incomplete straight-tooth of partial gear 5 is the half of the number of the second switching gear shaft 4a.
Described the first planetary pinion 6 is parallel with the rotational axis of the first sun gear shaft 8.
Piston 1 and the second tooth bar 3a can be a unitary moulding structure.
The 3rd technological scheme of the present invention: referring to Figure 17 to Figure 22, the differential transmission mechanism of internal-combustion engine, comprise piston 1, wrist pin 2 and the second tooth bar 3a, one end of the second tooth bar 3a is connecting rod and matches with the center hole of piston 1, connecting rod is provided with the through hole mating with wrist pin 2, and the other end bilateral 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 wrist pin 2, on the second switching gear shaft 4a, be provided with and coordinate gear 4a1 and driving gear 4a2, the spur rack of the second tooth bar 3a engages with the coordination gear 4a1 on the second switching gear shaft 4a, and the second switching gear shaft 4a is around the equidistant arrangement of the 3rd partial gear 5b periphery; The 3rd partial gear 5b center is provided 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; Driving gear 4a2 on the second switching gear shaft 4a engages with the incomplete straight-tooth of the 3rd partial gear 5b; Central shaft one end of the second planet carrier gear 7a is provided with A gear 7a2, and the other end is provided with the second planet pin 7a1 vertical with the central shaft of A gear 7a2, and the two ends of the second planet pin 7a1 are provided with the second planetary pinion 6a; The second sun gear shaft 8a is by spur gear and coaxial bevel gear arranged side by side forms and center is provided 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 planetary pinion 6a is intermeshing is connected by second for the bevel gear of the bevel gear of the 3rd partial gear 5b and the second sun gear shaft 8a; Oval gear B91 and the spur gear of output gear 92, the second sun gear shaft 8a and the output gear 92 of output gear shaft 9 are installed on output gear shaft 9 and engage, the oval gear B91 of output gear shaft 9 engages with the A gear 7a2 of the second planet carrier gear 7a.
Continuous straight-tooth and the radial symmetric of the numbers of teeth such as the incomplete straight-tooth of described the 3rd partial gear 5b is multistage, every section of continuous straight-tooth engages with the driving gear 4a2 of the second switching gear shaft 4a successively, and the hop count of the incomplete straight-tooth of partial gear 5b is the half of the number of the second switching gear shaft 4a.
Described the second planetary pinion 6a is vertical with the rotational axis of the second sun gear shaft 8a.
Piston 1 and the second tooth bar 3a can be a unitary moulding structure.
embodiment 1:the first technological scheme of the present invention, referring to Fig. 1 to Figure 11.The differential transmission mechanism of internal-combustion engine, comprises piston 1, wrist pin 2, the first tooth bar 3, the first switching gear shaft 4, the first partial gear 5, the first planetary pinion 6, the first planet carrier gear 7, the first sun gear shaft 8 and output gear shaft 9.
Internal-combustion engine adopts four-stroke working method, total cylinder A, cylinder B, cylinder C and tetra-cylinders of cylinder D, and cylinder-bore axis is parallel to each other, and cylinder-bore axis is circumferentially equally spaced.In internal combustion engine operation process, each cylinder carries out air-breathing in the direction of the clock successively, compression, work done, exhaust stroke.In each cylinder, wrist pin 2 is affixed to the first tooth bar 3 on piston 1, does as a wholely along the to-and-fro motion of cylinder-bore axis direction, and the first tooth bar 3 has two straight-sided flanks, and becomes 90 degree angles between two straight-sided flanks.Between every two the first tooth bars 3, transmit and motor coordination by the engagement driving effect realizable force of the first switching gear shaft 4, the first tooth bar 3 one has four, correspondingly, the first switching gear shaft 4 also one has four, close the mutual alignment of the first tooth bar 3 and the first switching gear shaft 4 is (as shown in Figure 23): in the time that cylinder A starts suction stroke, cylinder A inner carrier 1 starts from top dead center descending, start compression stroke with the clockwise adjacent cylinder B of cylinder A, the piston 1 in cylinder B starts from lower dead center up.In like manner, start power stroke with the clockwise adjacent cylinder D of cylinder B, cylinder D inner carrier 1 starts descending from top dead center, start exhaust stroke with the clockwise adjacent cylinder C of cylinder D, cylinder C inner carrier 1 starts up from lower dead center, the first tooth bar 3 alternate cycles to-and-fro motion like this that each cylinder is corresponding, and by the engagement driving effect of the switching of first between each the first tooth bar 3 gear shaft 4, realize motor coordination and power transmission between the first tooth bar 3.
Because the first switching gear shaft 4 one has four and uniform, therefore, the incomplete gear teeth of the first partial gear 5, are that two sections of about quarter turns are bored being circumferentially uniformly distributed of tooth continuously, and every section is bored central angle alpha corresponding to tooth is continuously 70 °～90 °.In the time that certain cylinder enters power stroke, piston starts descending from top dead center, drive the first switching gear shaft 4(clockwise direction of corresponding the first tooth bar 3 correspondences), the approximately quarter turn that this first switching gear shaft 4 starts to enter with the first partial gear 5 is bored engaging of tooth continuously, the rotating speed that piston merit starts to output to the first partial gear 5 and drive the first partial gear 5 acceleration of starting from scratch, realizes the output of piston merit.When this cylinder power stroke proceeds to approximately one half, corresponding the first switching gear shaft 4 drives the first partial gear 5 to accelerate to maximum (top) speed.Afterwards, corresponding this first switching gear shaft 4 of work done cylinder is still driving the first partial gear 5, but next cylinder (clockwise direction) compression stroke required power increases, therefore the first partial gear 5 reduces speed now, and finish 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 the engagement driving with the first partial gear 5, next cylinder power stroke starts, the first switching gear shaft 4 that next cylinder is corresponding starts to enter and the engaging of the first partial gear 5, the first partial gear 5 starts again the one direction speed ripple process of zero rotating speed-acceleration-maximum speed-deceleration-zero rotating speed of a new round, thereby starts new piston merit output procedure.
The complete gear teeth on the first partial gear 5, are 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 pinion 6 engagement driving.Planetary pinion 6 is parallel with the rotational axis of sun gear shaft 8, forms the plane differential gear train of planet wheel axis and center-wheel arbor line parallel.
The pulsation rotating speed of the first partial gear 5 and the uniform rotation conversion relation of output gear shaft 9, adopt reverse thinking mode, and the pulsation rotating speed transformational analysis from the at the uniform velocity rotating speed of output gear shaft 9 to the first partial gear 5, is easier to understand.Supposing has rotation speed n 0 on output gear shaft 9, due to the inertia of motor and load, can think that the rotation speed n 0 on output gear shaft 9 is even rotating speed, between sun gear shaft 8 and output gear shaft 9, it is stable drive ratio transmission, it between planet carrier gear 7 and output gear shaft 9, is the right variable ratio transmission (as shown in figure 25) of oval gear, according to differential gear train gear ratio calculation method, can draw by sun gear shaft 8, planet carrier gear 7, planetary pinion 6, in the plane differential gear train of the first partial gear 5 compositions such as grade, the velocity ratio of the first partial gear 5 to sun gear shaft 8, thereby can calculate the velocity ratio (as shown in figure 27) of the first partial gear 5 to output gear shaft 9.If the stable drive ratio of getting between sun gear shaft 8 and output gear shaft 9 is 2:1, and get planetary pinion 6 and compare for 1:4 with the Pitch radius of the complete gear teeth of the first partial gear 5 of corresponding engagement, correspondingly the eccentricity of oval gear B91 is 0.2, under this parameter of structure design, can obtain meet " output gear shaft 9 moves with uniform velocity, the first partial gear 5 does pulsation and rotates (minimum speed is zero), and the first partial gear 5 corners (that is stroke of corresponding piston) that each pulsation rotation period of the first partial gear 5 is corresponding 90 ° " etc. the plane differential gear train design result that requires, thereby realize motion conversion and the merit output of piston 1 to-and-fro motion to output gear shaft 9 uniform rotation.
From above-mentioned conversed analysis process, by sun gear shaft 8, planet carrier gear 7, planetary pinion 6, the plane differential gear train of partial gear 5 compositions such as grade, introducing output gear shaft 9 and sun gear shaft 8 by circular gear engagement driving, and output gear shaft 9 with and planet carrier gear 7 by after oval gear engagement driving, the transmission degrees of freedom of plane differential gear train is changed into 1 from 2, power transmission and motor coordination between sun gear shaft 8 and planet carrier gear 7 are realized, thereby realize the merit output to output gear shaft 9 through partial gear 5 of piston merit.
embodiment 2:the second technological scheme of the present invention, referring to Figure 12 to Figure 16, the present embodiment is a kind of differential transmission mechanism that can be applicable to internal-combustion engine, and its differential gearing system is made up of piston 1, wrist pin 2, the second tooth bar 3a, the second switching gear shaft 4a, the second partial gear 5a, the first planetary pinion 6, the first planet carrier gear 7, the first sun gear shaft 8 and output gear shaft 9.
Internal-combustion engine adopts four-stroke working method, total cylinder A ＇, cylinder B ＇, cylinder C ＇, tetra-cylinders of cylinder D ＇, and cylinder-bore axis is parallel to each other, and the orthogonal array distribution of cylinder-bore axis.In internal combustion engine operation process, each cylinder carries out air-breathing, compression, work done, exhaust stroke successively according to the cylinder A ＇ shown in Figure 24, cylinder B ＇, cylinder C ＇, cylinder D ＇ number order, for example, in the time that cylinder A ＇ starts suction stroke, cylinder B ＇ starts compression stroke, cylinder C ＇ starts power stroke, cylinder D ＇ starts exhaust stroke, in the time that cylinder A ＇ starts compression stroke, cylinder B ＇ starts power stroke, cylinder C ＇ starts exhaust stroke, and cylinder D ＇ starts suction stroke, so circulation.
In each cylinder, wrist pin 2 is affixed to the second tooth bar 3a on piston 1, does as a wholely along the to-and-fro motion of cylinder-bore axis direction, and each the second tooth bar 3a has two straight-sided flanks, and parallel between two straight-sided flanks.
Between every two the second tooth bar 3a, pass through the engagement driving effect of the second switching gear shaft 4a, realizable force transmission and motor coordination.Cylinder has four, and correspondingly, the second tooth bar 3a also one has four.In order to make the axial symmetry of the second partial gear 5a good, the incomplete gear teeth of getting the second partial gear 5a are two sections and circumferentially uniform, and the second switching gear shaft 4a also one has four.The mutual alignment of the second tooth bar 3a and the second switching gear shaft 4a is closed and is: as shown in figure 24, in the time that cylinder A ＇ starts suction stroke, cylinder A ＇ inner carrier 1 starts from top dead center descending, 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 center, the cylinder D ＇ adjacent with cylinder C ＇ starts exhaust stroke, cylinder D ＇ inner carrier 1 starts up from lower dead center, the second tooth bar 3a alternate cycles to-and-fro motion like this that each cylinder is corresponding, and by the engagement driving effect of the switching of second between each the second tooth bar 3a gear shaft 4a, realize motor coordination and power transmission between the second tooth bar 3a.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 quadrate dot location array of four second switching gear shaft 4a, and this foursquare diagonal is parallel with cylinder-bore axis.
The incomplete gear teeth of the second partial gear 5a, are being circumferentially uniformly distributed of two sections of about quarter turn continuous cylinder teeth, and every section of central angle alpha corresponding to the incomplete gear teeth is 70 °～90 °.In the time that (shown in Figure 24) cylinder A ＇ enters power stroke, piston 1 starts descending from top dead center, directly drive the second switching gear shaft 4a in outside by corresponding the second tooth bar 3a, and indirectly drive the second switching gear shaft 4a in another outside, the second switching gear shaft 4a in outside to start to enter and the engaging of 1/4 week incomplete gear teeth of the second partial gear 5a; The rotating speed that piston merit starts to output to the second partial gear 5a and drive the second partial gear 5a acceleration of starting from scratch, realizes the output of piston merit.When cylinder A ＇ power stroke proceeds to approximately one half, corresponding two second switching gear shaft 4a drive the second partial gear 5a to accelerate to maximum (top) speed, afterwards, corresponding the second switching gear shaft 4a of cylinder A ＇ is still driving the second partial gear 5a, but cylinder B ＇ compression stroke required power increases, therefore the second partial gear 5a reduces speed now, cylinder A ＇ power stroke finishes, when piston 1 arrives lower dead center, the rotating speed of the second partial gear 5a is also reduced to zero, so two switching the second gear shaft 4a that cylinder A ＇ drives exit the engagement driving with 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 definite plane of the axis of these two second switching gear shaft 4a by corresponding the second tooth bar 3a) start to enter and the engaging of the second partial gear 5a, the second partial gear 5a starts again the one-sided speed ripple process of zero rotating speed-acceleration-maximum speed-deceleration-zero rotating speed of a new round, thereby start new piston merit output procedure.
The complete gear teeth on the 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 the first planetary pinion 6 engagement driving.The pulsation rotating speed of the second partial gear 5a is identical with the uniform rotation conversion relation of output gear shaft 9 and embodiment's 1, and this is repeated no more.
embodiment 3:the 3rd technological scheme of the present invention, referring to Figure 17 to Figure 22.The present embodiment is a kind of differential transmission mechanism that can be applicable to internal-combustion engine, and its differential gearing system is made up of piston 1, wrist pin 2, the second tooth bar 3a, the second switching gear shaft 4a, the 3rd partial gear 5b, the second planetary pinion 6a, the second planet carrier gear 7a, the second sun gear shaft 8a, output gear shaft 9.
Internal-combustion engine adopts four-stroke working method, have four cylinders, as shown in figure 24, power transmission and the way of output of motor coordination mode and piston merit to the three partial gear 5b etc. between the second tooth bar 3a in the space arrangement of cylinder, the stroke of cylinder order, each cylinder, identical with embodiment 2.
The complete gear teeth on the 3rd partial gear 5b be complete circular cone tooth and with the 3rd partial gear 5b on incomplete gear teeth coaxial line.In the speed ripple process of the 3rd partial gear 5b, its complete gear teeth all the time with the second planetary pinion 6a engagement driving.The rotational axis of the second planetary pinion 6a and the second sun gear shaft 8a intersects vertically, and forms the space differential gear train that planet wheel axis and central gear axis intersect vertically.
The pulsation rotating speed of the 3rd partial gear 5b and the uniform rotation conversion relation of output gear shaft 9, adopt reverse thinking mode, and the pulsation rotating speed transformational analysis from the at the uniform velocity rotating speed of output gear shaft 9 to the 3rd partial gear 5b, is easier to understand.
Supposing has at the uniform velocity rotation speed n 0 on output gear shaft 9, between the second sun gear shaft 8a and output gear shaft 9, it is stable drive ratio transmission, it between the second planet carrier gear 7a and output gear shaft 9, is the right variable ratio transmission (as shown in figure 25) of oval gear, according to differential gear train gear ratio calculation method, can draw by the second sun gear shaft 8a, the second planet carrier gear 7a, the second planetary pinion 6a, in the space differential gear train of the 3rd partial gear 5b composition, the velocity ratio of the 3rd partial gear 5b to the second sun gear shaft 8a, thereby can calculate the velocity ratio (as shown in figure 27) of the 3rd partial gear 5b to output gear shaft 9.In the time getting stable drive ratio between the second sun gear shaft 8a and output gear shaft 9 and be 3:2, 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, the 3rd partial gear 5b does pulsation and rotates (minimum speed is zero), and the 3rd partial gear 5b corner (that is stroke of corresponding piston) of corresponding 90 degree of the each pulsation rotation period of the 3rd partial gear 5b " etc. the space differential gear train design result that requires, thereby realize motion conversion and the merit output of piston 1 to-and-fro motion to output gear shaft 9 uniform rotation.
From above-mentioned conversed analysis process, by the second sun gear shaft 8a, the second planet carrier gear 7a, the second planetary pinion 6a, the space differential gear train of the composition such as the 3rd partial gear 5b, in the stable drive ratio engagement driving of having introduced between output gear 92 and the second sun gear shaft 8a, and after variable ratio engagement driving between oval gear B91 and the second planet carrier gear 7a, the transmission degrees of freedom of plane differential gear train is changed into one from two, power transmission and motor coordination between the second sun gear shaft 8a and the second planet carrier gear 7a are realized, thereby realize the merit output to output gear shaft 9 through the 3rd partial gear 5b of piston merit.
In sum, key point of the present invention:
1, the differential transmission mechanism of internal-combustion engine is made up of piston 1, wrist pin 2, tooth bar, switching gear shaft, partial gear, planetary pinion, planet carrier gear, sun gear shaft and output gear shaft 9.
2, can piston 1 and tooth bar be fixedly connected into a whole assembly by wrist pin 2; Also can cancel wrist pin 2, directly piston 1 and the manufacturing of tooth bar entirety are shaped.
3, internal-combustion engine can have one or more cylinders, and in each stroke of internal-combustion engine, the assembly that piston 1, wrist pin 2, tooth bar etc. form is along the reciprocal translation of cylinder-bore axis direction.
4, switching gear shaft is realized motor coordination and the power transmission between the corresponding tooth bar of multiple cylinders.
5, when certain cylinder is during in power stroke, by the engagement driving between the corresponding tooth bar of this cylinder and switching gear shaft, piston merit passes to partial gear, and drive the rotating speed of partial gear from zero to maximum, again by being up to zero, the above variation continuously of rotating speed single order of partial gear, a speed ripple cycle that completes partial gear.
7, sun gear shaft, planet carrier gear, planetary pinion and partial gear composition plane or space differential gear train, and engage stable drive ratio transmission at the output gear of having introduced between output gear shaft 9 and sun gear shaft, and output gear shaft 9 with and planet carrier gear between oval gear engage after variable ratio transmission, the transmission degrees of freedom of plane differential gear train is changed into one from two, power transmission and motor coordination between sun gear shaft and planet carrier gear are realized, thereby the determinacy transmission to output gear shaft uniform rotation is rotated in the pulsation that has realized partial gear, realize the output to output gear shaft 9 through partial gear of piston merit.
The present invention has following advantageous application effect:
A) can significantly reduce engine consumption, improve fuel economy, improve engine exhaust emission.The present invention mainly realizes this effect 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 transmission system (as shown in figure 26), under the differential gearing mode adopting in the present invention, corresponding to output gear shaft 9(pto＝power take-off) uniform rotation, piston is approaching in the process of up/down stop, and it is mild that piston 1 linear velocity (being equivalent to the rotating speed of partial gear 5) converges to 0 velocity variations process gradually.That is to say, be about at the end in the compression stroke of piston 1, the line of motion speed of piston 1 of the present invention becomes very slow, and this will be conducive to the abundant mixing of combustible oil gas mixture in cylinder, and provides combustible oil gas mixture in cylinder fully to burn the needed time.Thereby can allow the ignition advance angle of motor greatly to reduce, greatly reduce compression negative work, increase the circulation merit of motor.And in the time that the power stroke of piston arrives, same because the line movement velocity of piston 1 is slowly to increase since 0, in cylinder, the burning of combustible oil gas mixture is more abundant, reach with the needed fuel delivery of cylinder of internal-combustion engine internal pressure peak value of existing crankshaft connecting rod type transmission system still less, thereby can reduce engine consumption, improved the toxic emission of motor simultaneously.
Secondly, according to interrelated data, frictional loss in existing crankshaft connecting rod type internal-combustion engine inner carrier to-and-fro motion process between piston 1 and cylinder wall, consume the 10%-20% of cycle of engine merit, in piston 1 power stroke of the present invention, piston 1 is subject to differential transmission mechanism reaction force direction can be all the time and cylinder-bore axis conllinear, and piston 1 greatly reduces with the more existing crankshaft connecting rod type internal-combustion engine of frictional loss of cylinder wall surface, thereby obviously reduce engine consumption, improve fuel economy.
Again, in 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, in the time that cylinder pressure arrives near maximum value, the block bearing of the each driving component of motor there will not be excessive pressure, and the frictional work of engine operation process consumption on bearing etc. compared the little of existing crankshaft connecting rod type internal-combustion engine, thereby can reduce engine consumption, improve fuel economy.
Finally, in 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, near cylinder pressure arrives maximum value time, the power output arm of force of piston 1 of the present invention is than large many of the power output arm of force of the piston of existing crankshaft connecting rod type internal-combustion engine 1, gaseous-pressure in cylinder fully can be converted into merit output, greatly improve heat energy-mechanical work conversion efficiency of the present invention, thereby obviously reduce engine consumption, improve fuel economy.
B) can improve the scavenging efficiency of motor, improve the limit speed of motor, thereby significantly improve the power to weight ratio of motor.The present invention mainly realizes this effect by following technological approaches:
First,, compared with the internal combustion engine movement velocity characteristic of existing crankshaft connecting rod type transmission system (as shown in figure 26), under the differential gearing mode adopting in the present invention, piston linear velocity converges to 0 velocity variations process mild (as shown in figure 27) gradually.When cylinder in exhaust stroke at the end, the present invention slowly piston linear velocity will to be conducive to exhaust abundant, and reduce exhaust process windage loss; When cylinder in suction stroke at the end, the present invention slowly piston linear velocity also will be conducive to suck more fresh oil gas mixture, and reduce breathing process windage loss.This will be conducive to improve engine breathing efficiency, also the raising of engine thermal cycle efficiency be gained to some extent, improve the power per liter of motor, thereby can improve the power to weight ratio of motor.
Secondly, compared with the internal-combustion engine of existing crankshaft connecting rod type transmission system, the present invention except the assembly of the formation such as piston and tooth bar be straight reciprocating motion, other driving component is all axialy symmetric part, thus permission motor has higher limit speed; From the combustion efficiency of motor, piston linear velocity characteristic of the present invention (as shown in figure 27), will contribute to motor under high rotating speed, still can keep higher combustion efficiency.Therefore, can, by improving the limit speed of motor of the present invention, significantly improve power to weight ratio and the power per liter of motor.
C) smoothness of operation of motor be can improve, engine luggine and noise reduced, increasing service life of engine.The present invention mainly realizes this effect by following technological approaches:
First, compared with the internal-combustion engine of existing crankshaft connecting rod type transmission system, driving mechanism major part of the present invention is axialy symmetric part, remaining non-axisymmetric parts is also straight reciprocating motion form, obviously reduce various vibrations and the noise that the each parts of transmission system cause due to mass unbalance, thereby can significantly improve the smoothness of operation of motor, reduce the running noise level of motor, and can extend the working life of motor.
Secondly, it is continuous above that the each transmission part movement process of motor of the present invention is all speed single order, without rigid impulse, also without soft impulse, thereby can improve the smoothness of operation of motor, reduces engine luggine and noise, increasing service life of engine.
Again, in 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, near cylinder pressure arrives maximum value time, the block bearing of the each driving component of motor there will not be excessive pressure, and the impact force that the parts such as engine bearing bear is little, long service life.
Finally, in piston power stroke of the present invention, piston 1 is subject to differential transmission mechanism reaction force direction can be all the time and cylinder-bore axis conllinear, thereby piston 1 greatly reduces with the more existing crankshaft connecting rod type internal-combustion engine of frictional force of cylinder wall surface, especially near cylinder pressure arrival maximum value time, piston 1 greatly reduces with the more existing crankshaft connecting rod type internal-combustion engine of frictional force of cylinder wall surface, thereby reduce the wearing and tearing between piston 1 and cylinder wall surface, extended the working life of motor.
D) engine structure relative compact of the present invention.Compared with the internal-combustion engine of existing crankshaft connecting rod type transmission system, the driving mechanism that the present invention uses is all gear transmission, makes engine structure relative compact.
E) the present invention is owing to only carrying out technological innovation for the transmission system of crankshaft connecting rod type internal-combustion engine, the other technologies of existing main flow I. C. engine crankshaft connecting rod type internal-combustion engine except transmission system still can be used, thereby have realized the maximum possible of existing internal-combustion engine technology is inherited.
F) engine power output of the present invention steadily.The present invention mainly realizes this effect by following technological approaches:
First, from Figure 27, near power stroke of the present invention initial stage cylinder pressure peak value goes out now, corresponding piston line movement velocity is slow, make engine power output momentary value be unlikely to higher, and when the compression stroke of the present invention later stage, cylinder pressure was higher, piston line movement velocity is slow, and compression consumed power is less, and these are all conducive to maintain, and the power stage of output gear shaft (pto＝power take-off) is steady and rotating speed is steady.
Secondly, the differential transmission mechanism that the present invention adopts, include multiple speed change rotatable parts such as piston 1, wrist pin 2, tooth bar, switching gear shaft, partial gear, planetary pinion, planet carrier gear, speed change parts are many, slewing range is larger, thereby the equivalent moment of inertia of whole driving mechanism is large, can fluctuate to rotary machine to melt ability strong, thereby be conducive to maintain output gear shaft 9(pto＝power take-off) rotating speed steady.
Claims (10)
1. the differential transmission mechanism of internal-combustion engine, comprise piston, wrist pin and the first tooth bar, it is characterized in that, one end of the first tooth bar is pitman shaft and matches with the center hole of piston, pitman shaft is provided with the through hole mating with wrist 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 wrist pin, the first switching gear shaft is formed by spur gear and tooth sector tandem compound, and the spur gear of the first switching gear shaft engages with the helical rack of the first tooth bar; The first partial gear is a pot peviform, and its center is provided with axis hole, and periphery is incomplete umbrella tooth, and interior week is provided with straight-tooth; The first switching gear shaft is around the equidistant arrangement of the first partial gear periphery, and the first the switching tooth sector of gear shaft and incomplete umbrella tooth of the first partial gear engages; One end of the first planet carrier gear is oval gear A, and the other end is support, and support is " Π " shape and is symmetrically arranged with planet pin, is provided with axis hole in support, is separately installed with the first planetary pinion on the planet pin of support; In the first partial gear, the straight-tooth in week engages with two first planetary pinions; Sun gear is equipped with in one end of the first sun gear shaft, the other end is equipped with shaft end gear, the first sun gear shaft is threaded onto in the axis hole of support and the first partial gear, and sun gear is loaded between two first planetary pinions and engagement, oval gear B and output gear are installed on output gear shaft, output gear engages with shaft end gear, and oval gear B engages with the oval gear A of the first planet carrier gear.
2. the differential transmission mechanism of internal-combustion engine according to claim 1, is characterized in that, the intersection line angle of described the first tooth bar both sides helical rack tooth top is 90 °.
3. the differential transmission mechanism of internal-combustion engine according to claim 1, it is characterized in that, continuous umbrella tooth and the radial symmetric of the numbers of teeth such as the incomplete umbrella tooth of described partial gear is multistage, every section of continuous umbrella tooth engages with the tooth sector of the first switching gear shaft successively, and the hop count of the incomplete umbrella tooth of partial gear is the half of the number of the first switching gear shaft.
4. the differential transmission mechanism of internal-combustion engine according to claim 1, is characterized in that, described the first planetary pinion is parallel with the rotational axis of the first sun gear shaft.
5. the differential transmission mechanism of internal-combustion engine, comprise piston, wrist pin and the second tooth bar, it is characterized in that, one end of the second tooth bar is connecting rod and matches with the center hole of piston, connecting rod is provided with the through hole mating with wrist pin, and the other end bilateral 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 wrist pin, on the second switching gear shaft, be provided with and coordinate gear and driving gear, the spur rack of the second tooth bar engages with the coordination gear on the second switching gear shaft, and the second switching gear shaft is around the equidistant arrangement of the second partial gear periphery; The center of the second partial gear is provided with axis hole, and the periphery of the second partial gear is provided with incomplete straight-tooth, and interior week is provided with straight-tooth; Driving gear on the second switching gear shaft engages with the incomplete straight-tooth of the second partial gear periphery; One end of the first planet carrier gear is oval gear A, and the other end is support, and support is " Π " shape and is symmetrically arranged with planet pin, is provided with axis hole in support, is separately installed with the first planetary pinion on the planet pin of support; In the second partial gear, the straight-tooth in week engages with two first planetary pinions; Sun gear is equipped with in one end of the first sun gear shaft, the other end is equipped with shaft end gear, the first sun gear shaft is threaded onto in the axis hole of support and the second partial gear, and sun gear is installed between two first planetary pinions and engagement, oval gear B and output gear are installed on output gear shaft, output gear shaft engages with shaft end gear, and oval gear B engages with the oval gear A of the first planet carrier gear.
6. the differential transmission mechanism of internal-combustion engine according to claim 5, it is characterized in that, continuous straight-tooth and the radial symmetric of the numbers of teeth such as the incomplete straight-tooth of described partial gear is multistage, every section of continuous straight-tooth engages with the driving gear of the second switching gear shaft successively, and the hop count of the incomplete straight-tooth of partial gear is the half of the number of the second switching gear shaft.
7. the differential transmission mechanism of internal-combustion engine according to claim 5, is characterized in that, described the first planetary pinion is parallel with the rotational axis of the first sun gear shaft.
8. the differential transmission mechanism of internal-combustion engine, comprise piston, wrist pin and the second tooth bar, it is characterized in that, one end of the second tooth bar is connecting rod and matches with the center hole of piston, connecting rod is provided with the through hole mating with wrist pin, and the other end bilateral 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 wrist pin, on the second switching gear shaft, be provided with and coordinate gear and driving gear, the spur rack of the second tooth bar engages with the coordination gear on the second switching gear shaft, and the second switching gear shaft is around the equidistant arrangement of the 3rd partial gear periphery; The center of the 3rd partial gear is provided with axis hole, and the periphery of the 3rd partial gear is coaxially set side by side with incomplete straight-tooth and bevel gear; Driving gear on the second switching gear shaft engages with the incomplete straight-tooth of the 3rd partial gear; Central shaft one end of the second planet carrier gear is provided with A gear, and the other end is provided with second planet pin vertical with the central shaft of A gear, and the two ends of the second planet pin are provided with the second planetary pinion; The second sun gear shaft is by spur gear and coaxial bevel gear arranged side by side forms and center is provided 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 is connected by the second planetary pinion is intermeshing with the bevel gear of the second sun gear shaft; Oval gear B and output gear are installed on output gear shaft, and 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 engages with the A gear of the second planet carrier gear.
9. the differential transmission mechanism of internal-combustion engine according to claim 8, it is characterized in that, continuous straight-tooth and the radial symmetric of the numbers of teeth such as the incomplete straight-tooth of described the 3rd partial gear is multistage, every section of continuous straight-tooth engages with the driving gear of the second switching gear shaft successively, and the hop count of the incomplete straight-tooth of partial gear is the half of the number of the second switching gear shaft.
10. the differential transmission mechanism of internal-combustion engine according to claim 8, is characterized in that, described the second planetary pinion is vertical with the rotational axis of the second sun gear shaft.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104727936A (en) * | 2015-01-22 | 2015-06-24 | 唐仁杰 | Double-piston rotor type internal combustion engine |
| CN106065813A (en) * | 2016-07-18 | 2016-11-02 | 朱晓明 | A kind of electromotor connected Crankless engine drive mechanism and there is it |
| CN114523895A (en) * | 2022-03-02 | 2022-05-24 | 蔚来汽车科技(安徽)有限公司 | Cup holder assembly and vehicle with same |
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| CN2039352U (en) * | 1988-08-02 | 1989-06-14 | 四川石油管理局川东开发公司 | Geared engine |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104727936A (en) * | 2015-01-22 | 2015-06-24 | 唐仁杰 | Double-piston rotor type internal combustion engine |
| CN106065813A (en) * | 2016-07-18 | 2016-11-02 | 朱晓明 | A kind of electromotor connected Crankless engine drive mechanism and there is it |
| CN106065813B (en) * | 2016-07-18 | 2019-03-22 | 朱晓明 | A kind of series connection Crankless engine transmission mechanism and the engine with it |
| CN114523895A (en) * | 2022-03-02 | 2022-05-24 | 蔚来汽车科技(安徽)有限公司 | Cup holder assembly and vehicle with same |
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|---|---|
| CN104153881B (en) | 2016-06-29 |
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