CN203296926U - Straight shaft type internal combustion engine - Google Patents
Straight shaft type internal combustion engine Download PDFInfo
- Publication number
- CN203296926U CN203296926U CN2013200750174U CN201320075017U CN203296926U CN 203296926 U CN203296926 U CN 203296926U CN 2013200750174 U CN2013200750174 U CN 2013200750174U CN 201320075017 U CN201320075017 U CN 201320075017U CN 203296926 U CN203296926 U CN 203296926U
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Abstract
The utility model discloses a straight shaft type internal combustion engine, and belongs to reciprocating piston type engine. The straight shaft type internal combustion engine resolves the problems that the pressure of an existing internal combustion engine is the largest when the oil supply bursts out, no force arm exists in the upwards vertical direction of a crankshaft handle, a torsion moment starts from zero, the swinging of a connecting rod applies lateral pushing force to a piston so that the connecting rod generates resolution of branch force at the two ends, an exhaust valve is opened at about 40 degrees in front of a lower dead center, and too much energy is exhausted too early. According to the technical scheme, the straight shaft type internal combustion engine is composed of an upper oval transmission gear, a lower oval transmission gear, a middle oval transmission gear, a balance block, an upper half oval gear, a lower half oval gear, a double-face rack connecting rod, a transmission large gear wheel, a transmission pinion, a speed regulator shaft, a gas distribution cam, an oil supply pump cam, a rocker claw, an air cylinder, a piston, an upper gear shaft, a power output shaft, a lower gear shaft, a cam shaft, a balance weight flywheel, a shell body and an externally carried shell body, wherein the double-surface rack connecting rod transmits pushing force of the piston to the upper half oval gear and the lower half oval gear and enables the upper oval transmission gear and the lower oval transmission gear fixed to the same shaft to transmit power through the middle oval transmission gear, and the double-surface rack connecting rod is controlled to make reciprocating motion. The straight shaft type internal combustion engine has the advantages of being simple in structure, low in cost, high in efficiency, large in power, long in service and simple in production process, and saving energy.
Description
Technical field
The utility model belongs to a kind of conventional engine.
Background technique
Present internal-combustion engine exists three large major defects:
1, pressure maximum when fuel feeding breaks out, crankshaft handle does not upwards vertically have the arm of force, torsional moment to start from scratch;
2, the swing of connecting rod, to side-thrust of piston, makes connecting rod to two, all produce the decomposition of a bearing pressure;
3, before bottom dead center about 40 ° open exhaust valves, too much too early energy of having drained.
Summary of the invention
The purpose of this utility model is to provide a kind of direct axis type intenral combustion engine, having solved existing internal-combustion engine pressure maximum, crankshaft handle when fuel feeding breaks out does not upwards vertically have the arm of force, torsional moment start from scratch and stop to zero, the swing of connecting rod to side-thrust of piston, make connecting rod to two, all produce the decomposition of a bearing pressure, three auxiliary strokes are also like this, open exhaust valve, the too much problem of the too early energy of having drained for about 40 ° before bottom dead center.
technical solution of the present utility model is: direct axis type intenral combustion engine is by upper oval driving gear, lower oval driving gear, middle oval driving gear, upper elliptic gear, lower half of elliptic gear, the two-sided rack connecting rod, the transmission gearwheel, driving pinion, governor shaft, equilibrium block, valve cam, the oil feed pump cam, oil pump drives homalocephalus, shake pawl, cylinder, piston, axle cogs, pto＝power take-off, the lower tooth wheel shaft, camshaft, counter-weight flywheel, housing, carrying housing outward on the arm forms, the two-sided rack connecting rod is passed to upper elliptic gear to the thrust of piston, lower half of elliptic gear, make to be fixed on the upper oval driving gear on an axle with them, lower oval driving gear transmits power by middle oval driving gear, and control the two-sided rack connecting rod moves reciprocatingly.
The utility model has the advantages that:
1, simple in structure, cost is low;
2, efficiency is high, saves the energy, power is large;
3, Durability is long.
The accompanying drawing explanation
Fig. 1 is sectional view of the present utility model
Fig. 2 is the schematic diagram of large small transmission gear peace weighing apparatus piece driving gear on the utility model camshaft
Fig. 3 is the schematic diagram of the half of elliptic gear of the utility model and the engagement of the two-sided rack connecting rod
Fig. 4 is the schematic diagram of the half of elliptic gear of the utility model and the engagement of the two-sided rack connecting rod
Fig. 5 is the schematic diagram of the half of elliptic gear of the utility model and the engagement of the two-sided rack connecting rod
Fig. 6 is piston schematic diagram of the present utility model
Fig. 7 is trapezoidal jump ring schematic diagram of the present utility model
Fig. 8 is adjustment pad schematic diagram of the present utility model
Fig. 9 is the two-sided rack connecting rod schematic diagram of the present utility model
Figure 10 is housing of the present utility model and carries the shell construction schematic diagram outward on the arm
Figure 11 is the dynamic schematic diagram of three oval driving gears of the present utility model
Embodiment
The utility model is the internal-combustion engine that adopts opposed twin-tub, two d-axis, the two-sided rack linkage mechanism.
direct axis type intenral combustion engine is by upper oval driving gear 3, lower oval driving gear 8, middle oval driving gear 5, equilibrium block 25, equilibrium block 33, upper elliptic gear 27, lower half of elliptic gear 16, the two-sided rack connecting rod 28, transmission gearwheel 20, driving pinion 30, valve cam 15, oil feed pump cam 21, shake pawl 29, cylinder 24, piston 23, axle 4 cogs, pto＝power take-off 7, lower tooth wheel shaft 10, camshaft 14, counter-weight flywheel 6, housing 13, carry housing 9 outward on the arm, 22 form, the two-sided rack connecting rod 28 is passed to upper elliptic gear 27 to the thrust of piston 23, lower half of elliptic gear 16, make to be fixed on the upper oval driving gear 3 on an axle with them, lower oval driving gear 8 transmits power by middle oval driving gear 5, and control the two-sided rack connecting rod 28 moves reciprocatingly.
Cog on axle 4 and be fixed with upper elliptic gear 27, upper oval driving gear 3, equilibrium block 25, the semi major axis of upper elliptic gear 27 and upper oval driving gear 3 becomes 90 ° of angles and installs on the axle 4 that cogs.On lower tooth wheel shaft 10, be fixed with lower half of elliptic gear 16, driving pinion 30, this end spindle nose 31 is governor shaft, lower oval driving gear 8, lower half of elliptic gear 16 becomes 90 ° of angles installations with the semi major axis of lower oval driving gear 8 on lower tooth wheel shaft 10.Oval driving gear 5, flywheel 6 in the middle of on pto＝power take-off 7, being fixed with.On the semi major axis correspondence of middle oval driving gear 5, the short radius of oval driving gear 3, lower oval driving gear 8 is installed.This moment, the semi major axis of upper elliptic gear 27 had tooth one side and lower half of elliptic gear 16 to be in the two-sided rack connecting rod 28 the hollowest middle place without the flank of tooth, and two equilibrium blocks 25 are in two major parts at the axle 4 that cogs on equilibrium block axle 34 with equilibrium block 33 relative and fix, and two major parts point to the opposite direction of two piston movements.On camshaft 14, be fixed with transmission gearwheel 20, valve cam 15, oil feed pump cam 21, shake pawl 29, the other end is that oil pump drives homalocephalus 12, transmission gearwheel 20 and driving pinion 30 engagements, the rule of engagement is: when the piston 23 on the two-sided rack connecting rod 28 is in the left end compression dead-centre position of cylinder 24, initiatively a tooth of half heel teeth head heel the two-sided rack connecting rod 28 these ends is about to separate, at this moment oil feed pump cam 21 backs down fuel feed pump plunger, and valve cam 15 should, by these end two valve-closings, complete outburst.
The two-sided rack connecting rod 28 is connected with land 50 by land 37 with piston 23, convex stake 38 on land 37 matches with the positioning groove 51 on land 50, with trapezoidal jump ring 35, be arranged in jump-ring slot 53, middle guide rail stake 39 is placed in guide rail sliding chute 48 again.
Lower tooth wheel shaft 10 is provided with oil channel hole 1, and the axle 4 that cogs is provided with oil channel hole 2, and upper elliptic gear 27 is provided with and gets rid of oilhole 26, lower half of elliptic gear 16 is provided with and gets rid of oilhole 18, and housing 13,19 is provided with oil-through hole 11,17, and piston 23 is provided with oil ring oil-through hole 55.
A tooth on upper elliptic gear 27, lower half of elliptic gear 16, the two-sided rack connecting rod 28 and last tooth can wear and tear after using certain hour, can be at piston 23 bottom shimmings 36.
Piston 23 is provided with heat radiation groove 52, and on the two-sided rack connecting rod 28, two ends are provided with stiffening rib 41.
When outburst, 28 teeth of the two-sided rack connecting rod and upper elliptic gear 27,16 tooth engagements of lower half of elliptic gear, be short radius this moment, wheel shaft is had to certain arm of force, make the short radius engagement of full-depth tooth elliptic wheel gear semi major axis on an axle and intermediate gear, Here it is, and power arm is short, the resistance brachium, namely overcome the zero-based shortcoming of bent axle, if while having avoided again wait this moment, equivalent, the isobaric torsional moment that changes into, pto＝power take-off will resemble the outburst draught head and produce and periodically strong and weakly tempestuously change and can't work.Yet its these characteristics have but exactly adapted to the inherent characteristics of internal-combustion engine.Turn to 45 moving, resistance arm equalitys while spending thereupon; While to 90, spending, power arm is greater than resistance arm, and lower half stroke repeats again this variation.So the torsional moment of pto＝power take-off is more uniform, the last tooth of this half side gear is about to leave the last tooth on the tooth bar connecting rod just when piston 23 arrives this stop, at this moment the half passive side gear above is under the control of three driving gears, and the tooth paddy that its tooth is about to enter on the two-sided rack connecting rod 28 is changed driving gear into.Because there is intermediate gear 5 to change upper elliptic gear 27, lower half of elliptic gear 16 into running in the other direction, and each gear is always to a direction rotation, initiatively the last tooth of half side gear end this end of heel the two-sided rack connecting rod is about to separate, a tooth of the half of elliptic gear that this moment is passive also is about to engagement, so just the two-sided rack connecting rod 28 can controlled to the piston 23 at two, moves reciprocatingly.The suction that has again simultaneously fuel feeding, distribution device on camshaft 14 to observe to complete two ends, pressure, quick-fried, alignment order are accurately worked, outwards output kinetic energy.
When the engagement of the teeth on upper elliptic gear 27 and the teeth on the two-sided rack connecting rod 28, lower half of elliptic gear 16 just anodontia one side towards the two-sided rack connecting rod 28.During the teeth on half of elliptic gear 16 and the teeth on the two-sided rack connecting rod 28 engagement instantly, upper elliptic gear 27 also just anodontia one side towards the two-sided rack connecting rod 28.The number of teeth of upper elliptic gear 27, lower half of elliptic gear 16 is identical with the number of teeth of the two-sided rack connecting rod 28, and the semi-perimeter of the geared surface of upper elliptic gear 27, lower half of elliptic gear 16 equates with the running length of piston 23, guarantees the accurate of stop.So namely avoid also there is no the tile kilning phenomenon because of the quick-fried off-energy that shakes.
Straight shaft transmission has been avoided decomposition, side pressure and the excessively friction of the two ends bearing pressure that produces in bent axle machine connecting rod swing.Because upper elliptic gear 27, lower half of elliptic gear 16 and the two-sided rack connecting rod 28 always with the bests of 90 degree to the power angle, tangent direction changes the torsional moment of d-axis in other words, conversion ratio is larger.
Piston 23 in cylinder 24 also as the bent axle machine two slow, middle fast, several years fuel feeding or igniting before having adapted to compression and ending, this moment fuel oil need be through atomization, mixing, evaporation, this physics and the needs of chemical reaction on time and space burn.The angular velocity of pto＝power take-off 7 is constant although the linear velocity of 5 elliptic gears changes, so pto＝power take-off 7 is rotations of average rate, even slightly have pause also can meet above-mentioned requirements when arriving the left and right stop.Also greatly alleviated the impact force of reciprocal inertia.When arriving the left and right stop, be all compression and exhaust, the impact force of reciprocal inertia changed into to two negative work that stroke is necessary, and do the required positive work d-axis of negative work and also reduce over half than bent axle.
The positive circular portion of the protrusion of two half of elliptic gears equals the middle lower hollow part of the two-sided rack connecting rod.
Owing to greatly having improved the transformation efficiency that thrust is changed into to torsional moment, so will limit fuel delivery, exhaust valve can be deferred to front 20 left and right, degree angle of stop and open.
Powerful thrust while breaking out for adapting to, narrow in the middle of teeth two head breadths on the two-sided rack connecting rod 28, because it has the arm of force, outside transmitting power simultaneously, and be unlikely the damage teeth.Due to the restriction fuel delivery, when running into unexpected super large resistance, also resemble the bent axle machine flame-out.
Claims (6)
1. direct axis type intenral combustion engine, it is characterized in that this direct axis type intenral combustion engine is by upper oval driving gear, lower oval driving gear, middle oval driving gear, equilibrium block, upper elliptic gear, lower half of elliptic gear, the two-sided rack connecting rod, the transmission gearwheel, driving pinion, governor shaft, valve cam, the oil feed pump cam, shake pawl, cylinder, piston, axle cogs, pto＝power take-off, the lower tooth wheel shaft, camshaft, counter-weight flywheel, housing, carrying housing outward on the arm forms, the two-sided rack connecting rod is passed to upper elliptic gear to the thrust of piston, lower half of elliptic gear, make to be fixed on the upper oval driving gear on an axle with them, lower oval driving gear transmits power by middle oval driving gear, and control the two-sided rack connecting rod moves reciprocatingly.
2. direct axis type intenral combustion engine as claimed in claim 1, it is characterized in that being fixed with upper elliptic gear, upper oval driving gear, equilibrium block on the axle that cogs of this direct axis type intenral combustion engine, the semi major axis of upper elliptic gear and upper oval driving gear becomes 90 ° of angles and installs on the axle that cogs, on the lower tooth wheel shaft, be fixed with lower half of elliptic gear, driving pinion, lower oval driving gear, the semi major axis of lower half of elliptic gear and lower oval driving gear becomes 90 ° of angles and installs on the lower tooth wheel shaft.
3. direct axis type intenral combustion engine as claimed in claim 1, oval driving gear in the middle of it is characterized in that on the pto＝power take-off of this direct axis type intenral combustion engine being fixed with, flywheel, oval driving gear on the semi major axis correspondence of middle oval driving gear, the short radius of lower oval driving gear is installed, this moment, the semi major axis of upper elliptic gear had tooth one side and lower half of elliptic gear to be in the two-sided rack connecting rod the hollowest middle place without the flank of tooth, and two equilibrium blocks are at the axle that cogs, on the equilibrium block axle, being in two major parts fixes relatively, and major part points to the opposite direction of two piston movements.
4. direct axis type intenral combustion engine as claimed in claim 1, it is characterized in that being fixed with the transmission gearwheel on the camshaft of this direct axis type intenral combustion engine, two valve cams, the oil feed pump cam, shake pawl, oil pump drives homalocephalus, transmission gearwheel and driving pinion engagement, the rule of engagement is: when the piston on the two-sided rack connecting rod is in the left end compression dead-centre position of cylinder, initiatively the last tooth of half side gear end this end of heel the two-sided rack connecting rod is about to separate, a tooth of the half of elliptic gear that this moment is passive also is about to engagement, at this moment the oil feed pump cam backs down fuel feed pump plunger, and valve cam should be by these end two valve-closings, complete outburst, in a word, two ends are observed and are inhaled separately, press, quick-fried, row's order.
5. direct axis type intenral combustion engine as claimed in claim 1, the two-sided rack connecting rod that it is characterized in that this direct axis type intenral combustion engine is connected by land with piston, positioning groove on land matches with the convex stake, with trapezoidal jump ring, be arranged in jump-ring slot, middle guide rail stake is placed in guide rail sliding chute again.
6. direct axis type intenral combustion engine as claimed in claim 1, is characterized in that the transmission gearwheel of this direct axis type intenral combustion engine and the gear ratio of driving pinion are 2: 1, housing with carry housings close outward on the arm and be connected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013200750174U CN203296926U (en) | 2013-01-28 | 2013-01-28 | Straight shaft type internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013200750174U CN203296926U (en) | 2013-01-28 | 2013-01-28 | Straight shaft type internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203296926U true CN203296926U (en) | 2013-11-20 |
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ID=49572940
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2013200750174U Expired - Fee Related CN203296926U (en) | 2013-01-28 | 2013-01-28 | Straight shaft type internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203296926U (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106870144A (en) * | 2017-04-15 | 2017-06-20 | 雷敬汉 | The Oscillating Tooth Gear Reducer internal combustion engine of push rod six |
| CN106870134A (en) * | 2017-04-15 | 2017-06-20 | 邱秀芳 | The oscillating tooth high-efficiency lubricating transmission internal combustion engine of push rod six |
| CN106870143A (en) * | 2017-04-15 | 2017-06-20 | 雷敬汉 | The Oscillating Tooth Gear Reducer internal combustion engine of push rod five |
| CN106884719A (en) * | 2017-04-15 | 2017-06-23 | 邱秀芳 | The oscillating tooth high-efficiency lubricating of push rod seven is driven four-cylinder internal combustion engine |
| CN106884714A (en) * | 2017-04-15 | 2017-06-23 | 邱秀芳 | The oscillating tooth high-efficiency lubricating of push rod five is driven four-cylinder internal combustion engine |
| CN106894893A (en) * | 2017-04-15 | 2017-06-27 | 邱秀芳 | Push rod list oscillating tooth high-efficiency lubricating transmission internal combustion engine |
| CN106968790A (en) * | 2017-04-15 | 2017-07-21 | 邱秀芳 | The oscillating tooth high-efficiency lubricating of push rod eight is driven two juxtaposed cylinders internal combustion engine |
| CN106968792A (en) * | 2017-04-15 | 2017-07-21 | 邱秀芳 | The oscillating tooth high-efficiency lubricating of push rod four is driven four-cylinder internal combustion engine |
| CN106988876A (en) * | 2017-04-15 | 2017-07-28 | 邱秀芳 | The oscillating tooth high-efficiency lubricating of push rod three is driven to row double cylinder IC engine |
| CN106988877A (en) * | 2017-04-15 | 2017-07-28 | 邱秀芳 | Push rod list oscillating tooth high-efficiency lubricating is driven to row double cylinder IC engine |
| CN109139245A (en) * | 2018-09-30 | 2019-01-04 | 安阳工学院 | A kind of new engine and its control method of no crankshaft |
| CN113323737A (en) * | 2021-06-29 | 2021-08-31 | 王少成 | Timing connecting rod component and horizontally opposed engine |
-
2013
- 2013-01-28 CN CN2013200750174U patent/CN203296926U/en not_active Expired - Fee Related
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106870144A (en) * | 2017-04-15 | 2017-06-20 | 雷敬汉 | The Oscillating Tooth Gear Reducer internal combustion engine of push rod six |
| CN106870134A (en) * | 2017-04-15 | 2017-06-20 | 邱秀芳 | The oscillating tooth high-efficiency lubricating transmission internal combustion engine of push rod six |
| CN106870143A (en) * | 2017-04-15 | 2017-06-20 | 雷敬汉 | The Oscillating Tooth Gear Reducer internal combustion engine of push rod five |
| CN106884719A (en) * | 2017-04-15 | 2017-06-23 | 邱秀芳 | The oscillating tooth high-efficiency lubricating of push rod seven is driven four-cylinder internal combustion engine |
| CN106884714A (en) * | 2017-04-15 | 2017-06-23 | 邱秀芳 | The oscillating tooth high-efficiency lubricating of push rod five is driven four-cylinder internal combustion engine |
| CN106894893A (en) * | 2017-04-15 | 2017-06-27 | 邱秀芳 | Push rod list oscillating tooth high-efficiency lubricating transmission internal combustion engine |
| CN106968790A (en) * | 2017-04-15 | 2017-07-21 | 邱秀芳 | The oscillating tooth high-efficiency lubricating of push rod eight is driven two juxtaposed cylinders internal combustion engine |
| CN106968792A (en) * | 2017-04-15 | 2017-07-21 | 邱秀芳 | The oscillating tooth high-efficiency lubricating of push rod four is driven four-cylinder internal combustion engine |
| CN106988876A (en) * | 2017-04-15 | 2017-07-28 | 邱秀芳 | The oscillating tooth high-efficiency lubricating of push rod three is driven to row double cylinder IC engine |
| CN106988877A (en) * | 2017-04-15 | 2017-07-28 | 邱秀芳 | Push rod list oscillating tooth high-efficiency lubricating is driven to row double cylinder IC engine |
| CN109139245A (en) * | 2018-09-30 | 2019-01-04 | 安阳工学院 | A kind of new engine and its control method of no crankshaft |
| CN109139245B (en) * | 2018-09-30 | 2020-11-03 | 安阳工学院 | Engine without crankshaft and control method thereof |
| CN113323737A (en) * | 2021-06-29 | 2021-08-31 | 王少成 | Timing connecting rod component and horizontally opposed engine |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20131120 Termination date: 20150128 |
|
| EXPY | Termination of patent right or utility model |