CN109184900A - A kind of engine-driven gearing - Google Patents
A kind of engine-driven gearing Download PDFInfo
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- CN109184900A CN109184900A CN201811160584.3A CN201811160584A CN109184900A CN 109184900 A CN109184900 A CN 109184900A CN 201811160584 A CN201811160584 A CN 201811160584A CN 109184900 A CN109184900 A CN 109184900A
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- engine
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- rotary motion
- axial
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B61/00—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing
- F02B61/06—Combinations of engines with mechanical gearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/181—Centre pivot rocking arms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transmission Devices (AREA)
Abstract
The invention discloses a kind of engine-driven gearings, including engine housing, case lid and the cylinder head being fixed on case lid, piston is equipped in cylinder head, it is characterized by also including axial-rotation driving mechanisms, the mechanism includes the axial movement component being connected with piston and for limiting its guiding mechanism moved in a straight line along piston traffic direction, and one by limitation be axially moved rotary motion component and output revolving shaft that is fixed thereto or being integrally connected, shaft rotation be assemblied on cabinet and with piston coaxial or parallel arrangement, axial movement component is cylinder-like structure, it is circumferentially equipped with the driving groove of at least one inclination closed loop thereon, and rotary motion component is placed on and is axially moved on component or protrudes into wherein, rolling element with driving groove cooperation is installed thereon, it is past with the straight line that will be axially moved component by driving trenched side-wall and contact rolling element Multiple movement is converted to the continuous rotation movement of rotary motion component.Energy conversion efficiency of the invention is much higher than traditional crankshaft-linking rod drive mechanism.
Description
Technical field
The present invention relates to a kind of engine-driven gearings.
Background technique
The transmission device of conventional engines mainly uses crankshaft-linking rod drive mechanism, and principle is caused by fuel detonation
The axial force on piston for driving it to move along a straight line is applied to by connecting rod and its is converted with the connection structure of crankshaft crank
At the radial force of driving crankshaft rotary motion, since its structure is simply again perfect extremely mature by continuing to optimize for a long time,
With relatively broad.
But it is known in industry, it is known that one very big problem of above-mentioned crankshaft-linking rod drive mechanism physical presence itself: by
There is an angle always when the power of the rectilinear direction acted on piston passes to crankshaft crank by connecting rod, so that crankshaft
What is obtained always in a rotational direction is the power being decomposed.Such case especially the initial stage of piston motion and latter stage very
Obvious and extreme, when the direction of the power decomposed at this time is close to 90 degree, power can not almost be passed, according to acting calculation formula W=
FS(F is power, and S is distance), it is understood that a big chunk power is wasted in the case where the time is constant.So passing
The output power of system engine is really the power obtained after being decomposed.Therefore the energy of most conventional engines turns at present
Changing efficiency can only achieve 35% or so, also waste while people bring people's convenience using above-mentioned conventional engines
The huge energy.
Therefore the energy conversion efficiency of engine is improved, core seeks to improve the structure of its internal transmission,
There is an urgent need to a kind of new efficient transmission devices in industry at present.
Summary of the invention
Object of the present invention is to: a kind of higher engine-driven gearing of energy conversion efficiency is provided.
The technical scheme is that a kind of engine-driven gearing, including engine housing, it is fixed on engine housing
On engine case lid and be fixed on the engine cylinder head that engine case covers, piston is equipped in engine cylinder head, feature exists
In further including axial-rotation driving mechanism, which includes an axial movement component being connected with piston and for limiting the axial direction
The rotary motion component that the guiding mechanism and one that moving link is moved in a straight line along piston traffic direction are axially moved by limitation
With the output revolving shaft fixed or be integrally connected with the rotary motion component, output revolving shaft rotation be assemblied on engine housing and with
The piston coaxial heart or parallel arrangement, axial movement component is cylinder-like structure, and rotary motion component is nested with and is being axially moved structure
On the outside of part or axial movement component inside is protruded into, is axially moved the driving ditch for being circumferentially equipped at least one inclination closed loop on component
Slot, and the rolling element with driving groove cooperation is installed on rotary motion component, it is connect by driving trenched side-wall and rolling element
Touching is moved with the continuous rotation that the straight reciprocating motion for being axially moved component is converted to rotary motion component.
Further, for stress balance between axial movement component and rotary motion component and stability the considerations of,
Heretofore described driving groove preferred design identical two or more, the axial direction of these driving grooves components axially movable is set
It sets without intersecting, drives circle center's interval any angle of relative axial movement component between groove；Or the driving ditch
Slot is identical two or more, the interval angles setting in relative circumferential center on the circumference for being axially moved component of these driving grooves
And intersect, and in the axial direction without being staggered；Or the driving groove is identical two or more, these driving grooves are in axial fortune
Relative circumferential center interval angles are arranged and intersect on the circumference of dynamic component, and are staggered in the axial direction.
Further, when heretofore described engine is four-stroke engine, piston intake and power phase often walk one
The rotational angle of the corresponding rotary motion component of a stroke is all larger than 180 degree, so as to the air inlet and working application time of oversize piston.It is real
Border in use, we have found that piston charging stage and power phase corresponding driving groove be same section, i.e., rolling element is covered
The angle that turns over of rotary motion component is identical when this section drives groove, is all larger than 180 degree.
Further, in the present invention piston intake and when power phase rolling element and same section of driving groove two sidewalls
Contact rolls respectively, this section drives the two sidewalls profile wire shaped of groove different, and the side wall wheel in corresponding piston intake stage
The initial slope of profile is greater than the side wall profile line initial slope of corresponding piston power phase, to accelerate piston downlink initial stage
Downstream rate, so that the negative pressure increased faster in cylinder in same downgoing time enters more oil gas, to improve engine
Power.
Further, heretofore described rolling element is the spherical rolling being mounted on rotary motion component by universal joint
Body.
Further, heretofore described rolling element is idler wheel, the rolling surface of the idler wheel and the two side walls of driving groove
Contact rolls.
Further, it is integrally formed with piston fixed link on heretofore described axial movement component, which wears
It crosses engine case lid to be connected with piston, the output revolving shaft is axially moved component and piston coaxial heart arrangement；And the Guiding machine
Structure includes several along piston traffic direction guide post disposed in parallel, and guide post one end is fixed with engine case lid, and the other end is then
It is fixed with a guide pillar support, and equal engagement sleeves are equipped with sliding guide sleeve on each guide post, these sliding guide sleeves are fixed or integrally set
In on axial movement component；And the bearing being placed on output revolving shaft is equipped in the engine housing and guide pillar support, and
The shaft shoulder portion that offsets with above-mentioned two side bearing is respectively equipped on output revolving shaft to limit the axial movement of rotary motion component, or
It is equipped in engine case body from both ends and supports the limiting bracket of only rotary motion component to limit the axial movement of rotary motion component.
Further, it is heretofore described be axially moved component on it is not set driving groove part be engraved structure to
Mitigate weight.
Further, heretofore described rotary motion component is cylindrical structural member or fork member, fork member packet
The attachment base fixed or be integrally connected for same output revolving shaft is included, which is equipped with the fork extended along piston motion direction
Item, rolling element are mounted on fork item, and when the quantity for pitching item is more than two, these fork items turn about rotary motion component
The moving axis heart is centrosymmetric distribution.
Further, heretofore described guide post is centrosymmetric setting about the circle center for being axially moved component.
The working principle of the invention is described as follows:
The inclination for needing to illustrate to drive groove in the present invention is the driving groove for being axially moved the axial line of component
" place face " get over the vertical plane close to axial line, then its gradient is bigger, on the contrary then its gradient is smaller, gentler.
The present invention can apply on the engine of any stroke, in actual work, the axial-rotation driving in the present invention
Mechanism tilts the rolling element fortune of the driving trenched side-wall promotion rotary motion component of closed loop design by being axially moved above component
It is dynamic, enable rotary motion component continuous rotation, so that the linear motion of piston to be converted to the continuous rotation of output revolving shaft
Movement.During being somebody's turn to do, the power of piston output changes direction simply by axial-rotation driving mechanism, and is absolutely not divided
Solution, removes seldom a part of frictional force, and most power are delivered to output revolving shaft output.And the starting point of piston acting
And end dead point area very little, most of energy are utilized.Therefore, it is much higher than from the transfer efficiency of its energy for the structure of itself
Conventional crankshaft-linking rod drive mechanism.
Secondly, the existing engine using crankshaft-linking rod drive mechanism, by taking four-stroke engine as an example, itself structure is determined
Determine its four stroke operating angles and is restricted to 180 degree, therefore, piston intake time and working application time are all fixed, but
From four impulse strokes of four-stroke engine, we can analyze out the cylinder of same discharge capacity in four impulse strokes, if
Entering more oil gas or working application time lengthening in cylinder body can make engine power bigger, in existing crankshaft-link rod engine
Middle people can only allow as far as possible more oil gas to enter cylinder body by way of shifting to an earlier date open time delay and turning off inlet valve, but the present invention can
To be designed by changing the driving groove path being axially moved on component to increase charging stage corresponding rotational angle (> 180
Degree), it is ensured that extend piston downgoing time when air inlet, under the premise of engine speed is constant to enter more oil in cylinder
Gas improves engine power.Certainly we can also be by driving the optimization design of the side wall profile line of groove (to improve side wall wheel
Profile initial slope) so that piston is accelerated downstream rate at downlink initial stage, to make to increase in cylinder faster in same downgoing time
Negative pressure further increase engine power hence into more oil gas.
Meanwhile for four-stroke engine, in four impulse strokes of its piston, piston working stroke is also wished
Power caused by detonation has more time effects on piston to allow more power to pass to output shaft, and in the present invention just
The corresponding driving groove of good piston working stroke driving groove corresponding with suction stroke is same section, is overlapped, therefore air inlet
The rotational angle of stroke increases (> 180 degree) and similarly the rotational angle of working stroke is made to increase (> 180 degree), fires to allow
Power has the more time to act on output revolving shaft, to improve the utilization rate of fuel oil and the Operating ettectiveness of engine.It can be seen that
Design of the invention corresponds to the driving groove path length of piston intake and power phase by extending, and not only increases same discharge capacity
The power of engine also improves the efficiency of engine, while also moves up the speed of engine best torque point, improves hair
Motivation best torque revolving speed, further improves engine power.
The invention has the advantages that
1. specially devising axial-rotation driving mechanism in the present invention replaces conventional crankshaft-linking rod drive mechanism, this axial rotation
Turn driving mechanism and passes through the driving trenched side-wall promotion rotary motion for being axially moved inclination closed loop design above component at work
The rolling element of component moves, and enables rotary motion component continuous rotation, so that the linear motion of piston is converted to output
The continuous rotation of shaft moves.During being somebody's turn to do, the power of piston output changes direction simply by axial-rotation driving mechanism,
And be absolutely not decomposed, seldom a part of frictional force is removed, most power are delivered to output revolving shaft output.And it is living
The starting point and end dead point area very little, most of energy for filling in acting are utilized.Therefore, from its energy for the structure of itself
Transfer efficiency is much higher than conventional crankshaft-linking rod drive mechanism.
2. the present invention can be by changing the driving groove being axially moved on component when being applied to four-stroke engine
It designs to increase charging stage corresponding rotational angle (> 180 degree) in path, it is ensured that extend under the premise of engine speed is constant
Piston downgoing time when air inlet improves engine power to enter more oil gas in cylinder.Certainly we can also pass through
Driving the optimization design (improving side wall profile line initial slope) of the side wall profile line of groove makes piston in the case where downlink initial stage accelerates
Scanning frequency degree, so that the negative pressure increased faster in cylinder in same downgoing time be made to further increase hence into more oil gas
Engine power.
3. in four impulse strokes of its piston, piston working stroke also wishes quick-fried for four-stroke engine
Power caused by firing has more time effects on piston to allow more power to pass to output shaft, and in the present invention just
The corresponding driving groove of piston working stroke driving groove corresponding with suction stroke is same section, is overlapped, therefore air inlet row
The rotational angle of journey increases (> 180 degree) and similarly the rotational angle of working stroke is made to increase (> 180 degree), thus allow fire it is dynamic
Power has the more time to act on output revolving shaft, to improve the utilization rate of fuel oil and the Operating ettectiveness of engine.It can be seen that this
The design of invention corresponds to the driving groove path length of piston intake and power phase by extending, and not only increases same discharge capacity hair
The power of motivation also improves the efficiency of engine, while also moves up the speed of engine best torque point, improves and starts
Machine best torque revolving speed, further improves engine power.
In conclusion when the same displacement engine using engine and conventionally employed crankshaft-linking rod drive mechanism of the invention
In comparison, power and efficiency are increased, and increase by 20% or more by measured power, improved efficiency 10 ~ 15% is sent out simultaneously
Motivation overall weight is also mitigated, and is mitigated up to 10% or so, volume is also smaller, and structure is more simple, and production cost is lower than
Conventional engines.
Detailed description of the invention
The invention will be further described with reference to the accompanying drawings and embodiments:
Fig. 1 is the structural schematic diagram of the invention applied when in four-stroke engine；
Fig. 2 is the core institution axial-rotation driving mechanism in the present invention and the independent assembly structure diagram (band between piston
It is axially moved component inside section view)；
Fig. 3 is the schematic perspective view of axial moving link in the present invention；
Fig. 4 is the refinement matching chart in Fig. 1 in driving mechanism for rocker arm between rocker arm and edge cam；
Fig. 5 is the actual distribution schematic diagram after the driving groove on moving link axial in Fig. 1 circumferentially face expansion in the plane；
Fig. 6 be Fig. 5 in when driving groove is non axial be staggered when expansion distribution schematic diagram；
Fig. 7 is the relational graph in the present invention between output revolving shaft rotational angle and piston trajectory curve；
Fig. 8 is the relational graph in conventional four-stroke engine between crank rotation angle and its piston trajectory curve；
Fig. 9 is that another embodiment of the present invention applies structural schematic diagram when in four-stroke engine；
Figure 10 is the independent schematic perspective view of the axial movement component in Fig. 9；
Figure 11 is the actual distribution signal after the driving groove being axially moved on component in Fig. 9 circumferentially face expansion in the plane
Figure；
Figure 12 is the refinement matching chart in Fig. 9 in driving mechanism for rocker arm between rocker arm and edge cam；
Figure 13 and Figure 14 is respectively the power with crankshaft-linking rod drive mechanism work stress conventional under the premise of displacement engine
Learn the mechanical model schematic diagram of the axial-rotation driving mechanism work stress in model schematic and the present invention；
Figure 15 is two kinds of mechanical models of Figure 13 and 14 (being 180 degree) when the angle of engine charge or acting is identical, output
Direction of rotation driving force is held to compare figure with the change curve of angle；
Figure 16 is that in engine charge or the angle difference of acting, (conventional engine remains unchanged two kinds of mechanical models of Figure 13 and 14
180 degree, and our engine is then greater than 180 degree), output end direction of rotation driving force compares figure with the change curve of angle.
Wherein: 1, engine housing；2, engine case lid；3, engine cylinder head；4, piston；5, it is axially moved component；6,
Rotary motion component；6a, attachment base；6b, fork item；7, output revolving shaft；8, groove is driven；9, rolling element；10, piston fixed link；
11, guide post；12, guide pillar support；13, sliding sleeve is slided；14, bearing；15, valve；16, rocker arm；17, camshaft；18, timing gear
Wheel；19, cam shaft gear；20, edge cam；21, cam groove；22, ball；23, valve lash adjusting screw；24, ball
Sliding block；25, valve spring；26, rocker-arm roller；801, first groove curve；802, second groove curve；901, the first rolling element
Initial position；902, the second rolling element initial position.
Specific embodiment
Embodiment 1: 1 ~ 8 a kind of specific embodiment of the invention is done specifically first with reference to the accompanying drawings of the specification
It is bright.The present invention is to provide a kind of engine-driven gearings, can be used on any Stroke Engine, such as two-stroke is started
Machine or four-stroke engine, and the present embodiment is just illustrated in case where in four-stroke engine by applying.
As shown in Figure 1, this engine-driven gearing has the engine housing 1 the same with routine techniques, engine case
Lid 2 and engine cylinder head 3,1 one end stationary engine case lid 2 of engine housing, engine cylinder head 3 is fixed on engine case lid 2
On, engine cylinder head 3 is equipped with valve 15 and controls the rocker arm 16 that valve 15 opens and closes, then it is equipped with piston 4 in cylinder head 3, and this hair
Bright core is improved design feature and is:
A kind of axial-rotation driving mechanism is specially devised, the composition of the mechanism is as follows: the axial fortune being connected with one with piston 4
Dynamic component 5 and the guiding mechanism moved in a straight line for limiting the axial movement component 5 along 4 traffic direction of piston, also have one
By the rotary motion component 6 of limitation axial movement and the output revolving shaft 7 being integrally connected with the rotary motion component 6, output revolving shaft 7
Rotation be assemblied on cabinet 1 and be axially moved component 5 and the concentric arrangement of piston 4.Further combined with shown in Fig. 1 ~ Fig. 3,
Axial moving link 5 is cylinder-like structure in the present embodiment, and rotary motion component 6 also for cylindrical structural member and is placed on axial fortune
Dynamic 5 outside of component.Driving grooves 8 on the axial movement component 5 circumferentially equipped with two inclination closed loops, and rotary motion component
The rolling element 9 cooperated with driving groove 8 is installed, by driving 8 side wall of groove and the contact of rolling element 9 with by axial fortune on 6
The straight reciprocating motion of dynamic component 5 is converted to the continuous rotation movement of rotary motion component 6.
Meanwhile needing to drive the driving mechanism of rocking motion as four-stroke engine, it is endured in the prior art using tappet
Linkage, and we cooperate axial rotary drive mechanism and specially devise a kind of driving mechanism for rocker arm in the present invention, it is specific to tie
It closes shown in Fig. 1 and Fig. 4, this driving mechanism for rocker arm has one and the camshaft 17 disposed in parallel of output revolving shaft 7, output revolving shaft 7
On be fixed with timing gears 18, and 17 one end of camshaft is fixed with the cam shaft gear 19 engaged with timing gears 18, camshaft
17 other ends are then fixed with the edge cam 20 for acting on 16 one end of rocker arm, 16 other end of rocker arm and are equipped with valve spring 25
Valve 15 offsets.As shown in figure 4, being equipped with cam groove 21 along cam curve on the edge cam 20, set in cam groove 21
There is ball 22, and one end that edge cam 20 is acted on rocker arm 16 is fixed with valve lash adjusting screw 23, the valve clearance
It adjusts 23 end of screw and is equipped with sliding slot, be embedded with the ball slider 24 to offset with ball 22 in sliding slot, ball slider 24 can be in cunning
It is free to slide in slot, while the ball slider 24 is equipped with the anticreep recess portion for accommodating ball 22.
In conjunction with shown in Fig. 1 ~ Fig. 3, it is integrally formed with piston fixed link 10 in axial movement component 5 described in the present embodiment,
The piston fixed link 10 passes through case lid 2 and is connected with piston 4；And guiding mechanism described in the present embodiment includes four and transports along piston 4
Line direction guide post 11 disposed in parallel, these guide posts 11 are centrosymmetric setting about the circle center for being axially moved component 5.And
And every 11 one end of guide post is fixed with case lid 2, and the other end is then fixed with a guide pillar support 12, cooperates on each guide post 11
It is arranged there are two sliding guide sleeve 13, these sliding guide sleeves 13, which are integrally provided on, to be axially moved on component 5.And 1 He of cabinet
It is equipped with the bearing 14 being placed on output revolving shaft 7 in guide pillar support 12, and is respectively equipped on output revolving shaft 7 and above-mentioned two side bearing
14 shaft shoulder portions to offset are to limit the axial movement of rotary motion component 6.
Rolling element 9 described in the present embodiment is idler wheel, and specifically as shown in connection with fig. 2, the pivotal axis of the idler wheel is perpendicular to driving
The floor design of groove 8, therefore the rolling surface of idler wheel contacts rolling with the two side walls of driving groove 8.
As shown in figure 3, the part of not set driving groove 8 is hollow out knot in axial movement component 5 described in the present embodiment
Structure is to mitigate weight.
The considerations of for stress balance between axial movement component 5 and rotary motion component 6 and stability, the present embodiment
Described in driving groove 8 use identical two, and this two driving grooves 8 be axially moved component 5 circumference on about
Circle center is spaced apart in angularly (180 degree), and there are two crosspoints for two driving groove 8 tools.For clear explanation and take off
The shape and the positional relationship between rolling element 9 for showing driving groove 8, by two driving grooves 8, circumferentially shape is unfolded in face for we
At plane distribution schematic diagram as shown in Figure 5.And the curve after driving groove 8 to be unfolded for wherein one is named as first groove
Curve 801, the initial position of rolling element 9 therein are named as the first rolling element initial position 901；And another driving ditch
Curve after slot 8 is unfolded is named as second groove curve 802, and the initial position of rolling element 9 therein is named as the second rolling
Body initial position 902.
And it may be noted that two driving grooves 8 and its interior rolling element 9 have displacement in the axial direction in the present embodiment,
It is staggered, design in this way has its purpose.Because if two driving groove 8 interval 180 degrees design but in the axial direction without position
It moves, then since the initial position of the rolling element 9 in driving groove 8 has to be perfectly the same, therefore in practical application, it is possible that
Rolling element 9 in each driving groove 8 at a time simultaneously by crosspoint the case where, as shown in Figure 6.At this point, 9 phase of rolling element
It being detached from when in same driving groove 8, rotary motion component 6 generates breakpoint without stress, so as to cause driving, although influencing less,
The run stability that still will cause entire axial-rotation driving mechanism, the driving groove 8 to avoid such case, therefore in this case
Optimization design as shown in Figure 5 is used with the position of rolling element 9.It is equivalent to compared to Fig. 6, Fig. 5 the first groove in Fig. 6 is bent
The translation certain distance downwards of line 801, second groove curve 802 is constant, so that the first rolling element initial position 901 and the
Two rolling element initial positions 902 are staggered in the axial direction, namely make two driving grooves 8 in the axial direction for being axially moved component 5
It is upper that there is displacement, and two rolling elements 9 are staggered in the axial direction, to avoid all rolling elements 9 while appear in friendship
On crunode.
Below we further combined with Fig. 7 and Fig. 8, the present invention is further described as follows, Fig. 7 be the present invention in output turn
Relational graph between 4 path curves of 7 rotational angle of axis and piston, abscissa are that output revolving shaft respectively corresponds four cycle engines
Machine air inlet, compression, acting and the rotational angle for being vented four-stage, also referred to as operating angle, curve are then the movement rails of piston 4
Mark, the shape with the driving groove 8 on 5 surface of axial moving link in this case is corresponding associated.And Fig. 8 is then conventional four punching
Relational graph in journey engine between crank rotation angle and its piston trajectory curve.
It is known that the existing four-stroke engine using crankshaft-linking rod drive mechanism, itself structure determine its into
Gas, compression, acting and the four-stage of exhaust stroke crankshaft operating angle be restricted to 180 degree, as shown in Figure 8.Therefore,
4 inlet period of piston and working application time are all fixed, but we can analyze out from four impulse strokes of four-stroke engine
The cylinder of same discharge capacity is in four impulse strokes, if entering more oil gas or working application time lengthening in cylinder body can make to send out
Motivation is more powerful, and people can only be by way of shifting to an earlier date open time delay and turning off inlet valve in existing crankshaft-link rod engine
More oil gas are allowed to enter cylinder body as far as possible, but the present invention can by the path design for the driving groove 8 being axially moved on component 5
Increase charging stage corresponding rotational angle (> 180 degree), as shown in Figure 7, it is ensured that extend under the premise of engine speed is constant
4 downgoing time of piston when air inlet improves engine power to enter more oil gas in cylinder.
Meanwhile for four-stroke engine, in four impulse strokes of its piston 4,4 working stroke of piston is also wished
Power caused by detonation is hoped there are more time effects on piston 4 to allow more power to pass to output revolving shaft 7, the present invention
In just the corresponding driving groove 8 of piston 5 working stroke driving groove 8 corresponding with suction stroke be same section, overlap,
Therefore the rotational angle of suction stroke increase (> 180 degree) similarly makes the rotational angle of working stroke increase (> 180 degree), referring to
Shown in Fig. 7, there is the more time to act on output revolving shaft 7 to allow and fire power, to improve the utilization rate and engine of fuel oil
Operating ettectiveness, and then improve generating efficiency.It can be seen that design of the invention is by extending corresponding 4 air inlet of piston and acting
8 path length of driving groove in stage, not only increases the power of same displacement engine, also improves the efficiency of engine, together
When also move up the speed of engine best torque point, improve engine best torque revolving speed, further improve engine
Power.
And the two sidewalls of rolling element 9 and same section of driving groove 8 when in the present invention due to 4 air inlet of piston and power phase
Contact rolls respectively, and we are further by the difference of the two sidewalls profile wire shaped design of this section driving groove 8, and correspond to
The side wall profile line that the initial slope of the side wall profile line of 4 charging stage of piston is greater than corresponding 4 power phase of piston is initially oblique
Degree, so that the downstream rate at 4 downlink initial stage of piston is accelerated, as shown in Figure 7 (in same operating angle, initial stage charging stage
4 running track gradient of piston is greater than power phase, it means that its speed is accelerated) so that in same downgoing time faster
Increase cylinder in negative pressure enter more oil gas, further increase engine power.
Embodiment 2: in conjunction with shown in Fig. 9 ~ 12, the overall structure of present invention another kind specific embodiment is basic with embodiment 1
It is identical, and distinctive points are: the design of the axial movement component 5 in axially driving rotating mechanism is on the one hand changed, by its table
Two of face driving grooves 8 relationship is from the circumferencial direction interval 180 degree in embodiment 1 and cross-over design has been changed to along axial fortune
The axial of dynamic component 5 is distributed and does not intersect, i.e., without crosspoint between two driving grooves 8, but two driving grooves 8 are still opposite
In the circle center's interval 180 degree for being axially moved component 5.11 quantity of guide post is still four simultaneously, and still about axial fortune
The circle center of dynamic component 5 is centrosymmetric setting, and the corresponding sliding guide sleeve 13 being axially moved in component 5 is also four.Rotation
Turn the rolling element 9 on moving link 6 and then correspond to two driving groove 8 redistributions, and necessarily is in two driving grooves 8
Same position.Equally two driving grooves 8 circumferentially are unfolded to form plane distribution schematic diagram as shown in figure 11 in face by we, can
With 802 nothing of first groove curve 801 and second groove curve being clearly seen that after two driving corresponding expansion of groove 8
Crosspoint, and initial position 901, the 902 same positions in respective groove curve of corresponding two rolling elements 9 therein
It sets, design in this way occurs without having to worry about rolling element 9 while the case where passing through crosspoint.
On the other hand the present embodiment has also carried out small improvement for driving mechanism for rocker arm, eliminate convex in embodiment 1
The design of groove 21, ball 22 and ball slider 24 is taken turns, specifically combines shown in Figure 12, acts on end in the present embodiment on rocker arm 16
One end of face cam 20 is equipped with the rocker-arm roller 26 contacted with the surface of edge cam 20, and is fixed on 16 other end of rocker arm
Valve lash adjusting screw 23, and offseted by the valve lash adjusting screw 23 with the valve 15.
Remaining assembling structure of the present embodiment is with embodiment 1, and working principle and implementation result are also referring to embodiment 1.
We carry out comparison with the axial-rotation driving in the present invention under the premise of displacement engine in conjunction with Figure 13 ~ Figure 16 below
The acting situation of mechanism and conventional crankshaft-linking rod drive mechanism.
Figure 13 and Figure 14 is respectively with crankshaft-linking rod drive mechanism work stress conventional under the premise of displacement engine
Mechanical model schematic diagram and the present invention in axial-rotation driving mechanism work stress mechanical model schematic diagram.Figure 13
The power of piston output is represented with the P in Figure 14, F then represents the direction of rotation driving force of two mechanical model output ends.Its
F in middle Figure 13 is the component that P is acted on crankshaft, and the F in Figure 14 is then that the rubbed power of P is lost and after conversion direction
Act on the power on output revolving shaft.
It is (equal when the angle of engine charge or acting is identical that two kinds of mechanical models of Figure 13 and 14 are shown in conjunction with Figure 15
For 180 degree), output end direction of rotation driving force compares figure with the change curve of angle；Abscissa T indicates air inlet or acting in figure
The angle change of stroke.A curve represent the output end direction of rotation driving force of conventional crankshaft-linking rod drive mechanism mechanical model with
The change curve of angle, and B curve then represents the output end direction of rotation of the axial-rotation driving mechanism mechanical model in this case
Driving force with angle change curve.Ordinate F then indicates the size of the output end direction of rotation driving force of two kinds of mechanical models,
Wherein Fmax1 is the maximum value in the F change procedure of conventional crankshaft-linking rod drive mechanism mechanical model, and Fmax2 is this case
Maximum value in the F change procedure of axial-rotation driving mechanism mechanical model.The F affirmative of two kinds of mechanical models is equal as we know from the figure
Less than P, and Fmax2 > Fmax1.Simultaneously it will be apparent that under each angle the F of conventional crankshaft-link rod driving mechanism mechanical model stabilization
Property and retentivity also all be not so good as this case.Curve can be characterized as corresponding mechanical model rotation side to the graphics area that abscissa surrounds
To the acting size of driving force, (in the case that radius of turn is equal, abscissa is equally represented by the driving of direction of rotation
The distance S that power is passed by), it is upper from figure it is clear that curve B total acting is higher than curve A in identical working stroke.
Figure 16 be two kinds of mechanical models of Figure 13 and 14 in engine charge or the angle difference of acting (conventional engine according to
Old 180 degree, and our engine is then greater than 180 degree), output end direction of rotation driving force compares with the change curve of angle
Figure.The same with Figure 15, abscissa T, which remains unchanged, in figure indicates the angle change of air inlet or working stroke.A curve represents conventional crankshaft and connects
The output end direction of rotation driving force of bar transmission mechanism mechanics model is with the change curve of angle, and B curve then represents in this case
Axial-rotation driving mechanism mechanical model output end direction of rotation driving force with angle change curve.Ordinate F then table
Show the size of the output end direction of rotation driving force of two kinds of mechanical models, wherein Fmax1 is conventional crankshaft-linking rod drive mechanism power
The maximum value in the F change procedure of model is learned, and the F that Fmax2 is the axial-rotation driving mechanism mechanical model of this case changed
Maximum value in journey.The F of two kinds of mechanical models is respectively less than P, and Fmax2 > Fmax1 certainly as we know from the figure.While it will be apparent that
The stability of the F of conventional crankshaft-link rod driving mechanism mechanical model and retentivity are also all not so good as this case under each angle.Curve and cross
The graphics area that coordinate surrounds can be characterized as the acting size (radius of turn of corresponding mechanical model direction of rotation driving force
In the case where equal, abscissa is equally represented by the distance S that the driving force of direction of rotation is passed by), it can understand from figure
Out, since the acting angle of this case increases, the driving force time acted on output revolving shaft is longer, and work distance is also longer, therefore
Curve B total acting is much higher than curve A.
Actually two curves A and B can also regard the energy conversion efficiency curve of corresponding respective mechanical model as, from figure
It is shown in 15 and Figure 16 and in conjunction with the energy conversion efficiency that analysis above can specify the axial-rotation driving mechanism in this case
Much higher than conventional crankshaft-linking rod drive mechanism, the power and efficiency of corresponding engine are also higher.
Certainly the above embodiments merely illustrate the technical concept and features of the present invention, and its object is to allow be familiar with technique
People can understand the content of the present invention and implement it accordingly, it is not intended to limit the scope of the present invention.It is all according to this hair
The modification that the Spirit Essence of bright main technical schemes is done, should be covered by the protection scope of the present invention.
Claims (10)
1. a kind of engine-driven gearing, including engine housing (1), the engine case lid being fixed on engine housing (1)
(2) and the engine cylinder head (3) that is fixed on engine case lid (2) piston (4), are equipped in engine cylinder head (3), feature exists
In further including axial-rotation driving mechanism, the mechanism is including an axial movement component (5) being connected with piston (4) and for limiting
What the guiding mechanism and one that the axial movement component (5) is moved in a straight line along piston (4) traffic direction were axially moved by limitation
Rotary motion component (6) and output revolving shaft (7) that is fixed with the rotary motion component (6) or being integrally connected, output revolving shaft (7) rotation
Turn to be assemblied on engine housing (1) and with piston (4) is concentric or parallel arrangement, being axially moved component (5) is cylindric knot
Structure, and rotary motion component (6) is nested with and is being axially moved on the outside of component (5) or is protruding into axial movement component (5) inside, it is axial to transport
The driving groove (8) of at least one inclination closed loop is circumferentially equipped on dynamic component (5), and be equipped on rotary motion component (6) with
The rolling element (9) for driving groove (8) cooperation, by driving groove (8) side wall with the contact of rolling element (9) structure will be axially moved
The straight reciprocating motion of part (5) is converted to the continuous rotation movement of rotary motion component (6).
2. a kind of engine-driven gearing according to claim 1, it is characterised in that the driving groove (8) is identical
Two or more, the axial of component (5) is arranged without intersecting axially movable for these drivings groove (8), phase between driving groove (8)
To the circle center's interval any angle for being axially moved component (5)；Or the driving groove (8) is identical two or more,
These drivings groove (8) relative circumferential center interval angles on the circumference for being axially moved component (5) are arranged and intersect, and in axis
Nothing is staggered upwards；Or the driving groove (8) is identical two or more, these drivings groove (8) are being axially moved component
(5) relative circumferential center interval angles are arranged and intersect on circumference, and are staggered in the axial direction.
3. a kind of engine-driven gearing according to claim 1, it is characterised in that the engine is four cycle engines
When machine, the rotational angle that piston (4) air inlet and power phase often walk the corresponding rotary motion component (6) of a stroke is all larger than
180 degree, so as to the air inlet and working application time of oversize piston (4).
4. a kind of engine-driven gearing according to claim 3, it is characterised in that when piston (4) air inlet and power phase
Rolling element contacts rolling with the two sidewalls of (9) same section of driving groove (8) respectively, which drives the two sidewalls profile of groove (8)
Wire shaped is different, and the initial slope of the side wall profile line of corresponding piston (4) charging stage is greater than corresponding piston (4) acting
The side wall profile line initial slope in stage, to accelerate the downstream rate at piston (4) downlink initial stage, so that in same downgoing time
The negative pressure increased in cylinder faster enters more oil gas.
5. a kind of engine-driven gearing according to claim 1 or 2 or 3 or 4, it is characterised in that the rolling element (9)
To be mounted on the spherical rolling body on rotary motion component (6) by universal joint.
6. a kind of engine-driven gearing according to claim 1 or 2 or 3 or 4, it is characterised in that the rolling element (9)
Rolling surface for idler wheel, the idler wheel contacts rolling with the two side walls of driving groove (8).
7. a kind of engine-driven gearing according to claim 1, it is characterised in that one on the axial movement component (5)
Body is equipped with piston fixed link (10), which passes through engine case lid (2) and be connected with piston (4), the output
Shaft (7) is axially moved component (5) and piston (4) concentric arrangement；And the guiding mechanism includes several along piston (4) fortune
Line direction guide post disposed in parallel (11), guide post (11) one end is fixed with engine case lid (2), and the other end is then led with one
Column holder (12) is fixed, and equal engagement sleeves are equipped with sliding guide sleeve (13) on each guide post (11), these sliding guide sleeves (13) are fixed
Or it is integrally provided on and is axially moved on component (5)；And be equipped in the engine housing (1) and guide pillar support (12) be placed on it is defeated
Bearing (14) in shaft (7) out, and be respectively equipped on output revolving shaft (7) shaft shoulder portion that offsets with above-mentioned two side bearing (14) with
It limits to be equipped in the axial movement or engine housing (1) of rotary motion component (6) from both ends and supports only rotary motion component
(6) limiting bracket is to limit the axial movements of rotary motion component (6).
8. a kind of engine-driven gearing described according to claim 1 or 2 or 7, it is characterised in that the axial movement component
(5) part of not set driving groove (8) is engraved structure to mitigate weight on.
9. a kind of engine-driven gearing according to claim 1 or 2 or 7, it is characterised in that the rotary motion component
It (6) is cylindrical structural member or fork member, fork member includes the company fixed or be integrally connected for same output revolving shaft (7)
Joint chair, the attachment base are equipped with the fork item extended along piston (4) direction of motion, and rolling element (9) is mounted on fork item, and when fork item
Quantity when being more than two, these fork items are centrosymmetric distribution about the center of rotation of rotary motion component (6).
10. a kind of engine-driven gearing according to claim 7, it is characterised in that the guide post (11) is about axial fortune
The circle center of dynamic component (5) is centrosymmetric setting.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811160584.3A CN109184900B (en) | 2018-09-30 | 2018-09-30 | Engine transmission device |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811160584.3A CN109184900B (en) | 2018-09-30 | 2018-09-30 | Engine transmission device |
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| CN109184900A true CN109184900A (en) | 2019-01-11 |
| CN109184900B CN109184900B (en) | 2024-01-30 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201811160584.3A Active CN109184900B (en) | 2018-09-30 | 2018-09-30 | Engine transmission device |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110159423A (en) * | 2019-05-10 | 2019-08-23 | 王志伟 | A kind of quartastroke engine cylinder |
| CN116901718A (en) * | 2023-08-30 | 2023-10-20 | 青岛海通制动器有限公司 | Automobile braking system with energy recovery function |
| CN120447462A (en) * | 2025-07-09 | 2025-08-08 | 中国航发湖南动力机械研究所 | Turboprop engine dual-rod timing coordinated control and disturbance-free switching system and method |
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| CN2177808Y (en) * | 1993-11-12 | 1994-09-21 | 王关林 | Double-piston transmission device |
| CN1173215A (en) * | 1994-12-02 | 1998-02-11 | 先进引擎技术有限公司 | Axial piston rotary engine |
| BG105976A (en) * | 2001-10-04 | 2002-02-28 | СТОЯНОВ Добромир | Satellite inertia module and stageless automatic transmission to it |
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| CN120447462A (en) * | 2025-07-09 | 2025-08-08 | 中国航发湖南动力机械研究所 | Turboprop engine dual-rod timing coordinated control and disturbance-free switching system and method |
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| CN109184900B (en) | 2024-01-30 |
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