CN200975266Y - Four-stroke engine variable stroke engines - Google Patents
Four-stroke engine variable stroke engines Download PDFInfo
- Publication number
- CN200975266Y CN200975266Y CNU2006201347477U CN200620134747U CN200975266Y CN 200975266 Y CN200975266 Y CN 200975266Y CN U2006201347477 U CNU2006201347477 U CN U2006201347477U CN 200620134747 U CN200620134747 U CN 200620134747U CN 200975266 Y CN200975266 Y CN 200975266Y
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- China
- Prior art keywords
- bent axle
- running shaft
- connecting rod
- transmission device
- camshaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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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
- F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
- F02B41/02—Engines with prolonged expansion
- F02B41/04—Engines with prolonged expansion in main cylinders
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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
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/048—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable crank stroke length
Abstract
A stroke-variable engine includes a pivot shaft which is rotatably supported in a crankcase so as to be rotatable about an eccentric axis parallel to a crankshaft and which is connected to a control rod so that a rotational power reduced at a reduction ratio of 1/2 is transmitted from the crankshaft to the pivot shaft. Acamshaftof a valve-operatingmechanismmounted at an upper portion of an engine body and the pivot shaft are operatively connected to each other. Thus, it is possible to decrease the number of parts of the valve-operating mechanism, increase a rotational speed, and further reduce mechanical noise.
Description
Technical field
The utility model relates to variable stroke engine, particularly, relates to a kind of like this variable stroke engine, and it has: master connecting rod, and the one end is connected on the piston by wrist pin; Slave connecting rod, it is connected on the crankpin of bent axle, simultaneously, is connected to the other end of above-mentioned master connecting rod, and described crankshaft rotating freely is bearing on the crankcase of engine main body; Controlling rod, the one end is being connected on the position of the link position that departs from above-mentioned master connecting rod on the above-mentioned slave connecting rod; And pivot, it is connected to the other end of above-mentioned controlling rod, can be around the eccentric axis parallel rotation, and rotation freely is bearing on the above-mentioned crankcase with above-mentioned bent axle, simultaneously, transmit the power after slowing down by 1/2 reduction speed ratio from above-mentioned bent axle.
Background technique
In the past, this variable stroke engine is for example known for everyone in TOHKEMY 2003-314237 communique etc., one end of controlling rod is connected on the slave connecting rod, be connected on this pivot by the other end this controlling rod, thereby stroke of piston is changed, and described pivot is set on the running shaft with axis parallel with bent axle.
; in the disclosed variable stroke engine of above-mentioned TOHKEMY 2003-314237 communique; valve actuating gear constitutes and makes running shaft be also used as OHV (overhead valve) type of camshaft; when using this OHV type valve actuating gear; not only the number that constitutes the component of valve actuating gear such as push rod becomes many; and because valve actuating gear forms bigger weight; therefore be difficult to realize high rotating speedization; and; because the contact position between the component of formation valve actuating gear is more; so it is bigger that mechanical noise becomes.
The model utility content
The utility model is finished in view of above-mentioned condition, and purpose is to provide a kind of variable stroke engine, and it can reduce the component number of valve actuating gear, simultaneously, can realize high rotating speedization, and then also can reduce mechanical noise.
For reaching such purpose, of the present utility model first is characterised in that in variable stroke engine, to have: master connecting rod, and the one end is connected on the piston by wrist pin; Slave connecting rod, it is connected on the crankpin of bent axle, simultaneously, is connected to the other end of above-mentioned master connecting rod, and this crankshaft rotating freely is bearing on the crankcase of engine main body; Controlling rod, the one end is being connected on the position of the link position that departs from above-mentioned master connecting rod on the above-mentioned slave connecting rod; And pivot, it can be around the eccentric axis rotation parallel with above-mentioned bent axle, and rotation freely is bearing on the above-mentioned crankcase, simultaneously, be connected to the other end of above-mentioned controlling rod, rotating power after transmission is slowed down by 1/2 reduction speed ratio from above-mentioned bent axle, in this variable stroke engine, the camshaft that valve actuating gear had that is arranged on engine main body top links with above-mentioned pivot and is connected.
Structure according to the 1st such feature, because valve actuating gear constitutes OHC (overhead camshaft) type, therefore, the component number that constitutes valve actuating gear is reduced, by making valve actuating gear form lighter weight, just can realize high rotating speedization easily, and, by the contact position between the component that constitute valve actuating gear is reduced, can reduce mechanical noise.
In addition, the 2nd feature of the present utility model is on the basis of the structure of above-mentioned the 1st feature, above-mentioned pivot is a spin axis with above-mentioned eccentric axis, rotation freely is bearing on the above-mentioned crankcase, simultaneously, be arranged on the eccentric position of running shaft, rotating power after this running shaft transmission is slowed down by 1/2 reduction speed ratio from above-mentioned bent axle, between above-mentioned camshaft and above-mentioned running shaft, the timing transmission device is set, this timing transmission device is made of following part: follower, and it is arranged on the above-mentioned camshaft; Driving wheel, it is arranged on the above-mentioned running shaft; And annular driving band, it is wound on this driving wheel and the above-mentioned follower.
Structure according to the 2nd such feature, the timing transmission device is used for the rotating power that is decelerated after 1/2 from bent axle is delivered to the camshaft that valve actuating gear has, because this timing transmission device is set between the running shaft and camshaft of the rotating power of transmission behind the crankshaft deceleration 1/2, therefore, the follower miniaturization that is arranged on the camshaft can be made, the miniaturization on engine main body top can be realized.And, owing to be provided with on the running shaft of pivot, only effect has the component of the explosive force that bent axle bears by master connecting rod and slave connecting rod, therefore, can set the diameter of axle of running shaft littler than the diameter of axle of bent axle, compare with the situation that driving wheel is set on bent axle, can make the diameter pathization of driving wheel, corresponding therewith, also can make the diameter pathization of follower, can constitute the timing transmission device more compactly, not only make engine main body top, and make its integral miniaturization, can improve the installation that is installed on working machine etc.And, when the driving wheel diameter is too small, the winding radius of annular driving band diminishes, flexural load increases, on durability, have problems, but by on 1/2 the running shaft of slowing down, driving wheel being set, the diameter of driving wheel can be set in the suitable scope, can improve the durability of annular driving band.
The 3rd feature of the present utility model is on the basis of the structure of above-mentioned the 2nd feature, the running shaft drive unit will be delivered on the above-mentioned running shaft from the rotating power deceleration 1/2 of above-mentioned bent axle, and this running shaft drive unit and above-mentioned timing transmission device are separated to be configured in the two axial outsides of above-mentioned crankpin.
Structure according to the 3rd such feature, will be from the rotating power of bent axle 1/2 running shaft drive unit and timing transmission device separate configuration the two axial outsides of slowing down at crankpin, because the component of the explosive force that bent axle bears acts on the substantial middle portion of running shaft, therefore, can be with the distance setting between the bearing at the two end part of bent axle and running shaft for impartial substantially, can improve the durability of running shaft, simultaneously, can make the axial load that acts on rotating shaft terminal portion impartial substantially, can make the two supports portion miniaturization of running shaft.
The 4th feature of the present utility model is on the basis of the structure of above-mentioned the 2nd feature, box main body that above-mentioned crankcase is opened wide by a side and the side cover that is attached to the open end of this box main body constitute, the running shaft drive unit will be delivered on the above-mentioned running shaft from the rotating power deceleration 1/2 of above-mentioned bent axle, for this running shaft drive unit and above-mentioned timing transmission device, above-mentioned timing transmission device is formed on above-mentioned side cover side and is configured between above-mentioned crankpin and the above-mentioned side cover.
Structure according to the 4th such feature, because between the crankpin and side cover of bent axle, set timing transmission device and running shaft drive unit successively from the side cover side, therefore, the driving wheel of timing being adjusted necessary timing transmission device is as the side cover side, easy visual timing marks, simultaneously, also be rotated the assembling of axial brake device easily, can improve assembling.
The 5th feature of the present utility model is on the basis of any one structure of above-mentioned the 2nd～the 4th feature, and above-mentioned bent axle has a pair of counterweight, and they are from the above-mentioned slave connecting rod of sandwich.According to this structure,, therefore, can make the power that acts on the bent axle obtain good balance because bent axle has a pair of counterweight that is configured in the slave connecting rod both sides.
The 6th feature of the present utility model is provided with the timing transmission device between above-mentioned camshaft and above-mentioned bent axle on the basis of the structure of above-mentioned the 1st feature, this timing transmission device transmits the rotating power of this bent axle by 1/2 reduction speed ratio.Above-mentioned pivot is set on above-mentioned camshaft, and this pivot has from the axis of the spin axis off-centre of described camshaft.
Structure according to the 6th such feature, by the timing transmission device, rotating power after will slowing down by 1/2 reduction speed ratio from bent axle is delivered on the camshaft that valve actuating gear had that is arranged at engine main body top, but because this camshaft is provided with pivot, therefore, being rotated situation about freely being bearing on the crankcase with the running shaft with pivot compares, do not need to guarantee to be used to dispose the space of running shaft, can realize the miniaturization of crankcase, simultaneously, can must be lower with the motor height setting, and, owing between running shaft and bent axle, do not need to be provided for the deceleration mechanism of rotary driving axle, therefore, the axial length of bent axle can be shortened, the integral miniaturization of motor can be made.In addition, owing to do not need running shaft, therefore can reduce the component number.In addition, controlling rod forms, between the bottom of engine main body and top, has long length, but by reduce controlling rod with the oscillating quantity at the tie point place of slave connecting rod, can suppress wearing and tearing, and, just play the effect of counterweight because of becoming than the long controlling rod that weighs that becomes, thereby can make bent axle obtain good dynamic balancing.
And then, the 7th feature of the present utility model is on the basis of the structure of above-mentioned the 6th feature, the center line of above-mentioned master connecting rod and above-mentioned controlling rod is configured at grade, according to this structure, can be along on the direction of the axis of bent axle, dispose master connecting rod, slave connecting rod and controlling rod compactly, can shorten the distance between the two end part bearing of bent axle.And then, move to crankshaft side by making controlling rod, the load that acts on master connecting rod and the slave connecting rod that is caused by explosive force is reduced.
For above-mentioned in the utility model and other purpose, feature and advantage, can be clear from the explanation of the following preferred embodiment that is described in detail with reference to the accompanying drawings.
Description of drawings
Fig. 1 and Fig. 2 represent the 1st embodiment of the present utility model, and Fig. 1 is the vertical profile profile of the side of motor, are the sectional drawings along the 1-1 line of Fig. 2, and Fig. 2 is the sectional drawing along the 2-2 line of Fig. 1.
Fig. 3 is the 2nd embodiment's of the present utility model sectional drawing corresponding to Fig. 2.
Fig. 4 and Fig. 5 represent the 3rd embodiment of the present utility model, and Fig. 4 is the vertical profile profile of motor, are the sectional drawings along the 4-4 line of Fig. 5, and Fig. 5 is the sectional drawing along the 5-5 line of Fig. 4.
Embodiment
See figures.1.and.2 on one side, on one side the 1st embodiment of the present utility model is described, this motor for example is the air-cooling type single-cylinder engine that utilizes in working machine etc., engine main body 21 is made of following part: crankcase 22; Cylinder block 23, its side from this crankcase 22 is inclined upwardly outstanding slightly; And cylinder head 24, it is bonded on the head of this cylinder block 23, on the outer side surface of cylinder block 23 and cylinder head 24, is provided with a plurality of air coolings radiating fin 23a ..., 24a ...In addition, crankcase 22 utilizes the attachment face 22a below this crankcase 22, is installed on the engine framework of various working machines.
Crankcase 22 is made of following part: box main body 25, and itself and cylinder block 23 are integrally cast into type, and a side is opened wide; Side cover 26, it is attached to the open end of this box main body 25.Bent axle 27 has a pair of counterweight 27a, 27b integratedly and connects crankpin 27c between two counterweight 27a, 27b, and described bent axle 27 rotations freely are bearing on above-mentioned box main body 25 and the side cover 26.
Be formed with cylinder barrel 29 in cylinder block 23, this cylinder barrel 29 is entrenched in wherein with making piston 28 free slidings, and the firing chamber 30 of facing piston 28 tops is formed between cylinder block 23 and the cylinder head 24.In addition, on cylinder head 24, suction port 31 and relief opening 32 that formation can be communicated with firing chamber 30, simultaneously, set the intake valve 33 and the exhaust valve 34 that can carry out on-off action, open and close between 33 pairs of suction ports 31 of described intake valve and the firing chamber 30, open and close between 34 pairs of relief openings 32 of described exhaust valve and the firing chamber 30.
The valve actuating gear 35 that intake valve 33 and exhaust valve 34 is carried out driven for opening and closing has: camshaft 36, and its reduction speed ratio with 1/2 is driven by bent axle 27 rotations; Air inlet side cam 37 and exhaust side cams 38, they are fixed on the camshaft 36, with these camshaft 36 rotations; And air inlet side and exhaust side rocking arm 39,40 driven with these cams 37,38 and that swing.This valve actuating gear 35 is set at the top of engine main body 21, one end of air inlet side and exhaust side rocking arm 39,40 is by shared swing fulcrum 41, swing freely is bearing on the cylinder head 24, described swing fulcrum 41 has the axis parallel with bent axle 27, the upper end portion butt of tappet screw 42,43 and intake valve 33 and exhaust valve 34 screws to described tappet screw 42,43 can regulate advance and retreat position the other end at air inlet side and exhaust side rocking arm 39,40.
Above-mentioned camshaft 36 has the axis parallel with bent axle 27, is rotated freely to be bearing on the cylinder head 24, and the embedded hole 44 that is used to this camshaft 36 is embedded is arranged in a side upper shed of cylinder head 24.Then, valve actuating gear 35 is covered by valve mechanism cover 45, and valve mechanism cover 45 is attached on the cylinder head 24, has the cap 45a of the outer end of stopping up above-mentioned embedded hole 44, breaks away from from embedded hole 44 to stop described camshaft 36.
The two end part rotation of running shaft 46 freely is bearing on the box main body 25 and side cover 26 of above-mentioned crankcase 22, this running shaft 46 has the axis parallel with bent axle 27, simultaneously, has the spin axis that more leans on the top than the axis of bent axle 27, between this running shaft 46 and bent axle 27, be provided with running shaft drive unit 47A, be delivered on the running shaft 46 after the rotating power deceleration 1/2 of this running shaft drive unit 47A with bent axle 27.On the other hand, be provided with timing transmission device 50 between the camshaft 36 of valve actuating gear 35 and running shaft 46, this timing transmission device 50 does not slow down to the rotating power of running shaft 46 and is directly delivered on the camshaft 36.And, running shaft drive unit 47A and timing transmission device 50 are separated to be provided in the two axial outsides of the crankpin 27c of bent axle 27, because crankpin 27c is set between a pair of counterweight 27a, the 27b, so running shaft drive unit 47A and timing transmission device 50 just are provided in two outsides that are arranged at a pair of counterweight 27a, 27b on the bent axle 27.
Above-mentioned running shaft drive unit 47A is by the actuation gear 48A that is fixed on the bent axle 27, and be arranged on integratedly on the running shaft 46 and constitute with the driven gear 49A of this actuation gear 48A engagement, actuation gear 48A is fixed on the bent axle 27, and in a pair of counterweight 27a, 27b that bent axle 27 is had, with the opposite side closed end of the counterweight 27b of side cover 26 opposite sides and box main body 25 between, driven gear 49A is corresponding with actuation gear 48A, is formed on the running shaft 46.
In addition, timing transmission device 50 is configured between the counterweight 27a and side cover 26 among a pair of counterweight 27a, the 27b that bent axle 27 had, side cover 26 sides, this timing transmission device 50 is made of following part: be fixed on the running shaft 46, as the driving sprocket wheel 51 of driving wheel; Be arranged on the above-mentioned camshaft 36, as the driven sprocket 52 of follower; And be wound on driving sprocket wheel 51 and the driven sprocket 52, as the timing cingulum 53 of annular driving band.In addition, form timing belt chamber 54 in cylinder block 23 and cylinder head 24, this timing belt chamber 54 is moved timing cingulum 53 therein.
With a pair of counterweight 27a, 27b that above-mentioned bent axle 27 is had between corresponding position, on above-mentioned running shaft 46, be provided with pivot 55 integratedly, the eccentric axis setting of the axis of this pivot 55 and this running shaft 46, this pivot 55, piston 28 and bent axle 27 couple together by linkage mechanism 58.
This linkage mechanism 58 is made of following part: master connecting rod 60, and the one end is connected on the piston 28 by wrist pin 59; Slave connecting rod 61, it is configured between two counterweight 27a, the 27b of bent axle 27, is connected on the crankpin 27c, simultaneously, is connected to the other end of master connecting rod 60; And controlling rod 62, the one end is being connected on the position of the link position that departs from master connecting rod 60 on the slave connecting rod 61, and simultaneously, the other end is connected on the above-mentioned pivot 55.
The other end of master connecting rod 60 is pivotally connected to an end of slave connecting rod 61 by the 1st pin 64.One end of controlling rod 62 is pivotally connected on the slave connecting rod 61 by the 2nd pin 65, be provided with circular axis hole 66 in the other end of controlling rod 62, but this axis hole 66 is entrenched in wherein with making above-mentioned pivot 55 slide relative.
So, rotation corresponding to bent axle 27, running shaft 46 is driven in rotation with 1/2 reduction speed ratio, follow the spin axis rotation of pivot 55 around running shaft 46, linkage mechanism 58 is so that the stroke of the piston in expansion stroke 28 moves than the big mode of stroke in compression stroke, thereby, can carry out bigger expansion work with same suction air-fuel mixture amount, can improve thermal efficiency of cycle.
Below, effect to the 1st embodiment describes, being arranged on the camshaft 36 that the valve actuating gear 35 on engine main body 21 tops had is connected on the pivot 55 by timing transmission device 50, because valve actuating gear 35 constitutes the OHC type, therefore, can reduce the component number that constitutes valve actuating gear 35, by making valve actuating gear 35 form lighter weight, just can realize high rotating speedization easily, and, by the contact position between the component that constitute valve actuating gear 35 is reduced, can reduce mechanical noise.
In addition, above-mentioned pivot 55 is set at the eccentric position of running shaft 46, this running shaft 46 transmits from bent axle 27 and is decelerated rotating power after 1/2, timing transmission device 50 is by the driven sprocket 52 that is arranged on the above-mentioned camshaft 36, the timing cingulum 53 that is arranged on the driving sprocket wheel 51 on the above-mentioned running shaft 46 and is wound on this driving sprocket wheel 51 and the above-mentioned driven sprocket 52 constitutes, this timing transmission device 50 transmits the rotating power after 1/2 of being decelerated from bent axle 27, because this timing transmission device 50 is arranged between running shaft 46 and the camshaft 36, therefore, driven sprocket 52 miniaturizations that are arranged on the camshaft 36 can be made, the top miniaturization of engine main body 21 can be made.And, on the running shaft 46 that is provided with pivot 55, only effect has the component of the explosive force that bent axle 27 bears by master connecting rod 60 and slave connecting rod 61, therefore, can set the diameter of axle of running shaft 46 littler than the diameter of axle of bent axle 27, compare with the situation that driving sprocket wheel is set on bent axle 27, can make the diameter pathization of driving sprocket wheel 51, corresponding therewith, also can make the diameter pathization of driven sprocket 52, can make the structure of timing transmission device 50 compact more, not only make engine main body top, and make its integral miniaturization, can improve the installation that is installed on working machine etc.
And, when the diameter of driving sprocket wheel 51 is too small, the winding radius of timing cingulum 53 diminishes, flexural load increases, on durability, have problems, but by on 1/2 the running shaft 46 of slowing down, driving sprocket wheel 51 being set, the diameter of driving sprocket wheel 51 can be set in the suitable scope, can improve the durability of timing cingulum 53.
In addition, be configured to than the axis of bent axle 27 more by the top by spin axis with running shaft 46, just can must be shorter with the distance setting between driving sprocket wheel 51 and the driven sprocket 52, can shorten the length of timing cingulum 53.
In addition, to slow down from the rotating power of bent axle 27 and 1/2 be delivered to the two axial outsides that running shaft drive unit 47A on the running shaft 46 and timing transmission device 50 are separated to be configured in crankpin 27c, the component of the explosive force that bent axle 27 is born acts on the substantial middle portion of running shaft 46, therefore, can be with the distance setting between the bearing at the two end part of bent axle 27 and running shaft 46 for impartial substantially, can improve the durability of running shaft 46, simultaneously, can make the axial load that acts on running shaft 46 two end part impartial substantially, can make the two supports portion miniaturization of running shaft 46.
In addition, because the driving sprocket wheel 51 of necessary timing transmission device 50 is adjusted in timing, be arranged on the running shaft 46, and between the counterweight 27a and side cover 26 in a pair of counterweight 27a, 27b that bent axle 27 is had, side cover 26 sides, therefore, easy visual timing marks can improve assembling.
And, because bent axle 27 has a pair of counterweight 27a, the 27b that is configured in slave connecting rod 61 both sides, therefore, can make the power that acts on the bent axle 27 obtain good balance.
Fig. 3 represents the 2nd embodiment of the present utility model, the part corresponding with above-mentioned the 1st embodiment is given same as label, and only illustrates and omits its detailed description.
Will from the rotating power of bent axle 27 slow down 1/2 be delivered to running shaft 46 ' on running shaft drive unit 47B constitute by following part: be fixed on the actuation gear 48B on the bent axle 27; And be arranged on integratedly running shaft 46 ' on, driven gear 49B with this actuation gear 48B engagement, actuation gear 48B is fixed on the bent axle 27, and between crankpin 27c and side cover 26 that bent axle 27 is had, because the two ends of crankpin 27c connect a pair of counterweight 27a, 27b, therefore, between the counterweight 27a and side cover 26 of side cover 26 sides of actuation gear 48B in two counterweight 27a, 27b, be fixed on the bent axle 27.
And, the camshaft 36 of valve actuating gear 35 and running shaft 46 ' between, be provided with timing transmission device 50, this timing transmission device 50 is configured between the counterweight 27a and side cover 26 of side cover 26 sides among above-mentioned two counterweight 27a, the 27b, this timing transmission device 50 is made of following part: driving sprocket wheel 51, its be fixed on running shaft 46 ' on; Driven sprocket 52, it is arranged on the camshaft 36; And timing cingulum 53, it is wound on driving sprocket wheel 51 and the driven sprocket 52.
That is, between running shaft drive unit 47B and timing transmission device 50 are configured in crankpin 27c one end is connected the counterweight 27a and side cover 26, and above-mentioned timing transmission device 50 is configured in more close side cover 26 sides than running shaft drive unit 47B.
According to the 2nd embodiment, the driving sprocket wheel 51 of timing being adjusted necessary timing transmission device 50 is configured in side cover 26 sides, and easy visual timing marks simultaneously, also assembles running shaft drive unit 47B easily, can improve assembling.
With reference to Fig. 4 and Fig. 5, one side describes the 3rd embodiment of the present utility model on one side.This motor for example is the air-cooling type single-cylinder engine that utilizes in working machine etc., and engine main body 71 is made of following part: crankcase 72; Cylinder block 73, it projects upwards from this crankcase 72; Cylinder head 74, it is bonded on the head of this cylinder block 73; And valve mechanism cover 75, it is combined on the cylinder head 74.In addition, the attachment face 72a of crankcase 72 below this crankcase 72 is installed on the engine framework of various working machines.
Bent axle 77 rotations freely are bearing on the crankcase 72, and this bent axle 77 has a pair of counterweight 77a, 77b integratedly, and is connected the crankpin 77c between two counterweight 77a, the 77b.
Be formed with cylinder barrel 79 in cylinder block 73, this cylinder barrel 79 is entrenched in wherein with making piston 78 free slidings, and the firing chamber 80 of facing piston 78 tops is formed between cylinder block 73 and the cylinder head 74.In addition, on cylinder head 74, suction port 81 and relief opening 82 that formation can be communicated with firing chamber 80, simultaneously, set the intake valve 83 and the exhaust valve 84 that can carry out on-off action, open and close between 83 pairs of suction ports 81 of described intake valve and the firing chamber 80, open and close between 84 pairs of relief openings 82 of described exhaust valve and the firing chamber 80.
The valve actuating gear 85 that intake valve 83 and exhaust valve 84 is carried out driven for opening and closing has: camshaft 86, and its reduction speed ratio with 1/2 is driven by bent axle 77 rotations; Be arranged on air inlet side cam 87 and exhaust side cams 88 on this camshaft 86; And the air inlet side rocking arm 89 swung driven with air inlet side cam 87; And exhaust side rocking arm (not shown) driven with exhaust side cams 88 and that swing, one end of air inlet side rocking arm 89 and exhaust side rocking arm is by having the shared swing fulcrum 91 of the axis parallel with bent axle 77, swing freely is bearing on the cylinder head 74, can regulate screws at the tappet screw 92 of the other end of air inlet side rocking arm 89 and the upper end portion butt of intake valve 83 with advancing and retreat the position, and can regulate screws at the tappet screw (not shown) of the other end of exhaust side rocking arm and the upper end portion butt of exhaust valve 84 with advancing and retreat the position.
Above-mentioned camshaft 86 has the axis parallel with bent axle 77, is rotated freely to be bearing between cylinder head 74 and the valve mechanism cover 75.Be provided with timing transmission device 95 between this camshaft 86 and bent axle 77, this timing transmission device 95 is configured between the side 77a and crankcase 72 of a pair of counterweight 77a, 77b that bent axle 77 had.This timing transmission device 95 is made of following part: driving sprocket wheel 96, and it is fixed on the bent axle 77; Driven sprocket 97, it is arranged on the above-mentioned camshaft 86; And timing cingulum 98, it is wound on driving sprocket wheel 96 and the driven sprocket 97.Form band chamber 99 in cylinder block 73 and cylinder head 74, this band chamber 99 is moved above-mentioned timing cingulum 98 therein.
Between above-mentioned air inlet side cam 87 and exhaust side cams 88, on above-mentioned camshaft 86, be provided with pivot 100 integratedly, this pivot 100 has the axis with the spin axis off-centre of this camshaft 86, and this pivot 100, piston 78 and bent axle 77 couple together by linkage mechanism 101.
This linkage mechanism 101 is made of following part: master connecting rod 102, and the one end is connected on the piston 78 by wrist pin 105; Slave connecting rod 103, it is connected on the crankpin 77c of bent axle 77, simultaneously, is connected to the other end of master connecting rod 102; And controlling rod 104, the one end is being connected on the position of the link position that departs from master connecting rod 102 on the slave connecting rod 103, and simultaneously, the other end is connected on the above-mentioned pivot 100.
The other end of master connecting rod 102 is pivotally connected to an end of slave connecting rod 103 by the 1st pin 107.One end of controlling rod 104 is pivotally connected on the slave connecting rod 103 by the 2nd pin 108, be provided with circular axis hole 109 in the other end of controlling rod 104, but this axis hole 109 is entrenched in wherein with making above-mentioned pivot 100 slide relative.
And the center line of master connecting rod 102 and controlling rod 104 is configured on the same plane with the orthogonal axe of bent axle 77, and controlling rod 104 and cylinder barrel 79 adjacency run through the operating chamber 110 of setting on the cylinder block 73 up and down with extending.
So, pivot 100 is corresponding with the rotation of bent axle 77 and with the rotation of 1/2 reduction speed ratio, follow this rotation, linkage mechanism 101 is so that the stroke of the piston in expansion stroke 78 moves than the big mode of stroke in compression stroke, thereby, can carry out bigger expansion work with same suction air-fuel mixture amount, can improve thermal efficiency of cycle.
Below, the 3rd embodiment's effect is described.Between the camshaft 86 and bent axle 77 that the valve actuating gear 85 that is provided with on engine main body 21 tops is had, timing transmission device 95 is set, this timing transmission device 95 transmits the rotating power of this bent axle 77 with 1/2 reduction speed ratio, pivot 100 is set on camshaft 86, this pivot 100 has from the axis of the spin axis off-centre of camshaft 86, is connecting the controlling rod 104 of a part that constitutes linkage mechanism 101 on this pivot 100.
Promptly, because valve actuating gear 85 constitutes the OHC type, therefore, the component number that constitutes valve actuating gear 85 is reduced, by making valve actuating gear 85 form lighter weight, just can realize high rotating speedization easily, and, by the contact position between the component that constitute valve actuating gear 85 is reduced, can reduce mechanical noise.
In addition, by timing transmission device 95, rotating power after will slowing down with 1/2 reduction speed ratio from bent axle 77 is delivered on the camshaft 86 that valve actuating gear 85 had, because pivot 100 is set on this camshaft 86, therefore, being rotated situation about freely being bearing on the crankcase with the running shaft with pivot compares, do not need to guarantee to be used to dispose the space of running shaft, can realize the miniaturization of crankcase 72, simultaneously, can must be lower with the motor height setting, and, owing to need between running shaft and bent axle, not be provided for the deceleration mechanism of rotary driving axle, therefore, the axial length of bent axle 77 can be shortened, the integral miniaturization of motor can be made.Owing to do not need running shaft, therefore can reduce the component number.
In addition, controlling rod 104 forms, between the bottom of engine main body 71 and top, has long length, but by reduce controlling rod 104 with the oscillating quantity at the tie point place of slave connecting rod 103, can suppress wearing and tearing, and, becoming the effect that heavy controlling rod 104 plays counterweight because of becoming long, bent axle 77 can obtain good dynamic balancing.
In addition, because the centreline configuration of master connecting rod 102 and controlling rod 104 is at grade, therefore, along on the direction of the axis of bent axle 77, master connecting rod 102, slave connecting rod 103 and controlling rod 104 can be disposed compactly, the distance between bent axle 77 two end part bearings can be shortened.And then, by making controlling rod 104, the load that affacts on master connecting rod 102 and the slave connecting rod 103 that is caused by explosive force is reduced to bent axle 77 side shiftings.
More than, embodiment of the present utility model is illustrated, but the utility model is not limited to the foregoing description, not breaking away under the described situation of the present utility model of claim scope, can carry out all design alterations.
Claims (7)
1. variable stroke engine in this variable stroke engine, has: master connecting rod (60,102), and the one end is connected on the piston (28,78) by wrist pin (59,105); Slave connecting rod (61,103), it is connected on the crankpin (27c, 77c) of bent axle (27,77), simultaneously, be connected to the other end of described master connecting rod (60,102), this bent axle (27,77) rotation freely is bearing on the crankcase (22,72) of engine main body (21,71); Controlling rod (62,104), the one end is being connected on the position of the link position that departs from described master connecting rod (60,102) on the described slave connecting rod (61,103); And pivot (55,100), it can be around the eccentric axis rotation parallel with described bent axle (27,77), and rotation freely is bearing on the described crankcase (22,72), simultaneously, be connected to the other end of described controlling rod (62,104), can transmit the rotating power after slowing down by 1/2 reduction speed ratio from described bent axle (27,77), it is characterized in that
Be arranged on camshaft (36,86) that the valve actuating gear (35,85) on engine main body (21,71) top had with described pivot (55,100) interlock and be connected.
2. variable stroke engine as claimed in claim 1 is characterized in that,
Described pivot (55) is a spin axis with described eccentric axis, rotation freely is bearing on the described crankcase (22), simultaneously, be arranged on the eccentric position of running shaft (46,46 '), rotating power after this running shaft (46,46 ') transmission is slowed down by 1/2 reduction speed ratio from described bent axle (27), between described camshaft (36) and described running shaft (46,46 '), timing transmission device (50) is set, this timing transmission device (50) is made of following part: follower (52), and it is arranged on the described camshaft (36); Driving wheel (51), it is arranged on the described running shaft (46,46 '); And annular driving band (53), it is wound on this driving wheel (51) and the described follower (52).
3. variable stroke engine as claimed in claim 2 is characterized in that,
Running shaft drive unit (47A) will be delivered on the described running shaft (46) from the rotating power deceleration 1/2 of described bent axle (27), and this running shaft drive unit (47A) and described timing transmission device (50) are separated to be configured in the two axial outsides of described crankpin (27c).
4. variable stroke engine as claimed in claim 2 is characterized in that,
Described crankcase (22) is made of following part: box main body (25), and the one side is opened wide; And side cover (26), it is attached to the open end of this box main body (25), running shaft drive unit (47B) will be delivered on the described running shaft (46 ') from the rotating power deceleration 1/2 of described bent axle (27), for this running shaft drive unit (47B) and described timing transmission device (50), described timing transmission device (50) is formed on described side cover (26) side and is configured between described crankpin (27c) and the described side cover (26).
5. as each described variable stroke engine of claim 2～4, it is characterized in that,
Described bent axle (27) has a pair of counterweight (27a, 27b), and they are from the described slave connecting rod of sandwich (61).
6. variable stroke engine as claimed in claim 1 is characterized in that,
Between camshaft (86) and described bent axle (77) that the valve actuating gear (85) that is arranged at described engine main body (71) top is had, timing transmission device (95) is set, this timing transmission device (95) transmits the rotating power of this bent axle (77) by 1/2 reduction speed ratio, described pivot (100) is set on described camshaft (86), and this pivot (100) has from the axis of the spin axis off-centre of described camshaft (86).
7. variable stroke engine as claimed in claim 6 is characterized in that,
The center line of described master connecting rod (102) and described controlling rod (104) is configured at grade.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005247794 | 2005-08-29 | ||
| JP2005247794A JP2007064011A (en) | 2005-08-29 | 2005-08-29 | Stroke variable engine |
| JP2005247795 | 2005-08-29 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN200975266Y true CN200975266Y (en) | 2007-11-14 |
Family
ID=37817096
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2006201347477U Expired - Lifetime CN200975266Y (en) | 2005-08-29 | 2006-08-29 | Four-stroke engine variable stroke engines |
| CN2006101265965A Expired - Fee Related CN1924318B (en) | 2005-08-29 | 2006-08-29 | Stroke-variable engine |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006101265965A Expired - Fee Related CN1924318B (en) | 2005-08-29 | 2006-08-29 | Stroke-variable engine |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2007064011A (en) |
| CN (2) | CN200975266Y (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1924318B (en) * | 2005-08-29 | 2010-07-07 | 本田技研工业株式会社 | Stroke-variable engine |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009085187A (en) * | 2007-10-03 | 2009-04-23 | Yamaha Motor Co Ltd | Compression ratio variable engine |
| JP4922121B2 (en) * | 2007-10-11 | 2012-04-25 | 本田技研工業株式会社 | Variable stroke engine |
| WO2014162815A1 (en) * | 2013-04-01 | 2014-10-09 | 本田技研工業株式会社 | Vehicular power transmission device |
| CN103306845B (en) * | 2013-06-28 | 2015-05-20 | 力帆实业(集团)股份有限公司 | Right crankcase of engine |
| CN103321771B (en) * | 2013-06-28 | 2015-07-01 | 力帆实业(集团)股份有限公司 | Left crankcase for engines |
| CN104141519B (en) * | 2014-07-18 | 2016-05-18 | 燕山大学 | A kind of variable stroke engine distribution switching mechanism |
| CN104534040A (en) * | 2014-11-17 | 2015-04-22 | 重庆翼虎动力机械有限公司 | Crankshaft connecting rod mechanism with small load impact |
| DE102015203387A1 (en) * | 2015-02-25 | 2016-08-25 | Fev Gmbh | Double-acting piston of a VCR engine |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007064011A (en) * | 2005-08-29 | 2007-03-15 | Honda Motor Co Ltd | Stroke variable engine |
-
2005
- 2005-08-29 JP JP2005247794A patent/JP2007064011A/en active Pending
-
2006
- 2006-08-29 CN CNU2006201347477U patent/CN200975266Y/en not_active Expired - Lifetime
- 2006-08-29 CN CN2006101265965A patent/CN1924318B/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1924318B (en) * | 2005-08-29 | 2010-07-07 | 本田技研工业株式会社 | Stroke-variable engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2007064011A (en) | 2007-03-15 |
| CN1924318A (en) | 2007-03-07 |
| CN1924318B (en) | 2010-07-07 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20071114 Effective date of abandoning: 20060829 |