CN2791283Y - Variable compression reatio type engine - Google Patents
Variable compression reatio type engine Download PDFInfo
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- CN2791283Y CN2791283Y CN 200320102482 CN200320102482U CN2791283Y CN 2791283 Y CN2791283 Y CN 2791283Y CN 200320102482 CN200320102482 CN 200320102482 CN 200320102482 U CN200320102482 U CN 200320102482U CN 2791283 Y CN2791283 Y CN 2791283Y
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Abstract
The utility model relates to a variable compression ratio type engine. A subsidiary rod and a piston are interconnected through a connecting rod, wherein the subsidiary rod is connected with a crank shaft. An eccentric shaft and the subsidiary rod are interconnected through a control rod, wherein the eccentric shaft is installed on the eccentric position of a supporting shaft which is rotatablely arranged on a variable compression ratio type engine body, so the compression ratio of the variable compression ratio type engine can be changed through the change of the rotating position of the supporting shaft. The variable compression ratio type engine also comprises a one-way clutch which is installed between the supporting shaft and the variable compression ratio type engine body for restricting the rotating direction of the supporting shaft. Through a restricting device for rotating positions, the rotating position of the supporting shaft is selectively confined to a plurality of points, and through a buffer, load on at least one of the supporting shaft and the restricting device for rotating positions can be buffered.
Description
Technical field
The utility model relates to a kind of variable reduction ratio enqine, and it comprises: connecting rod, and the one end is connected with piston by wrist pin; Auxiliary rod is connected with bent axle and is connected with the other end of described connecting rod by crank pin; Controlling rod, an end is connected with described auxiliary rod at the position of the link position that leaves described connecting rod; Back shaft is arranged in the engine body rotationally; And eccentric shaft, be installed in the eccentric position place on the described back shaft and be connected, thereby the pivotal position that changes described back shaft changes described compression ratio with the other end of described controlling rod.
Background technique
For example, a kind of variable reduction ratio enqine of routine is disclosed among the flat 9-228858 of Japanese Patent Application Laid-Open, wherein auxiliary rod that is connected with bent axle and piston interconnect by connecting rod, and be installed between the eccentric shaft at the eccentric position place on the back shaft and the described auxiliary rod and be connected by controlling rod, wherein said back shaft is arranged in the engine body rotationally, changes the compression ratio of described motor by the pivotal position that changes described back shaft.
In the motor of described routine, rotate the pivotal position that changes described back shaft by driving described back shaft, thereby change described compression ratio by actuator such as electric notor and cylinder.But expansion load and compressive load are applied on the described controlling rod by burning in the described motor and inertia.Based on this reason, impulsive load is applied on the actuator such as electric notor and cylinder, and therefore must install between described actuator and back shaft and be used to relax the device of such impact, thereby makes complex structure.
If the sense of rotation of described back shaft is limited in the direction, then described back shaft can utilize the expansion load and the compressive load that are applied on the described controlling rod by burning in the motor and inertia to rotate.Utilize this structure, do not need to be used to drive the actuator that described back shaft rotates.But, need be used for limiting the restricting means of the pivotal position of described back shaft, and when the pivotal position of described back shaft is restricted, the contacting part branch generation of such restricting means and back shaft be impacted at a plurality of points, therefore need to relax this impact.
The model utility content
Therefore, the purpose of this utility model provides a kind of variable reduction ratio enqine, wherein back shaft utilizes described in-engine burning and inertia to rotate, and, can also relax the impact that produces because of the pivotal position of limiting described back shaft with simple structure.
For achieving the above object, according to first feature of the present utility model, provide a kind of variable reduction ratio enqine, it comprises: connecting rod, and the one end is connected with piston by wrist pin; Auxiliary rod, it is connected with bent axle by crank pin and is connected with the other end of described connecting rod; Controlling rod, the one end is connected with described auxiliary rod at the position of the link position that leaves described connecting rod; Back shaft is arranged in the engine body rotationally; And eccentric shaft, it is installed in the eccentric position place on the described back shaft and is connected with the other end of described controlling rod, change described compression ratio by the pivotal position that changes described back shaft, wherein said motor also comprises: overrunning clutch, and it is installed between described back shaft and the described engine body to limit the sense of rotation of described back shaft; The pivotal position restricting means is used for the pivotal position at the described back shaft of a plurality of point selection ground restriction; And damping device, be used for when changing described compression ratio, relax the load on one of them at least that is applied to described back shaft and pivotal position restricting means.
Utilize this structure of described first feature, expansion load and compressive load are applied on the described controlling rod by burning in the described motor and inertia, thereby when described compression ratio changed, described back shaft and eccentric shaft rotated in the direction of described overrunning clutch restriction.Therefore, do not need directly to rotate the actuator of described back shaft.And, when described compression ratio changes, can cushion the load on one of them at least that is applied to described back shaft and pivotal position restricting means by described damping device.
According to second feature outside first feature of the present utility model, on described bent axle, fix a flywheel, rotatory force is sent on the described flywheel from kick-starter according to the start-up function of described motor; Described damping device comprises: output block, it is coaxial with described bent axle that this output block is set, thereby direction can be sent on the described flywheel with the identical rotatory force of described kick-starter, and when described kick-starter is not worked the limited in rotation system of this flywheel; The input block coaxial with described output block; And be installed in helical spring between described output block and the input block; And between described back shaft and input block, torque transmission device is installed, thereby this device transmits described rotatory force with (wind up) the described helical spring of reeling from described back shaft to described input block in a direction, till finishing described helical spring coiling, but its permission back shaft dallies after described helical spring coiling is finished (race).
Utilize this structure of second feature, when changing described compression ratio, the torque of described back shaft is sent to the input block of described damping device by described torque transmission device, thereby power is accumulated in this helical spring by described helical spring coiling, realizes relaxing impact thereby absorb the load that is applied to described back shaft by described helical spring.In other words, when described compression ratio changed, described back shaft turned to next limit rotation position by described pivotal position restricting means, and the helical spring by described damping device can cushion and accumulate the torque that is applied on the described back shaft.In the process of the accumulation of power in described helical spring, the limited in rotation system of described output block, and when starting in the starting next time of described kick-starter at described motor, the spring force that is accumulated in the described helical spring is sent to described flywheel from described output block.Therefore, even the expansion load on the kick-starter is alleviated, described motor also can fully start.
Except that the structure of described first feature, according to the 3rd feature of the present utility model, the position of a plurality of points on described back shaft is provided with restriction bearing (limiting abutment), and described a plurality of somes space and its position in the axial direction are arranged on the circumferencial direction of described back shaft; Actuator is connected with limiting part, rotate to drive this limiting part, described limiting part is arranged in the described engine body to constitute the part of described pivotal position restricting means, thereby thereby its rotational that can wind perpendicular to described back shaft alternately limits the bearing adjacency with one of them, to limit the pivotal position of described back shaft; And between described limiting part and engine body, insert described damping device, with relax the restriction bearing selected when rotating and described limiting part in abutting connection with the time generation axial impact.
Utilize this structure of described the 3rd feature, can limit the pivotal position of described back shaft in such a way, rotate described limiting part by described actuator, make described limiting part with to be arranged on one of them of a plurality of restriction bearings on the described back shaft adjacent, thereby change described compression ratio.Like this, limit contacting between bearing by described limiting part with one of them, be applied to described limiting part perpendicular to the impact in the direction of described back shaft, but described impact energy is relaxed by the simple structure that described damping device is arranged between described limiting part and the engine body.Therefore, can avoid described impact to be applied to being used to driving on the actuator of described limiting part and improve serviceability and reliability, avoid simultaneously increasing owing to the intensity such as the different parts of back shaft and limiting part increases their size that causes.In addition, can also restrain the sound that when described limiting part contacts with one of them restriction bearing, produces low-level.
Except that described first feature, according to the 4th feature of the present utility model, described damping device is installed between described back shaft and the engine body, is applied to radial load on the described back shaft with buffering from described controlling rod.
Utilize this structure of the 4th feature, when described compression ratio changed, described back shaft and pivotal position restricting means were applied in bigger load, and the radial load that is applied on the described back shaft is relaxed by described damping device.Therefore, can improve serviceability and reliability, their size of avoiding intensity because of each parts of all back shafts as described and pivotal position restricting means to increase simultaneously causing increases.And the sound that produces in the time of also can be with the restriction that is subjected to described pivotal position restricting means in described pivotal position is restrained reduced levels.
Description of drawings
Above-mentioned and other purposes of the present utility model, specific and advantage will be by following joint accompanying drawing the explanation of preferred embodiment become clear.
Fig. 1 is the front elevation of motor;
Fig. 2 cuts open the sectional view of getting along the line 2-2 among Fig. 1;
Fig. 3 cuts open the sectional view of getting along the line 3-3 among Fig. 2;
Fig. 4 cuts open the sectional view of getting along the line 4-4 among Fig. 2;
Fig. 5 cuts open the amplification view of getting along the line 5-5 among Fig. 2;
Fig. 6 is the planimetric map that cuts open the part removal that is in light condition of getting along the line 6-6 among Fig. 1;
Fig. 7 is and the similar view of Fig. 6, but its expression heavy condition;
Fig. 8 is near the amplification view in the zone of an end of expression back shaft shown in Figure 2;
Fig. 9 cuts open the sectional view of getting along the line 9-9 among Fig. 8;
Figure 10 is the zone on the side of the other end of the back shaft shown in the presentation graphs 2 and near the zoomed-in view in the zone buffering/collecting apparatus;
Figure 11 cuts open the sectional view of getting along the line 11-11 among Figure 10;
Figure 12 is near the zoomed-in view in the zone the torque transmission device shown in expression Figure 10;
Figure 13 cuts open the sectional view of getting along the line 13-13 among Figure 12;
Figure 14 cuts open the sectional view of getting along the line 14-14 among Fig. 2.
Embodiment
1-14 describes the utility model by preferred embodiment below with reference to accompanying drawings.
Referring to figs. 1 through 3, be the air cooling single-cylinder engine according to this embodiment's motor, be used for for example working machine etc., and this motor has engine body 21, described engine body comprises: crankcase 22; Cylinder block 23, it is inclined upwardly and side-prominent from described crankcase 22 a little; Cylinder head 24 with the top that is connected to described cylinder block 23.The outer surface of described cylinder block 23 and cylinder head 24 is provided with a plurality of radiating fin 23a and 24a.Described crankcase 22 is installed on the cylinder head of any working machine by the installation surface 22a of its lower surface.
Described crankcase 22 comprises by the integrally formed crankcase body 25 of casting and described cylinder block 23 and is connected to side cover 26 on the opening end of described crankcase body 25.One end 27a of bent axle 27 gives prominence to from described side cover 26.Between end 27a of described bent axle 27 and described side cover 26, ball bearing 28 and oil sealing 30 are set.The other end 27b of described bent axle 27 gives prominence to from described crankcase body 25.Between the other end 27b of described bent axle 27 and crankcase body 25, ball bearing 29 and oil sealing 31 are set.
Flywheel 32 is installed on the other end 27b of the bent axle 27 in described crankcase body 25 outsides.The cooling fan 33 that is used for providing to the different piece of engine body 21 cooling air is installed on described flywheel 32.Arranged outside kick-starter 34 at described cooling fan 33.
In described cylinder block 23, form in casing bore 39 and this casing bore and hold a piston 238 slidably.Between described cylinder block 23 and cylinder head 24, form firing chamber 40, so that the top surface of described piston 38 is to this firing chamber 40.
In described cylinder head 24, form suction port 41 and the relief opening 42 that leads to firing chamber 40.In described cylinder head 24, be provided with: intake valve 43, it can open and close so that being communicated with or disconnection between described suction port 41 and the firing chamber 40 to be provided; With exhaust valve 44, it can open and close to provide the connected sum between described relief opening 42 and the firing chamber 40 to disconnect.Screw thread is installed a spark plug 45 on the described cylinder head 24, and the electrode surface of this spark plug is to described firing chamber 40.
Top at cylinder head 24 connects Carburetor 35.The downstream of the gas-entered passageway 46 of this Carburetor 35 is communicated with suction port 41.The suction tude 47 of leading to the upstream extremity of gas-entered passageway 46 is connected with Carburetor 35, and also is connected with air Cleaner (not shown).The outlet pipe 48 that leads to relief opening 42 is connected with the top of cylinder head 24, and also is connected with muffler 49.In addition, fuel tank 51 is arranged on the crankcase 22, thereby it is supported on the described crankcase 22.
Be near the part of side cover 26 at crankcase 22 and integrally form actuation gear 52 on the bent axle 27.To be installed on the camshaft 54 with the driven gear 53 of this actuation gear 52 engagements, this camshaft is arranged in the described crankcase 22 rotationally and it has the axis parallel with this bent axle 27.Rotatory force sends described camshaft 54 by intermeshing actuation gear 52 with driven gear 53 with the ratio 1/2 of dwindling from bent axle 27.
On camshaft 54, be provided with respectively and described intake valve 43 and exhaust valve 44 corresponding intake cam 55 and exhaust cams 56.Be arranged on exercisable follower 57 and intake cam 55 sliding contacts in the cylinder block 23.On the other hand, in cylinder block 23 and cylinder head 24, form operating room 58, thereby the top of described follower 57 is stretched in the bottom of operating room 58.The lower end that is arranged on the push rod 59 in the operating room 58 abuts against on the follower 57.On the other hand, rocking arm 60 is arranged in the cylinder head 24 swingably, and an end of this rocking arm abuts against the upper end of the intake valve 43 of setovering by a spring in closing direction.The upper end of push rod 59 abuts against the other end of described rocking arm 60.Therefore, described push rod 59 comes axial operation according to the rotation of intake cam 55, and the oscillating motion of the rocking arm 60 that causes of the operation by push rod 59 comes the described intake valve 43 of open and close.
Also be provided with between exhaust cam 56 and the exhaust valve 44 with intake cam 55 and intake valve 43 between similar mechanism, thereby described exhaust valve 44 is opened and closure according to the rotation of exhaust cam 56.
With reference to Fig. 4, be arranged on and be used in the crankcase 22 of engine body 21 being connected by bindiny mechanism 62 each other through cylinder axis C and the piston 38, bent axle 27 and the eccentric shaft 61 that move perpendicular to the plane of the axis of bent axle 27.
This bindiny mechanism 62 comprises: the connecting rod 64 that an end is connected with piston 38 by wrist pin 63; The auxiliary rod 68 that is connected with bent axle 27 and is connected rotationally with the other end of described connecting rod 64 by crank pin 65; With controlling rod 69, the one end is connected with auxiliary rod 68 rotationally in the position of the link position that leaves connecting rod 64, and the other end is connected with eccentric shaft 61.
The other end of connecting rod 64 is connected with an end of auxiliary rod 68 by cylindrical connection lever pin 75.The opposite end of pushing the connection lever pin 75 in the other end that is engaged in connecting rod 64 is assemblied in the branch 71 of an end that is arranged in auxiliary rod 68 rotationally.
One end of controlling rod 69 is connected with the other end of auxiliary rod 68 rotationally by auxiliary lever pin 76.The opposite end of auxiliary lever pin 76 and branch's 72 Spielpassung that are positioned at the other end, wherein said auxiliary lever pin 76 passes through an end of the controlling rod 69 of the branch 72 that is inserted into the other end that is arranged in auxiliary rod 68 relatively rotationally.And, a pair of intermediate plate (clip) 77,77 is installed in the branch 72 that is positioned at the described the other end, with the opposite end of auxiliary lever pin 76 in abutting connection with and prevent that described auxiliary lever pin 76 from separating with branch 72.
In addition, described crank cap 73 is fixed on branch 71 and 72 by the bolt 78 on a pair of relative both sides that are arranged on bent axle 27.Described connection lever pin 75 and auxiliary lever pin 76 are arranged on the axis elongation line of bolt 78.
Cylindrical eccentric shaft 61 is wholely set the eccentric position place on back shaft 81, and this back shaft is arranged in the crankcase 22 of engine body 21 rotationally and has the axis parallel with bent axle 27.One end of back shaft 81 is supported on the bottom cylindrical shaft bearing 82 rotationally, and this bearing support is arranged on the side cover 26 of crankcase 22 and is inserted with ball bearing 83 between described back shaft 81 and bearing support 82.The other end of back shaft 81 passes through the crankcase body 25 of crankcase 22 rotationally, and is inserted with ball bearing 84 between described crankcase body 25 and back shaft 81.
Overrunning clutch 85 is installed in the outside at ball bearing 83 between bearing support 82 and back shaft 81.Lip ring 86 is inserted in the outside at ball bearing 84 between described crankcase body 25 and back shaft 81.
According to the work cycle of motor, the load wheels in the direction of load in the direction of compression control bar 69 and stretching controlling rod 69 for be applied on its other end and the controlling rod 69 that eccentric shaft 61 is connected.Because described eccentric shaft 61 is arranged on eccentric position place on the back shaft 81, so controlling rod 69 also applies towards the rotatory force of a side with towards the rotatory force of opposite side back shaft 81.In other words and since described back shaft 81 with between the bearing support 82 on the side cover 26 of crankcase 22, be provided with overrunning clutch 85, therefore described back shaft 81 can rotate in the direction shown in the arrow 80 in Fig. 4.
With reference to Fig. 5, on back shaft 81, be positioned at the coaxial axial region 81a that minor diameter is set in the position of axially leaving eccentric shaft 61 in such a way, around the excircle of this minor diameter axial region 81a, to form circular groove 81b.A plurality of points on minor diameter axial region 81a, for example axially spaced two some places are wholely set restriction bearing 87 and 88, and the position of these somes mutual alternative (displace) on the circumferencial direction of back shaft 81.
The pivotal position of back shaft 81 is rotated position limit device 89 and is limited in a plurality of points then, for example two points.Pivotal position restricting means 89 comprises: be arranged on the rotating shaft 90 in the crankcase 22 rotationally, this rotating shaft has the axis perpendicular to the axis of back shaft 81; With the limiting part 91 that is fixed in the rotating shaft 90, therefore the rotation of described limiting part 91 by rotating shaft 90 can rotate with restriction bearing 87,88 adjacency.
Be wholely set bottom cylindrical shaft supporting part 92 and annular shaft supporting part 93 on the crankcase body 25 of crankcase 22, a segment distance is oppositely arranged so that they are separated by on the same axis perpendicular to the axis of back shaft 81.Near the rotating shaft 90 that one end is positioned at the axle support section 92 is supported on axle support section 92 and 93 rotationally, and its other end is protruding from axle support section 93.
Limiting part 91 by on pin 94 fixed rotating shafts 90 between axle support section 92 and 93, and its one is provided with projection 91a, this projection can stretch among the circular groove 81b with rotate with restriction bearing 87 and 88 adjacency.
When at the projection 91a of limiting part 91 with one of them adjacent state of restriction bearing 87 and 88 with when projection 91a changes each other with these two states of wherein another adjacent state of restriction bearing 87 and 88, back shaft 81 by be applied to be installed in back shaft 81 on the controlling rod 69 that is connected of the eccentric shaft 61 at eccentric position place on load rotate.But, the impact that one of them that must avoid described restriction bearing 87 and 88 causes the projection 91a of restriction bearing 91 because of the rotation of back shaft 81 when adjacency.Therefore, between the axle support section 93 of crankcase 22 and limiting part 91, impulse force reliever 97 is set, be used to relax restriction bearing 87 and 88 with the limiting part 91 selected of rotating take place in abutting connection with the time in the impact of axial direction generation.
Impulse force reliever 97 comprises the ring-shaped rubber spare 99 that is clipped between a pair of packing ring 98,98, and described packing ring is passed in described rotating shaft 90.Rubber parts 99 has higher hardness, oil resistance and heat resistance, and makes this rubber parts roasting molten and condense on the packing ring 98,98 in addition.
With reference to Fig. 6, diaphragm actuator 101 is connected with the rotating shaft 90 of pivotal position restricting means 89.Described actuator 101 comprises: casing 103 is installed on the dunnage 102 on top of the crankcase body 25 that is fixed to crankcase 22; Diaphragm 106, thus the inside that is supported in the casing 103 casing 103 is divided into negative pressure chamber 104 and normal pressure chamber (atmospheric pressure chamber) 105; Spring 107 is installed between casing 103 and the diaphragm 106 with compressive state, thereby acts on spring force on the direction that increases negative pressure chamber's 104 volumes; With operating handle 108, be connected with the intermediate portion of diaphragm 106.
Described normal pressure chamber 105 is limited between the diaphragm 106 and the first half chests body 109.An end that stretches into the operating handle 108 in the normal pressure chamber 105 through through hole 111 is connected with the intermediate portion of diaphragm 106, and wherein said through hole is arranged on the intermediate portion of the first half chests body 109.Described normal pressure chamber 105 by through hole 111 inner edge and gap and the external communications between the outer periphery of operating handle 108.
The pipeline 112 that leads to negative pressure chamber 104 is connected with the second half chests body 110 of casing 103, and also is connected with the downstream of the gas-entered passageway 46 of Carburetor 35.In other words, the air-intake negative-pressure in the gas-entered passageway 46 is introduced into the negative pressure chamber 104 in the actuator 101.
The other end of the operating handle 108 of actuator 101 be arranged on dunnage 102 on be used for being connected around the driving arm 113 of the rotational that is parallel to rotating shaft 90.Slave arm 114 is fixed on the other end of the rotating shaft 90 of stretching out from crankcase 22.Described driving arm 113 interconnects by connecting rod 115 with slave arm 114.Mounting spring 116 rotates it to promote described slave arm 114 in clockwise direction shown in Figure 6 between slave arm 114 and dunnage 102.
When motor was in the underloading working state, wherein the negative pressure in the negative pressure chamber 104 was very high, and the elastic force of diaphragm 106 relative returning springs 107 and spring 116 bends reducing the volume of negative pressure chamber 104, and operating handle 108 shrinks, as shown in Figure 6.Under this state, the pivotal position of the limiting part 91 of rotating shaft 90 and pivotal position restricting means 89 is the restriction bearing 87 of the projection 91a of limiting part 91 and back shaft 81 and the position of one of them 87 contiguous engagement of 88.
On the other hand, when motor was in the high capacity working state, wherein the negative pressure in the negative pressure chamber 104 was lower, and diaphragm 106 utilizes the volume of the spring force bending of returning spring 107 and spring 117 with increase negative pressure chamber 104, and operating handle 108 elongations, as shown in Figure 7.Therefore the limiting part 91 of rotating shaft 90 and pivotal position restricting means 89 turns to the restriction bearing 87 of the projection 91a of limiting part 91 and back shaft 81 and the position of one of them 88 contiguous engagement of 88.
As mentioned above, the rotation that is applied in the back shaft 81 of rotatory force when engine operation in a direction is limited in such position, and any one in this position limit bearing 87,88 engages with the projection 91a of restricted part 91 by rotation limiting part 91.Different mutually by stopping back shaft 81 in phase place, for example be separated by the rotation of each position in two positions of 167 degree, make the position that is in the axis that departs from back shaft 81, the eccentric shaft 61 that is the other end of controlling rod 69 moves between perpendicular to these two positions in the plane of the axis of bent axle 27, thereby changes the compression ratio of motor.
With reference to Fig. 8 and 9, when compression ratio changes, replace the projection 91a of ground and limiting part 91 in abutting connection with producing impact for fear of restriction bearing 87 and 88 moving runners by back shaft 81, between the bearing support 82 of end of back shaft 81 and engine body 21 upper crankcases 22, radially damping device 120 is installed, is used to relax from controlling rod 69 and is applied to load on the back shaft 81 in radial direction.
Described radially damping device 120 comprises: be wholely set the eccentric cam 121 on back shaft 81, be located near the minor diameter axial region 81a on the side of ball bearing 83; Spring seat 122 engages with encirclement eccentric cam 121 with ball bearing 82, thereby prevents the rotational of described spring seat 122 around back shaft 81; With pressure spring 123, remain on the spring seat 122 and eccentric cam 121 rubbing contact.
The coaxial cylindrical part 124 that is provided with is with around eccentric cam 121 on back shaft 81.Spring seat 122 is assemblied in the cylindrical part 124 slidably.The ring-type dunnage 125 relative with ball bearing 83 and bearing support 82 is connected with spring seat 122 one.Be formed with outstanding annular projection 126 in dunnage 125 near on the end of bearing support 82, thereby the end that forms cylindrical part 124 between projection 126 and spring seat 122 is inserted in circular groove wherein, and some place on bearing support 82 on circumference is formed with joint plate part 127, stretches out with radially outward.
Described joint plate part 127 is clipped between the locking plate part 128,128 on a pair of top end that is arranged on bearing support 82 highlightedly, thereby forbids the rotation of spring seat 122 around the axis of back shaft 81.And, on dunnage 125, be wholely set outstanding annular ledge 129, and this bearing is supported on outer ring (outer race) 83a of ball bearing 83 in the mode of adjacency.
Described pressure spring 123 roughly forms annular, and some place on circumference has opening slot 130, and it has anastomosis part 123a and 123b, described these anastomosis part radially outwards are heaved for trapezoidal, with with the pair of engaging hole 131 that is arranged on the diameter line that is positioned at back shaft 81 in the spring seat 122,131 engage, and also have a pair of radially flexible flexible support 123c and 123d, this to bearing can with flexibly sliding contact of eccentric cam 121.Flexible support 123c and 123d are arranged on perpendicular to two some places on the straight line of the line that anastomosis part 123a and 123b are linked together.
Utilize radially damping device 120, in the rotation process of back shaft 81, one of them of eccentric cam 121 pivoting flexible bearing 123c and 123d also bends it, is applied to radial load on the back shaft 81 thereby can relax when compression ratio changes from controlling rod 69.And, when compression ratio when low compression ratio becomes high compression ratio, utilize burning in the motor may cause bigger impact to back shaft 81.Therefore, become from low compression ratio the process of high compression ratio at compression ratio, the initial deformation amount of the flexible support 123c that contacts with eccentric shaft 121 and one of them 123c of 123d is configured to the initial deformation amount greater than flexible support 123d.Therefore, can effectively relax the impact that when compression ratio becomes the process of high compression ratio from low compression ratio, is applied on the back shaft 81, thereby can avoid anti-rotational torque unnecessary in the change procedure of compression ratio from the high compression ratio to the low compression ratio to be applied on the back shaft 81.
Refer again to Fig. 2, the casing 134 of kick-starter 34 comprises: around flywheel 32 and be fixed on the columniform box part 135 on the crankcase body 25 of crankcase 22 and be fixed on the box part 135 lid shape (cap-shaped) box part 136 with the opening of closed box part 135.Spool 138 rotational support are on axle 137, and axle 137 is installed in the box part 136 coaxial with bent axle 27, and helical spring 139 is installed between axle 137 and the belt wheel 138.
An end that is wrapped in the rope 140 on the spool 138 is tied up on spool 138, and the opening 141 that the other end of rope 140 is provided with from box part 136 reaches the outside.
The lid shape starter pulley 124 that the part of spool 138 is fixed on the end of bent axle 27 covers, and ratchet 144 is supported on the spool 138 and can engages with the locked groove 143 in the inner circumference that is arranged on starter pulley 124.
Therefore, when the elastic force of relative helical spring 139 spurs rope 140 and discharges pulling force then, spool 138 rotates under the effect of the elastic force of helical spring 139, and ratchet 144 engages with locked groove 143 in the starter pulley 142, is sent on the bent axle 27 from spool 138 thereby will start rotatory force.
With reference to Figure 10 and 11, between the crankcase body 25 of crankcase 22 and flywheel 32, buffering/collecting apparatus 145 is set, thereby direction and kick-starter 34 identical rotatory forces can be sent to flywheel 32.
Buffering/collecting apparatus 145 comprises and being installed in and the output block 146 of bent axle 27 coaxial settings and the helical spring 148 between the input block 147.Output block 146 and input block 147 all are configured as tabular ring, around bent axle 27 and coaxial with bent axle, described output block and input block are arranged to make them separated by a distance on the axial direction of crankcase 27, and output block 146 is arranged on the position near crankcase 22.
Be in and being fixed on the output block 146 of the corresponding position of excircle of input block 147 with bent axle 27 axially extending ends that are roughly columniform outer tube 149.Pipe 150 in this air inlet component 147 is formed with, pipe and bent axle 27 coaxial settings and be positioned at the inboard of outer tube 149 in this.Helical spring 148 is contained in the space that is limited by output block 136, outer tube 149, input block 147 and interior pipe 150, and its opposite end is connected with interior pipe 150 with outer tube 149 in the mode that engages.
In sort buffer/collecting apparatus 145, be limited at output block 146 under the situation of its rotation, helical spring 148 can wind up with accumulation power by rotating input block 147.If remove restriction to output block 146, and the rotation of restriction input block 147, then output block 146 rotates by the spring force of helical spring 148 accumulations.
For this rotatory force with output block 146 sends flywheel 32 to, on the inner circumference of flywheel 32 in a circumferential direction with the spaced a plurality of points of equidistance place, for example two some places are wholely set radially inwardly outstanding trapezoidal locking projection 151,151.On the other hand, a plurality of points that separate with equidistance in a circumferential direction on the outer tube 149 that is fixed on the output block 146, for example two some places are provided with the groove 152,152 that radially concaves.Ratchet 153,153 is supported on the output block 146 with locking projection 151,151 and engages, and rotates so that ratchet stretches out the position of groove 152,152 and is contained between the position in the groove 152,152 at it.That is, ratchet 153,153 has been wholely set axle 154,154, and this axle and bent axle 27 are parallel and be supported on rotationally on the output block 146.
And, in the roller 155,155 each is fixed in the axle 154,154 coaxially be positioned on each the end described roller this from output block 146 towards the crankcase body 25 of crankcase 22 stretch out a bit.On crankcase body 25, be provided with cylindrical conduit 156 integratedly and highlightedly, so that roller 155,155 rolls on cylindrical conduit 156.
Therefore, when rotating in the direction shown in the arrow 157 of output block 146 in Figure 11, roller 155,155 rolls along the internal surface of conduit 156, thereby described axle 154,154 rotates so that ratchet 153,153 stretches out from groove 152,152 in a direction.The ratchet 153,153 that stretches out from groove 152,152 engages with locking projection 151,151 respectively, thereby allows the rotatory force of output block 146 to send flywheel 32 to.
With bent axle 27 coaxial be arranged in the dispatch tube 158 of pipe 150 inboards be fixed on the inner circumferential portion of input block 147 by a plurality of rivets 159, and this dispatch tube is supported on the crankcase body 25 of crankcase 22 rotationally, and is provided with ball bearing 160 between this dispatch tube and body 25.On the inner circumference of output block 146, be formed with cylindrical support pipe 161, the excircle sliding contact of itself and dispatch tube 158.
Rotational torque on the direction of coiling helical spring 148 is sent to the input block 147 of buffering/collecting apparatus 145 by torque transmission device 162 and dispatch tube 158 from back shaft 81.
With reference to Figure 12 and 13, described torque transmission device 162 is constructed such that it transmits rotational torque till the coiling of helical spring 148 is finished in the direction of described helical spring 148 of reeling, but after the coiling of helical spring 148 was finished, described torque transmission device can make back shaft 81 idle running.Torque transmission device 162 comprises: at the annular element 163 that centers on described back shaft 81 from the crankcase body 25 outstanding parts of crankcase 22; The a pair of ball 164,164 that can change between two states, described ball a state therein are connected with annular element 163 with back shaft 81 and are breaking away from annular element 163 under another state and remaining on the back shaft 81; Spring 165, be installed between the ball 164,164 with effect make ball 164,164 make they with back shaft 81 and direction that annular element 163 is connected on the elastic force that is offset; Actuation gear 166 is wholely set on the excircle of described annular element 163; With driven gear 167, be wholely set on dispatch tube 158 and mesh with described actuation gear 166.
Described annular element 163 is around described back shaft 81, and its axial position is determined constant.Back shaft 81 is provided with through hole 158 at itself and annular element 163 corresponding positions, and this through hole extends along a diameter line.On the other hand, circular groove 169 and a pair of locked groove 170,170 are set in the inner circumference of annular element 163.Described locked groove 170,170 forms they is outwards caved in from circular groove 169 on a diameter line of annular element 163.
The part of each ball 164,164 is inserted in each opposite end of through hole 169.Spring 165 is contained in the through hole 169, thereby it is plugged between the ball 164,164.Described circular groove 169 forms and makes it have enough degree of depth to roll that half is contained in ball 164,164 in two opposite ends of through hole 169.Locked groove 170,170 forms semicircle, is bonded on wherein with the ball 164,164 in two opposite ends that almost half are contained in described through hole 169.
In this torque transmission device 162, at ball 164,164 are bonded on locked groove 170, under the state in 170, be ball with state that back shaft 81 and annular element 163 engage under, by the rotation of back shaft 81, with the rotational torque of back shaft 81 by annular element 163, actuation gear 166, driven gear 167 and dispatch tube 158 send input block 147 to.Therefore, be at buffering/collecting apparatus 145 under the confined state of rotation of described output block 146, described helical spring 148 is rolled-up.
In addition, the elastic force of helical spring 148 is as resistance, and can relax the radial load that is applied to back shaft 81 when compression ratio changes from controlling rod 69, thereby torque transmission device 162 also can be used as radially damping device.
After the coiling of helical spring 148 was finished, when back shaft 81 rotated according to the variation of compression ratio, described back shaft 81 idle running were to repeat this two states, it is ball 164,164 are bonded on the state that state in the locked groove 170,170 and ball 164,164 roll in circular groove 169.By relaxing because compression ratio changes from controlling rod 69 and be applied to radial load on the back shaft 81 from the creep resistance that produced when entering circular groove 169 of locked groove 170,170 in the elastic force of ball 164,164 relative springs 165.Therefore, even in this case, described torque transmission device 162 also plays the radially effect of damping device.
In current embodiment, interfering to avoid conduit 156 and torque transmission device 162 being provided with recess 156a of conduit 156 with torque transmission device 162 corresponding positions.
The rotation of the output shaft 146 of buffering/collecting apparatus 145 is by 171 restrictions of cumulative release/restricting means.Cumulative release/restricting means 171 restriction output blocks 146 are in the rotation of the not duration of work of kick-starter 34, but it just allows described output block 146 to rotate in case start kick-starter 34 operations.
With reference to Figure 14, described cumulative release/restricting means 171 comprises: restriction step 172, its round the excircle setting of output block 146 with in the face of the downstream in the sense of rotation shown in the arrow 157 among Figure 11; Limit rod 173, it is parallel to bent axle 27 and extends with by itself and the rotation that limits output block 146 that engages that limits step 172, and an end of this limit rod engages with conjugate foramen 174 in the crankcase body 25 that is arranged on crankcase 22; Rocking arm 175, it can unsteadily be supported on the supporting part 176, and this supporting part is fixed on the box part 135 of casing 134 of kick-starter 34, and an end of this rocking arm engages with the other end of limit rod 173; With returning spring 177, it is installed in and is used for applying the spring force that makes limit rod 173 skews between casing body 135 and the rocking arm 175 in a termination that makes limit rod 173 is combined in the direction of conjugate foramen 174.
Supporting part 176 is fixed near the internal surface of the casing body 135 the opening 141, and has patchhole, and the rope 140 of kick-starter 32 is by this patchhole.Described rocking arm 175 forms from relative both sides with described supporting part 176 and is clipped in the middle, and the intermediate portion of this rocking arm can unsteadily be supported on the supporting part 176 by the axle 179 perpendicular to limit rod 173.Described returning spring 177 is torsion springs, and is installed between described box part 135 and the rocking arm 175 with threaded shaft 179.
When kick-starter 34 is in idle state; rocking arm 175 turns to a position by the spring force effect of returning spring 177; be clipped at the described rope 140 in this position and wave between 175 the other end and supporting part 176; under this state, is in the limit rod 173 that the one termination is combined in the position in the conjugate foramen 174 and engages to limit the rotation of output block 176 with restriction step 172.
When the rope 140 of pulling kick-starter 34 starts described motor and makes it be in this state, by tensioning rope 140, make thrust be applied to the other end of rocking arm 175 from rope 140, thereby described rocking arm 175 rotates relative to the elastic force of returning spring 177, makes limit rod 173 break away from described conjugate foramen 174.Therefore, an end of limit rod 173 is in free state, and limit rod 173 is in its other end and can unsteadily be supported on state on the rocking arm 175.Therefore, output block 146 is in the state that allows its rotation, and when helical spring 148 kept the power of accumulation, described output block 146 rotated like this.
To describe current embodiment's operation below in detail.The side cover 26 of the crankcase 22 by being installed in motor 21 and the overrunning clutch 82 between the back shaft 81 limit the sense of rotation of the back shaft 81 with the eccentric shaft 61 that is in eccentric position and is connected with controlling rod 69, and expansion load and compressive load are applied on the controlling rod 69 by burning in the motor and inertia.Therefore, when compression ratio changed, back shaft 81 and eccentric shaft 61 rotated in the direction that is limited by overrunning clutch 85.
Optionally the pivotal position of back shaft 81 is limited in by pivotal position restricting means 89 a plurality of, two positions and change the compression ratio of motor by the pivotal position that changes back shaft 81 for example.
In addition, according to the start-up function of motor, rotatory force is sent on the flywheel 32 that is fixed on the bent axle 27 from kick-starter 34.Can be sent to from the buffering/collecting apparatus 145 that includes helical spring 148 on the flywheel 32 with the rotational torque of kick-starter 34 equidirectionals, wherein said helical spring 148 is installed between the output block 146 and input block 147 with bent axle 27 coaxial settings.Described torque transmission device 162 is installed between back shaft 81 and the input block 146, wherein this torque transmission device can will be sent to input block 146 till the coiling of helical spring 148 is finished from back shaft 81 at the rotational torque in the direction of coiling helical spring 148, and allows back shaft 81 to dally after the coiling of helical spring 148 is finished.When kick-starter is not worked, the rotation of the output block 146 by cumulative release/restricting means 171 restriction buffering/collecting apparatus 145, and these cumulative release/restricting means 171 permission output blocks 146 rotate according to the start-up function of kick-starter 34.
Therefore, when compression ratio changed, the rotational torque of back shaft 81 was sent to the input block 147 of buffering/collecting apparatus 145 by torque transmission device 162.Therefore, the coiling by helical spring 148 can be accumulated in power in the helical spring 148, and the load that is applied on the back shaft 81 can absorb by helical spring 148, impacts thereby help to relax.In other words, when back shaft 81 turns to next limit rotation position by pivotal position restricting means 89 when compression ratio changes, be applied to rotational torque on the back shaft 81 can be cushioned/helical spring 148 accumulation of collecting apparatus 145.In the process that power is accumulated in helical spring 148, the rotation of output block 146 is by 171 restrictions of cumulative release/restricting means, but when described kick-starter 34 started in the starting next time of motor, cumulative release/restricting means 171 allowed the rotation of output blocks 146.Therefore the spring force that is accumulated in the helical spring 148 is sent to flywheel 32 from output block 146, even therefore reduce the hauled load on the kick-starter 34, described motor also can fully start.
When one of them and limiting part 91 of restriction bearing 87 and 88 are in contact with one another, described limiting part 91 is subjected to perpendicular to the impact in the direction of the axis of back shaft 81, but can utilize a kind of simple structure to relax this impact, in this structure, between the axle support section 93 of limiting part 91 and crankcase body 25, thrust damping device 97 is set.Therefore, can avoid impact force action to the actuator 101 that is used to drive limiting part 91 and improve serviceability and reliability, avoid simultaneously increasing such as the size of the various parts of back shaft 81 and limiting part 91 intensity because of them.In addition, the sound that produces in the time of also one of them and the limiting part 91 in restriction bearing 87 and 88 being in contact with one another restrain one low-level.
Between the side cover 26 of back shaft 81 and motor 21 upper crankcases 22, radially damping device 120 is installed, is used to relax from controlling rod 69 and affacts radial load on the back shaft 81.Also be installed between buffering/collecting apparatus 145 and the back shaft 81 as the torque transmission device 162 of damping device radially.
Therefore, when compression ratio changes,, but utilize radial load damping device 120 and the radial load of torque transmission device 162 abirritations on back shaft 81 even back shaft 81 and pivotal position restricting means 89 bear bigger load.Therefore, can improve serviceability and reliability, avoid simultaneously that the powerful increase because of them increases such as the size of the various parts of back shaft 81 and pivotal position restricting means 89.And, also the sound that produces when pivotal position restricting means 89 limits pivotal positions can be restrained at a reduced levels.
Though above embodiment of the present utility model is described in detail, should understand that the utility model is not limited to above-mentioned specific embodiment, and under the situation that does not deviate from the spirit and scope of the present utility model that define in claims, can carry out different modifications the utility model.
Claims (10)
1, a kind of variable reduction ratio enqine, it comprises; The connecting rod that one end is connected with piston by wrist pin; The auxiliary rod that is connected with bent axle and is connected by crank pin with the other end of described connecting rod; The controlling rod that one end is connected with described auxiliary rod at the position of the link position that leaves described connecting rod; Be arranged on the back shaft in the engine body rotationally; Be installed in described back shaft on the eccentric position place and the eccentric shaft that is connected with the other end of described controlling rod, change described compression ratio by the pivotal position that changes described back shaft so that position of eccentric moves,
It is characterized in that described motor also comprises: overrunning clutch, it is installed between described back shaft and the described engine body, thereby can only rotate along a direction by the described back shaft of overrunning clutch; The pivotal position restricting means, its pivotal position that is used for described back shaft that links to each other with described back shaft is limited in a plurality of somes place, thereby by changed the pivotal position of described back shaft by the pivotal position restricting means, changes the compression ratio that starts; And damping device (97,120), it is installed at least between one of them of described engine body and described back shaft and described pivotal position restricting means, the load that produces with the described compression ratio of operation change that relaxes by described pivotal position restricting means.
2, variable reduction ratio enqine as claimed in claim 1, it is characterized in that, described damping device is damping device (120) radially, and it is installed between described back shaft and the engine body to relax from described controlling rod and is applied to radial load on the described back shaft.
3, variable reduction ratio enqine as claimed in claim 2, it is characterized in that, described radially damping device comprises: be wholely set the eccentric cam on back shaft, this eccentric cam is positioned on the side of ball bearing, and this ball bearing is inserted in described back shaft and supports rotationally between the bottom cylindrical shaft bearing of described back shaft one end; Spring seat, it engages with described ball bearing to surround described eccentric cam; And pressure spring, it remains on the described spring seat and described eccentric cam rubbing contact.
4, variable reduction ratio enqine as claimed in claim 1 is characterized in that, described damping device is impulse force reliever (97), and it is installed between described engine body and the described pivotal position restricting means.
5, variable reduction ratio enqine as claimed in claim 4, it is characterized in that, described impulse force reliever comprises the ring-shaped rubber spare that is clipped between a pair of packing ring, is arranged in the crankcase rotationally and its axis normal is passed described packing ring in the rotating shaft of the axis of described back shaft.
As claim 1,4 or 5 described variable reduction ratio enqines, it is characterized in that 6, on the point of a plurality of axial spaces on the described back shaft restriction bearing is set, replace the position of these points in the circumferencial direction of described back shaft; One actuator is connected with a limiting part, and described limiting part is arranged in the described engine body, constitutes the part of pivotal position restricting means, and be actuated to rotate in abutting connection with described restriction bearing; Described damping device be arranged between described limiting part and the engine body with relax the restriction bearing selected when rotating and described limiting part in abutting connection with the time generation axial impact.
7, a kind of variable reduction ratio enqine, it comprises: the connecting rod that an end is connected with piston by wrist pin; The auxiliary rod that is connected with bent axle and is connected by crank pin with the other end of described connecting rod; The controlling rod that one end is connected with described auxiliary rod at the position of the link position that leaves described connecting rod; Be arranged on the back shaft in the engine body rotationally; Be installed in described back shaft on the eccentric position place and the eccentric shaft that is connected with the other end of described controlling rod, change described compression ratio by the pivotal position that changes described back shaft so that position of eccentric moves,
It is characterized in that described motor also comprises: overrunning clutch, it is installed between described back shaft and the described engine body, thereby can only rotate along a direction by the described back shaft of overrunning clutch; The pivotal position restricting means, its pivotal position that is used for described back shaft that links to each other with described back shaft is limited in a plurality of somes place, thereby by changed the pivotal position of described back shaft by the pivotal position restricting means, changes the compression ratio that starts; And buffering/collecting apparatus (145), it is installed between the crankcase body and described flywheel of described crankcase.
8, variable reduction ratio enqine as claimed in claim 7, it is characterized in that, also comprise a kick-starter, wherein said buffering/collecting apparatus comprises: output block, itself and the coaxial setting of described bent axle, input block, it is coaxial with described output block, and helical spring, it is installed between described output block and the input block; Torque transmission device, it is installed between described back shaft and the described input block along the described helical spring direction of reeling rotatory force is sent to described input block from described back shaft, till described helical spring coiling is finished, and allow described back shaft after described helical spring coiling is finished, to dally.
9, a kind of variable reduction ratio enqine, it comprises: the connecting rod that an end is connected with piston by wrist pin; The auxiliary rod that is connected with bent axle and is connected by crank pin with the other end of described connecting rod; The controlling rod that one end is connected with described auxiliary rod at the position of the link position that leaves described connecting rod; Be arranged on the back shaft in the engine body rotationally; Be installed in described back shaft on the eccentric position place and the eccentric shaft that is connected with the other end of described controlling rod, change described compression ratio by the pivotal position that changes described back shaft so that position of eccentric moves,
It is characterized in that described motor also comprises: overrunning clutch, it is installed between described back shaft and the described engine body, thereby can only rotate along a direction by the described back shaft of overrunning clutch; The pivotal position restricting means, its pivotal position that is used for described back shaft that links to each other with described back shaft is limited in a plurality of somes place, thereby by changed the pivotal position of described back shaft by the pivotal position restricting means, changes the compression ratio that starts; And torque transmission device (162), it is installed between a dispatch tube and the described back shaft, to relax the load of radial effect on described back shaft when changing compression ratio, wherein said dispatch tube also is supported on the crankcase body of crankcase rotationally with the coaxial setting of bent axle.
10, variable reduction ratio enqine as claimed in claim 9 is characterized in that, described torque transmission device comprises: at the annular element that centers on described back shaft from the outstanding part of the crankcase body of described crankcase; The a pair of ball that can change between two states, described ball a state therein are connected with annular element with described back shaft and are breaking away from described annular element under another state and remaining on the described back shaft; Spring, its be installed between the described ball with effect make ball make they with back shaft and direction that annular element is connected on the elastic force that is offset; Actuation gear is arranged on the excircle of described annular element (163) integratedly; And driven gear, be arranged on integratedly on the described dispatch tube and mesh with described actuation gear.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP313706/2002 | 2002-10-29 | ||
| JP313708/2002 | 2002-10-29 | ||
| JP2002313706A JP3944053B2 (en) | 2002-10-29 | 2002-10-29 | Variable compression ratio engine |
| JP313707/2002 | 2002-10-29 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2791283Y true CN2791283Y (en) | 2006-06-28 |
Family
ID=32458228
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200320102482 Expired - Lifetime CN2791283Y (en) | 2002-10-29 | 2003-10-29 | Variable compression reatio type engine |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP3944053B2 (en) |
| CN (1) | CN2791283Y (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100343497C (en) * | 2002-10-29 | 2007-10-17 | 本田技研工业株式会社 | Variable reduction ratio enqine |
| CN102086811A (en) * | 2009-12-02 | 2011-06-08 | 现代自动车株式会社 | Variable compression ratio device |
| CN110159426A (en) * | 2019-06-28 | 2019-08-23 | 长城汽车股份有限公司 | The assembly method and engine of engine |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5515045B2 (en) * | 2010-01-29 | 2014-06-11 | スターテング工業株式会社 | Small engine starter |
| JP5898776B2 (en) * | 2012-09-13 | 2016-04-06 | 川崎重工業株式会社 | Turbocharged engine |
| CN104619967B (en) | 2012-09-13 | 2017-10-27 | 川崎重工业株式会社 | Engine with booster |
| BR112017000582B1 (en) * | 2014-07-14 | 2022-04-12 | Nissan Motor Co., Ltd | Internal combustion engine with variable compression ratio |
-
2002
- 2002-10-29 JP JP2002313706A patent/JP3944053B2/en not_active Expired - Fee Related
-
2003
- 2003-10-29 CN CN 200320102482 patent/CN2791283Y/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100343497C (en) * | 2002-10-29 | 2007-10-17 | 本田技研工业株式会社 | Variable reduction ratio enqine |
| CN102086811A (en) * | 2009-12-02 | 2011-06-08 | 现代自动车株式会社 | Variable compression ratio device |
| CN102086811B (en) * | 2009-12-02 | 2015-03-25 | 现代自动车株式会社 | Variable compression ratio device |
| CN110159426A (en) * | 2019-06-28 | 2019-08-23 | 长城汽车股份有限公司 | The assembly method and engine of engine |
| CN110159426B (en) * | 2019-06-28 | 2021-04-20 | 长城汽车股份有限公司 | Engine assembling method and engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2004150286A (en) | 2004-05-27 |
| JP3944053B2 (en) | 2007-07-11 |
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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 |
Effective date of abandoning: 20031029 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |