CN1719064A - V-belt continuously variable speed changer - Google Patents

Abstract

The present invention provides a V-belt type continuously variable transmission in which one end of a slide gear is coupled to a movable pulley half body of a drive pulley so as to be relatively immovable in the axial direction and relatively rotatable around the axial line and the inner periphery of the slide gear threadedly engaged with the outer periphery of a cylindrical screw shaft in which the position of the axial direction and the position around the axial line are consistent, wherein a sealing function of a seal member between the inner periphery of a cover and the outer periphery of the slide gear is prevented from being deteriorated due to an abrupt pressure increase while avoiding the upsizing of a transmission case by employing a relatively small cover. The V-belt type continuously variable transmission is provided with an end wall 116a fixed to a screw shaft 115, formed in a bottomed cylindrical shape and equipped with an annular seal member 124 between the outer periphery of the slide gear 114 band the inner periphery of a cover 116 covering a screwing part of the slide gear 114 and a screw shaft 115. A communication hole 126 for communicating with the outside an annular chamber 123 formed in the cover 116 so as to be faced to the end of the slide gear 114, is provided to the screw shaft 115.

Description

V-belt continuously variable speed changer

technical field

The present invention relates to a V-belt type continuously variable transmission in which a belt groove is formed between a movable pulley half constituting a drive pulley together with a fixed pulley half fixed to an input shaft and the fixed pulley half In the belt groove, an annular V-shaped belt that transmits power to the driven pulley side installed on the output shaft is hung. In order to change the width of the belt groove, the half body of the movable pulley can move relatively in the axial direction. The input shaft is fixedly coupled to the input shaft in a manner that cannot rotate relative to the input shaft, and one end of the sliding gear that can slide in the axial direction of the input shaft is connected to the movable shaft so that it can relatively rotate about the axis and cannot move relatively in the axial direction. On the pulley half, the inner circumference of the sliding gear is screwed to the outer circumference of a cylindrical threaded shaft arranged coaxially with the input shaft, and the axial position and the position around the axis are constant.

Background technique

Such a V-belt type continuously variable transmission is known in, for example, Patent Document 1 or the like.

Patent Document 1: Japanese Patent No. 2967374

In such a V-belt type continuously variable transmission, it is necessary to avoid the phenomenon that dust intrudes into the sliding support portion of the sliding gear or the threaded portion of the sliding gear and the threaded shaft, causing the movement to be unsmooth. In the device disclosed in the above-mentioned Patent Document 1, The whole slide gear and the threaded portion of the slide gear and the threaded shaft are covered by a large cover. However, accommodating such a large cover in the transmission will result in an increase in the size of the transmission.

The intrusion of dust to the sliding bearing part of the sliding gear can be prevented by using a sealing member, as long as only the screwing part of the sliding gear and the hub is covered with a smaller cover, and a ring-shaped seal is installed between the inner circumference of the cover and the outer circumference of the sliding gear. The sealing part can avoid the enlargement of the gearbox. However, when the movable sheave half of the drive pulley is moved quickly to the side where the width of the belt groove is increased in order to change the gear stage from TOP to LOW quickly, the opposite direction is faced to the movable sheave half. The volume of the annular chamber formed in the cover will shrink rapidly, and the annular chamber will be pressurized rapidly, which may damage the seal between the inner circumference of the cover and the outer circumference of the sliding gear. The sealing function of the component.

Contents of the invention

The present invention was made in view of the above-mentioned problems, and its object is to provide a V-belt type continuously variable transmission, which avoids the enlargement of the gearbox by using a small cover, and at the same time, does not damage the cover due to rapid pressurization. The sealing function of the sealing member between the inner circumference of the sliding gear and the outer circumference of the sliding gear.

In order to achieve the above functions, the first aspect of the present invention provides a V-belt type continuously variable speed changer, which forms the movable pulley half of the driving pulley together with the fixed pulley half fixed on the input shaft and the fixed pulley. A belt groove is formed between the pulley halves, and an annular V-shaped belt that transmits power to the driven pulley side installed on the output shaft is hung in the belt groove. In order to change the width of the belt groove, the movable pulley The half body is connected to the input shaft so that it can move relatively axially but can not rotate relatively. One end of the sliding gear that can slide along the axial direction of the input shaft is connected to the On the movable pulley half, the inner circumference of the sliding gear is screwed with the outer circumference of a cylindrical threaded shaft arranged coaxially with the input shaft, and the axial position and the position around the axis are fixed, and its It is characterized in that, between the inner periphery of the cover having the end wall fixed to the threaded shaft, forming a bottomed cylindrical shape, covering the screwed part of the sliding gear and the threaded shaft, and the outer periphery of the sliding gear A ring-shaped sealing member is interposed therebetween, and a communication hole is provided on the threaded shaft or the cover so that the annular chamber formed in the cover facing the other end of the sliding gear communicates with the outside.

The second aspect of the present invention is based on the first aspect. The threaded shaft coaxially surrounds the input shaft at a certain axial position relative to the input shaft, and an anti-vibration component is installed between it and the gearbox, so that Orientation relative to the direction of rotation about its axis.

According to the invention described in claim 1, by covering the threaded portion of the slide gear and the threaded shaft with the cover, and installing an annular seal member between the inner circumference of the cover and the outer circumference of the slide gear, it is possible to use a small cover to prevent It is possible to avoid the phenomenon that the operation is not smooth due to the intrusion of dust, and the size of the gearbox can be avoided. Moreover, since the annular chamber in the cover communicates with the outside through the communication hole, the rapid pressurization of the annular chamber is avoided, and the relationship between the inner circumference of the cover and the outer circumference of the sliding gear will not be damaged due to the rapid pressurization. The sealing function of the sealing parts between.

According to the invention described in claim 2, the load received from the sliding gear in the axial direction of the threaded shaft does not act on the anti-vibration member, but only the load in the direction of rotation of the threaded shaft acts on the anti-vibration member. Therefore, it is possible to Extend the life of the anti-vibration parts and reduce the size of the anti-vibration support structure of the threaded shaft.

Description of drawings

Fig. 1 is the side view of the power plant and rear wheel of the first embodiment;

Fig. 2 is the 2-2 line sectional view of Fig. 1;

Fig. 3 shows the enlarged view near the driving pulley of Fig. 2 in the LOW state;

Fig. 4 is a side view of the threaded shaft and the support plate seen from the side of the movable pulley;

Fig. 5 is a sectional view corresponding to Fig. 3 in the TOP state;

Fig. 6 is an enlarged sectional view showing a part of the gear reduction mechanism;

Fig. 7 is a sectional view of line 7-7 of Fig. 6;

Figure 8 is a view of the cover part viewed from the same direction as Figure 7;

Fig. 9 is a view of the cover part viewed from the side opposite to Fig. 8;

Fig. 10 is a sectional view corresponding to Fig. 3 of the second embodiment.

Symbol Description

16 Crankshaft as input shaft

51 gearbox

58 drive pulley

59 driven pulley

61 output shaft

62 fixed pulley half

63 Movable pulley half

64 slotted

114 sliding gear

115 threaded shaft

116 cover

116a end wall

120 Anti-vibration rubber as an anti-vibration part

123 donut

124 sealing parts

126, 159 Connecting hole

MV belt type continuously variable speed changer

Detailed ways

Next, embodiments of the present invention will be described with reference to embodiments of the present invention shown in the drawings.

Fig. 1～Fig. 9 shows the first embodiment of the present invention, Fig. 1 is the side view of power unit and rear wheel, Fig. 2 is the 2-2 line sectional view of Fig. 1, Fig. 3 shows the driving of Fig. 2 in LOW state Figure 4 is a side view of the threaded shaft and support plate seen from the side of the movable pulley, Figure 5 is a cross-sectional view corresponding to Figure 3 in the TOP state, and Figure 6 is an enlarged view of a part of the gear reduction mechanism Fig. 7 is a sectional view of line 7-7 in Fig. 6, Fig. 8 is a view of the cover part seen from the same direction as Fig. 7, and Fig. 9 is a view of the cover part seen from the opposite side of Fig. 8 picture.

First, in FIG. 1 and FIG. 2 , the power plant is composed of an engine E disposed in front of the rear wheel WR as a driving wheel, and a V-belt type continuously variable transmission M disposed between the engine E and the rear wheel WR. P is mounted on a vehicle body frame (not shown) of a small motorcycle, and the rear wheel WR arranged on the right side of the rear portion of the power unit P is pivotally supported on the rear portion of the power unit P.

The engine main body 11 of the engine E includes: a crankcase 12 rotatably supporting a crankshaft 16 having an axis of rotation parallel to the axis of rotation of the rear wheel WR; a cylinder block 13 combined with the crankcase 12; The cylinder block 13 is joined on the side opposite to the crankcase 12 ; and the cylinder head cover 15 is joined to the cylinder head 14 on the side opposite to the cylinder block 13 .

The cylinder block 13 is arranged such that the axis line of the cylinder bore 17 provided on the cylinder block 13 is substantially horizontal along the front-rear direction of the motorcycle and slightly inclined forward and upward. In addition, the crankcase 12 is composed of a pair of box halves 12a, 12b combined on a plane including the cylinder axis and perpendicular to the axis of the crankshaft 16, and one of the two box halves 12a, 12b is connected to the crankshaft 16. A ball bearing 18 is provided between them, and a roller bearing 19 and an annular seal member 20 disposed outside the roller bearing 19 are provided between the other case half 12 b and the crankshaft 16 .

A piston 21 is slidably fitted in the cylinder bore 17 , and the crankshaft 16 is connected to the piston 21 via a crank pin 37 and a connecting rod 38 . A combustion chamber 23 is formed between the cylinder head 14 and the above-mentioned piston 21 . An intake valve 24 for controlling intake air into the combustion chamber 23 and an exhaust valve 25 for controlling exhaust gas from the combustion chamber 23 are arranged on the cylinder head 14 such that they are aligned on a plane perpendicular to the rotation axis of the crankshaft. They are roughly arranged in a V shape on the projection diagram. Also, a spark plug 26 facing the combustion chamber 23 is attached to the left side of the cylinder head 14 in a state facing forward in the direction in which the motorcycle travels.

Between the cylinder head 14 and the cylinder head cover 15 is accommodated a valve train 30, which drives and opens and closes the intake valve 24 and the exhaust valve 25, has an axis parallel to the axis of the crankshaft 16, and can rotate freely. It is supported by the cylinder head 14 and includes a camshaft 27 having intake and exhaust cams 28 and 29 .

A driven sprocket 31 is fixed to one end of the camshaft 27 . On the other hand, on the crankshaft 16, a first driving sprocket 32 is fixed at a position corresponding to the above-mentioned driven sprocket 31 on the outside of the ball bearing 18, and an annular sprocket 32 is hung on the first driving sprocket 32 and the driven sprocket 31. The camshaft chain 33 is accommodated in a chain chamber 34 formed in the cylinder block 13 , the cylinder head 14 , and the cylinder head cover 15 so that the camshaft chain 33 can move. The camshaft 27 is driven to rotate at a rotational speed of 1/2 of the rotational speed of the crankshaft 16 by the first driving sprocket 32 , the driven sprocket 31 , and the camshaft drive chain 33 .

On the outside of the first drive sprocket 32 a second sprocket 40 is fastened to the crankshaft 16 . On the other hand, an oil pump 41 (see FIG. 1 ) that draws oil from the lower part of the crankcase 12 and a cooling water pump that circulates cooling water through a cooling water jacket 43 provided on the cylinder block 13 and the cylinder head 14 42 (see FIG. 1 ) is coaxially connected and provided at the lower part of the crankcase 12, and the rotational power is transmitted from the second drive sprocket 40 to the above-mentioned oil pump 41 and the above-mentioned cooling water pump 42 through a transmission chain (not shown).

A generator 46 having a stator 47 fixed to a right cover 45 attached to the right side of the crankcase 12 and an outer rotor 48 fixed to the crankshaft 16 surrounding the stator 47 is disposed outside the second drive sprocket 40 .

Between the second driving sprocket 40 and the above-mentioned outer rotor 48, a driven gear 49 coaxially surrounding the crankshaft 16, and relatively rotatably supported on the crankshaft 16 is arranged, and the driven gear 49 is provided via a one-way clutch 50 It is connected to the above-mentioned outer rotor 48 . Moreover, the driven gear 49 can be input with rotational power from a starter motor not shown, and when the generator E is started, the drive force from the starter motor is transmitted to the crankshaft 16. After the generator E is started, due to the single It acts on the clutch 50 without transmitting the power from the crankshaft 16 to the starter motor side.

The V-belt type continuously variable transmission M is housed in a housing chamber 56 that covers a part of the generator body 11 from the side and is connected to the generator body 11 and extends to the gearbox 51 on the left side of the rear wheel WR. 51 includes: an inner case 52 integrally connected with the case half 12b of the pair of case halves 12a, 12b constituting the crankcase 12; an outer case 53 covering the inner case 52 from the outside; a cover plate 54 on the The outer box 53 is fastened to the rear of the inner box 52; the reduction gear box 55, which is sandwiched between the inner box 52 and the front of the outer box 53, is formed and accommodated between the inner box 52 and the cover plate 54. Chamber 56 is isolated from gear chamber 57.

The V-belt type continuously variable transmission M includes: a driving pulley 58 attached to the other end of the crankshaft 16 as an input shaft protruding from the crankcase 12 into the storage chamber 56; a driven pulley 59 having and The parallel axis of the crankshaft 16 is attached to an output shaft 61 rotatably supported by the inner case 52 and the cover plate 54 ;

The driving pulley 58 has a fixed pulley half body 62 fixed to the crankshaft 16 and a movable pulley half body 63 that can be approached and separated relative to the fixed pulley half body 62. The width of the belt groove 64 between the wheel half body 62 and the movable pulley half body 63 changes, and the power to drive the above-mentioned movable pulley half body 62 in the axial direction is transmitted from the electric motor 65 installed in the gearbox 51 through gears. The reduction mechanism 66 is transmitted to the above-mentioned movable pulley half body 63 .

In addition, the driven pulley 59 includes: an inner cylinder 70 that is relatively rotatable and coaxially surrounds the output shaft 61; an outer cylinder 71 that is relatively rotatable around the axis and relatively movable in the axial direction, and is slidably fitted into the inner cylinder. 70; the fixed pulley half body 72, which is fixed on the inner cylinder 70; the movable pulley half body 73, which is opposite to the fixed pulley half body 72, is fixed on the outer cylinder 71; the torque cam mechanism 74, It is arranged between the inner cylinder 70 and the outer cylinder 71, and according to the relative rotational phase difference between the movable pulley half 73 and the fixed pulley half 72, an axial force acts between the two pulley halves 72, 73. Partial force; spring bracket part 75, is fixed on the inner cylinder 70 at the position sandwiching movable pulley half body 73 between it and fixed pulley half body 72; Coil spring 76, it surrounds outer cylinder 71, is compressed in can Between the driving pulley half body 73 and the spring support part 75; the centrifugal clutch 77, which is arranged between the inner cylinder 70 and the output shaft 61, forms a power transmission state as the generator speed exceeds the set speed, and the V-shaped belt 60 is hung It is mounted on the belt groove 78 formed between the fixed pulley half body 72 and the movable pulley half body 73 of the driving pulley 58 .

Furthermore, the gap between the fixed sheave half 72 and the movable sheave half 73 of the driven pulley 59 is determined by the axial force generated by the torque cam mechanism 74 and the axial elastic force generated by the coil spring 76 . , and acting on the balance of the force from the V-belt 60 in the direction of expanding the distance between the fixed pulley half body 72 and the movable pulley half body 73. In the driving pulley 58, when the movable When the pulley half body 63 approaches the fixed pulley half body 62 to increase the hanging radius of the V-shaped belt 60 to the driving pulley 58, the hanging radius of the V-shaped belt 60 to the driven pulley 59 decreases.

The axle 79 of the rear wheel WR is rotatably supported on the cover plate 54 and the inner cover 52, and the end of the axle 79 protruding from the transmission 51 is connected to the engine main body 11, and is rotatably supported on the right side of the rear wheel WR. side support arm 80.

In the gear chamber 57, a reduction gear train 81 arranged between the output shaft 61 and the axle shaft 79 is accommodated. The reduction gear train 81 includes: a first gear 82, which is disposed on the output shaft 61; a second gear 84, which is connected to the output shaft 61; The shaft 61 and the axle shaft 79 are parallel, arranged on the intermediate shaft 83 rotatably supported on the inner box 52 and the cover plate 54, and meshed with the first gear 82; the third gear 85 is arranged on the intermediate shaft 83; A gear 86 , which meshes with the third gear 85 , is provided on the axle 79 .

On the side wall of the part of the outer case 53 of the gearbox 51 that is opposite to the above-mentioned driving pulley 58, an external air inlet 88 for allowing cooling air to enter the storage chamber 56 is provided. The outer circumference of the pulley half body 62 is integrally provided with a cooling fan 89 for dispersing the cooling air entering from the outside air inlet 88 into the storage chamber 56 .

The outer surface of the gearbox 51 is covered by a box cover 90 and a soundproof cover 91. The box cover 90 covers the outer surface of the front half of the gearbox 51 including the part where the above-mentioned external air inlet 88 is arranged, and is fastened to the gearbox at multiple positions. On the outer case 53 of 51, the soundproof cover 91 covers the outer surface of the rear half of the gearbox 51 on the side corresponding to the driven pulley 59, and is fastened on the outer case 53 of the gearbox 51 at multiple positions.

Moreover, the front edge portion of the soundproof cover 91 is covered by the rear edge of the case cover 90, and the case cover 90 and the soundproof cover 91 are installed on the gearbox 51, and the two bosses 91a... Between the rear part of the case cover 90 and the transmission case 51, the rear edge part of the case cover 90 and the front edge part of the soundproof cover 91 are both fastened to the transmission case 51 by the screw member 92.... In addition, an air inlet 93 opened on the rear side is formed between the rear edge portion of the box cover 90 and the front edge portion of the soundproof cover 91, and an air inlet communicating with the air inlet 93 is formed between the box cover 90 and the transmission case 51. Room 94.

The above-mentioned outside air inlet 88 is blocked from the side of the air introduction chamber 94, and the filter 95 is installed on the outer surface of the gearbox 51, and the outside air introduced into the air introduction chamber 94 from the air inlet 93 is purified by the filter 95, Inhale into the storage chamber 56 .

Between the gearbox 51 and the soundproof cover 91, the space between the gearbox 51 and the soundproof cover 91 is divided into a plurality of, for example, three closed spaces 96, 97, 98, and for example, four soundproof parts 99, 100, 101, 102 are arranged. .

Each sound-insulating member 99-102 is formed into a line shape by cutting and forming a polyurethane sheet, and one side of these sound-insulating members 99-102 is bonded to one of the transmission case 51 and the sound-insulating cover 91 by an adhesive, and in this embodiment, the bonding In the inner surface of the soundproof cover 91.

In this way, the space between the gearbox 51 and the sound-proof cover 91 is divided into a plurality of closed spaces 96-98 by the sound-insulating members 99-102, so that the noise emitted from the gearbox 51 is controlled by the sound-insulating components arranged between the gearbox 51 and the sound-proof cover 91. Components 99 to 102 are absorbed and suppressed, and at the same time, multiple closed spaces 96 to 98 formed between the transmission case 51 and the soundproof cover 91 prevent and suppress the resonance of sound, so that sufficient noise prevention can be obtained with a simple structure. Effect.

In FIG. 3 , in the part facing the storage chamber 56 in the transmission case 51 , the crankshaft 16 is provided with an outwardly facing annular section 16 a , and a cylinder coaxially surrounding the crankshaft 16 that cannot rotate around the axis with the crankshaft 16 The inner view of the sealed ball bearing 105 is sandwiched between the inner end of the ring-shaped sleeve 104 and the above-mentioned annular shoulder 16a. In addition, the nut 106 is screwed on the outer end of the crankshaft 16, and the fixed pulley half body 62 of the driving pulley 58 is installed on the crankshaft 16 so that it cannot rotate relatively. Between the outer ends of the barrel 104 , the fixed pulley half 62 is fixed to the crankshaft 16 by fastening nuts 106 .

The movable pulley half body 63 of the driving pulley 58 integrally has a cylindrical portion 63a coaxially surrounding the above-mentioned sleeve 104, and is fitted in a guide hole 108 extending in the axial direction at one place in the circumferential direction of the cylindrical portion 63a. The key 109 engaged with the above-mentioned sleeve 104 is engaged. As a result, the movable sheave half 63 cannot rotate around the axis on the sleeve 104, that is, the crankshaft 16, and at the same time, can perform relative movement in the axis direction. Furthermore, since the guide hole 108 is provided at one place in the circumferential direction of the cylindrical portion 63a, the gap between the key 109 and the key groove can be reduced, thereby reducing the load on the key 109 due to looseness. In addition, an annular seal member 110 is interposed between the inner end of the cylindrical portion 63 a and the sleeve 104 .

The movable pulley half body 63 is equipped with a cylindrical supporting cylinder 111 coaxially surrounding its cylindrical portion 63a, which cannot move relative to the axial direction, but can rotate relatively. Ring-shaped seal members 112 , 112 are attached between the cylindrical portion 63 a and the support cylinder 111 at two positions of the hole 108 .

The inner ring of the sealed ball bearing 113 is attached to the outer periphery of the support cylinder 111 so that it cannot move relatively in the axial direction, and the outer ring of the ball bearing 113 is held by the driven gear as the reduction gear mechanism 66 so that it cannot move relatively in the axial direction. The inner circumference of one end of the sliding gear 114 . That is, one end of the slide gear 114 movable in the axial direction of the crankshaft 16 is connected to the movable pulley half body 63 so that it cannot relatively rotate in the axial direction but can relatively rotate about the axis through the sealed ball bearing 113. .

The outer ring of the sealed ball bearing 105 is held on the inner periphery of a cylindrical threaded shaft 115 coaxially surrounding the crankshaft 16 such that it cannot move relative to the axial direction. That is, the threaded shaft 115 is a threaded shaft coaxially surrounding the crankshaft 16 at a fixed axial position, and three helical grooves 117... are provided on the outer periphery of the threaded shaft 115, and the inner periphery of the other end of the above-mentioned sliding gear 114 is connected to the inner periphery of the above-mentioned threaded shaft 115. Peripheral screwing.

Referring to Fig. 4 again, on the above-mentioned threaded shaft 115, a support plate 118 is fixed, and at a position deviated from the axis of the above-mentioned crankshaft 16, a cylindrical mounting tube 119 having an axis parallel to the crankshaft 16 is fixed on the above-mentioned support plate 118. .

A cylindrical collar 121 with a cylindrical anti-vibration rubber 120 thermally bonded to the outer periphery is inserted into the above-mentioned installation cylinder 119, and the bolt 122 inserted through the collar 121 is screwed and fastened to the transmission case 51. On the inner box 52 of the inner side, the support plate 118, namely the threaded shaft 115, is positioned in the gearbox 51 through the above-mentioned anti-vibration rubber 120 relative to the rotation direction around the threaded shaft 115 axis.

The slide gear 114 screwed to the threaded shaft 115 positioned in the axial direction of the crankshaft 16 and not required to rotate around the axis is rotated by the power transmitted from the electric motor 65 through the reduction gear mechanism 66, so that the movable pulley half 63 is shown in FIG. 3 and the TOP position shown in FIG. 5 , the support plate 118 is integrally provided with a movable pulley half body 63 that is engaged with the sliding gear 114 at the LOW position. The stopper 118a at the moving end that moves to the LOW position, and the stopper 128 at the moving end that restricts the movement of the movable sheave half body 63 to the TOP position side by engaging with the slide gear 114 at the TOP position are fixed inside the transmission case 51 box 52.

The threaded portion of the threaded shaft 115 and the sliding gear 114 is covered by a bottomed cylindrical cover 116 having an end wall 116a fixed to the threaded shaft 115. Between the inner circumference of the cover 116 and the outer circumference of the sliding gear 114, An annular seal member 124 is interposed therebetween.

However, an annular chamber 123 facing the other end of the sliding gear 114 is formed in the cover 116. The volume of the annular chamber 123 corresponds to the position between the LOW position and the TOP position of the movable pulley half 63 and the sliding gear 114. changes along the axial movement. Moreover, when the movable sheave half body 63 is rapidly moved to the side where the width of the belt groove 64 is increased in order to change the shift speed from TOP to the LOW side rapidly, the volume of the annular chamber 123 is rapidly contracted. Rapid pressurization of the annular chamber 123 may impair the sealing function of the seal member 124 between the inner periphery of the cover 116 and the outer periphery of the slide gear 114 .

Therefore, in order to make the above-mentioned annular chamber 123 and the outer circumference of the sleeve 104, the inner circumference of the threaded shaft 115, the inner circumference of the slide gear 114, the inner end of the cylindrical portion 63a of the movable pulley half 63 and the support cylinder The cavity 125 side defined by the outer circumference of 111 communicates, and the side wall of the threaded shaft 115 is provided with a communication hole 126 that communicates with the above-mentioned annular chamber 123. The other end communicates with the recessed portion 125 of the cavity 125 .

Although the volume of the empty chamber 125 also changes in response to the axial movement of the movable sheave half 63 and the slide gear 114 between the LOW position and the TOP position, the empty chamber 125 changes when the transmission stage is changed from the TOP to the LOW side. The volume change ratio of the chamber 125 is smaller than that of the above-mentioned annular chamber 123, and when the shift gear is changed from TOP to the LOW side, the degree of pressure increase in the annular chamber 123 is due to the communication between the annular chamber 123 and the empty chamber 125. suppressed to a lesser extent.

Referring to Fig. 6 again, the gear reduction mechanism 66 has at least a drive gear 130 coaxially connected to the electric motor 65, and an idle gear 131 and a pinion gear 132 meshed with the drive gear 130 are integrally provided on an idle rotation shaft 133 to form an idle gear. Gear 134. In this embodiment, the above-mentioned gear reduction mechanism 66 also has a second idle gear 135 arranged between the above-mentioned pinion gear 132 and the above-mentioned sliding gear 114. The bull gear 136 and the pinion gear 137 formed integrally with the bull gear 136 and meshing with the slide gear 114 are constituted.

Parts of the inner case 52 and the reduction gear case 55 constituting a part of the transmission case 51 protrude toward the front side of the cylinder head 14 than the outer case 53, and are defined by the portion of the peripheral wall portion 55a of the reduction gear case 55 that protrudes forward than the outer case 53. A through hole 138 having a substantially half circumference is provided on the reduction gear 55 . On the other hand, a mounting plate 139 having a cylindrical portion 139a airtightly fitted into the above-mentioned through hole 138 is fastened to the outside of the reduction gear box 55 by a plurality of bolts 140 . The electric motor 65 is fixed on the mounting plate 139, and the rotating shaft 141 penetrates the cylindrical portion 139a and protrudes into the gearbox 51. Also, the driving gear 130 is integrally formed with the rotation shaft 141 .

Cylindrical bearing brackets 142, 143 for rotatably supporting both ends of the idle rotation shaft 133 of the idle gear 134 are protruded coaxially and opposed to each other in the reduction gear box 55 and the inner box 52. Both ends of the rotating shaft 133 are rotatably supported by the two bearing brackets 142 , 143 via ball bearings 144 , 145 .

In addition, on the inner surface of the reduction gear box 55, a part of the peripheral wall portion 55a of the reduction gear 55 cooperates with a part of the peripheral wall portion 55a of the reduction gear 55 to surround the drive gear 130 connected to the electric motor 65, and constitutes a part of the idle gear 134 and meshes with the drive gear 130. The wall portion 55b of the large gear 131 .

A cover member 147 is attached to the reduction gear case 55 to form a reduction gear chamber 146 for housing the drive gear 130 and the bull gear 131 from the storage chamber 56 in the transmission case 51 between the reduction gear case 55 and the reduction gear case 55 .

Referring to FIGS. 7 to 9 again, the cover member 147 covers the end portion of the above-mentioned wall portion 55b of the reduction gear case 55, and is opposed to the inner periphery of the above-mentioned peripheral wall portion 55a. The end portion of the portion 55b is in contact with the seal rubber 148 that is in contact with the inner surface of the peripheral portion 55a.

In the reduction gear box 55, mounting portions 149, 150 are provided on the wall portion 55b and the outer inner surface of the wall portion 55b, and a flat mounting arm portion 147a and a flat mounting arm portion 147a contacting the mounting portion 149 are integrally provided on the cover member 147. The mounting arm portion 147b bent in contact with the mounting portion 150 is fastened to the mounting portion 149, 150 by screwing and fastening the bolts 152 inserted through the insertion holes 151... The cover member 147 is attached to the reduction gear case 55 .

In addition, a cylindrical portion 147c forming a circular opening 153 penetrating through the pinion 132 of the idle gear 134 protrudes from the cover member 147 to protrude into the reduction gear chamber 146, and the front end of the cylindrical portion 147c is inserted. The annular groove 131 a provided in the large gear 131 of the idle gear 134 forms a labyrinth passage 154 between the cover member 147 and the large gear 131 .

Then, in FIG. 3 and FIG. 5 , the second idle gear 135 is rotatably supported by the inner case 52 and the reduction gear case 55 of the transmission case 51, which are installed at both ends by pins 157 and retaining rings 158 to limit axial movement. on the metal rotating shaft 156.

Further, a gear 165 is integrally provided at the end of the rotating shaft 156 on the reduction gear case 55 side, and a worm 167 provided on a stroke sensor shaft 166 rotatably supported by the reduction gear case 55 meshes with the gear 165 . The stroke sensor shaft 166 is connected to a stroke sensor not shown in the figure, and the stroke of the movable pulley half body 63 in the driving pulley 58 is detected by the rotating part of the second idle gear 135 constituting a part of the reduction gear mechanism 66, so the driving force can be improved. The maintainability of the pulley 58 can improve the stroke detection accuracy.

However, in the drive gear 130, the idle gear 134, the second idle gear 135, and the slide gear 114 constituting the reduction gear mechanism 66, the second idle gear 135 is formed of a self-lubricating resin, and the drive gear 130, the idle gear 134, and the slide gear 114 is a metal gear.

The action of this first embodiment will be described below. One end of a sliding gear 114 that can slide in the axial direction of the crankshaft 16 is connected to the movable pulley half 63 constituting a part of the driving pulley 58 so that it cannot move relative to the axial direction but can relatively rotate around the axis. The position and the position around the axis are fixed, and the outer circumference of the cylindrical threaded shaft 115 arranged coaxially with the crankshaft 16 is screwed with the inner circumference of the sliding gear 114, and has a bottomed cylindrical shape with an end wall 116a fixed to the threaded shaft 115. An annular seal member 124 is provided between the inner periphery of the cover 116 that covers the screwed portion of the sliding gear 114 and the threaded shaft 115 and the outer periphery of the sliding gear 114 .

Therefore, by using a small cover 116 , it is possible to prevent the movement of the screwed portion of the slide gear 114 and the threaded shaft 115 from being unsmooth due to intrusion of dust, and it is possible to avoid an increase in the size of the transmission case 51 .

And since the communication hole 126 that makes the annular chamber 123 formed in the cover 116 facing the other end of the sliding gear 114 communicate with the external cavity 125 is provided on the threaded shaft 115, so the rapid increase of the annular chamber 123 can be avoided. The rapid pressurization prevents damage to the sealing function of the seal member 124 between the inner periphery of the cover 116 and the outer periphery of the slide gear 114.

In addition, the above-mentioned threaded shaft 115 having a fixed axial position with respect to the crankshaft 16 and coaxially surrounding the crankshaft 16 can be prevented from rotating around its axis by installing anti-vibration rubber 120 between it and the inner case 52 of the transmission case 51. Therefore, the load received from the sliding gear 114 in the axial direction of the threaded shaft 115 does not act on the anti-vibration rubber 120, and only the load in the direction of rotation of the threaded shaft 115 acts on the anti-vibration rubber 120. The life of the anti-vibration rubber 120 can be extended, and the anti-vibration support structure of the threaded shaft 115 can be miniaturized.

In addition, between the electric motor 65 and the movable pulley half body 63 of the drive pulley 58, the reduction gear mechanism 66 accommodated in the transmission case 51 has at least a drive gear 130 coaxially connected to the electric motor 65, and a The large gear 131 and the pinion 132 meshed with the driving gear 130 are integrally provided with the idle gear 134 formed on the idle rotation shaft 133, and the reduction gear chamber 146 is formed between the cover member 147 and the reduction gear box 55 of the transmission case 51 to reduce the speed of the drive gear. The gear chamber 146 is defined from the storage chamber 56 in the transmission case 51, and accommodates the drive gear 130 and the large gear 131. A labyrinth passage 154 is formed between the cover member 147 and the large gear 131, and an opening through the small gear 132 is formed. 153, installed on the reduction gear box 55 of the transmission case 51, therefore, the smaller cover member 147 can be used to prevent the intrusion of dust in the reduction gear mechanism 66, especially in the meshing parts of the driving gear 130 and the idle gear 134 with a large number of meshing times. , can avoid the enlargement of the gearbox 51, and improve the life of the reduction gear mechanism 66.

In addition, a bearing bracket 142 that rotatably supports one end of the idle rotation shaft 133 is provided on the reduction gear case 55 constituting a part of the transmission case 51, and at the same time, the mounting parts 149 and 150 of the cover member 147 are provided, so that the size can be reduced. The labyrinth passage 154 is formed in such a way that the sealing performance can be improved. In addition, as in this embodiment, when both ends of the idle rotation shaft 133 of the idle gear 134 are rotatably supported on the reduction gear case 55 and the inner cover 52, by assembling the V-belt type continuously variable transmission M The idle gear 134 is retained by the cover member 174 on the side of the reduction gear case 55 so that the assemblability can be improved.

In addition, the reduction gear mechanism 66 includes a second idle gear 135 formed of a self-lubricating resin that is installed between the pinion gear 132 and the slide gear 114 of the metal idle gear 134. In the reduction gear mechanism 66, the reduction gear chamber The gear meshing part outside 146 can be lubricated with resin to simplify the lubrication structure. In addition, the second idle gear 135 made of resin is arranged in a wide space outside the reduction gear chamber 146 in the transmission 51 to improve cooling performance. .

Fig. 10 shows the second embodiment of the present invention, the threaded shaft 115 positioned in the axial direction of the crankshaft 16 and not rotating around the axis and the threaded part of the slide gear 114 have an end wall 116a fixed to the threaded shaft 115 and form a bottomed shaft. It is covered by a cylindrical cover 116 , and an annular seal member 124 is interposed between the inner periphery of the cover 116 and the outer periphery of the slide gear 114 .

In order to make the annular chamber 123 formed in the cover 116 at the other end facing the sliding gear 114 communicate with the storage chamber 56 in the gearbox 51, a communication hole 159 with one end communicating with the upper part of the annular chamber 123 is provided at the end of the cover 116. On the portion 116 a and the support plate 118 , a communication hole cover 160 that covers the other end of the communication hole 159 and opens upward is fixed on the outer surface of the support plate 118 .

According to this second embodiment, in order to quickly change the shift stage from TOP to LOW, the movable sheave half 63 is quickly moved to the side where the width of the belt groove 64 is increased, thereby even the ring-shaped The rapid contraction of the volume of the chamber 123 can also suppress the pressurization of the annular chamber 123, so that the function of the sealing member 124 between the inner periphery of the cover 116 and the outer periphery of the slide gear 114 can be prevented from being damaged due to rapid pressurization.

The embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various design changes can be made in the present invention without departing from the scope of the claims.

Claims (2)

1, a kind of V-belt formula stepless speed changer, and be fixed in fixed pulley half (62) on the input shaft (16) and constitute together between the movable pulley half (63) of driving pulley (58) and the described fixed pulley half (62) and form trough of belt (64), in described trough of belt (64), mount ring-type V-belt (60) to the driven pulley that is installed on output shaft (61) (59) side transferring power, described movable pulley half (63) can not be combined on the described input shaft (16) with the relative rotation for the change width that makes described trough of belt can axially relatively move, one end of the sliding gear (114) that can slide along the axial direction of described input shaft (16) can not axially relatively move and can be connected in the relative rotation on the described movable pulley half (63) around axis, on the periphery that is screwed on thread spindle cylindraceous (115) interior week of described sliding gear (114), described thread spindle cylindraceous (115) axial position and certain around the position of axis, with described input shaft (16) arranged coaxial, it is characterized in that, has the end wall (116a) that is fixed in described thread spindle (151), be formed with the round-ended cylinder shape, cover the sealed member (124) that ring-type is housed between the periphery of interior week of cap assembly (116) of screwing part of described sliding gear (114) and described thread spindle (115) and described sliding gear (114) simultaneously, make the other end that faces described sliding gear (114), be formed at the intercommunicating pore (126 of interior annular chamber (123) of described cover (116) and external communications, 159) be located on described thread spindle (115) or the described cover (116).

2, V-belt formula stepless speed changer as claimed in claim 1, it is characterized in that, with respect to the axial position of described input shaft (16) certain and coaxial around this input shaft (16) described thread spindle (115) and gearbox (51) between antivibrating parts (120) is housed, thereby described thread spindle (115) is located with respect to the sense of rotation around its axis.

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