JPH01224521A - ball bearing - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

Detailed Description of the Invention A0 Object of the Invention (1) Industrial Application Field The present invention provides an annular ball having a plurality of balls arranged in an annular arrangement and pockets for accommodating these balls between a pair of opposing races. This invention relates to an improvement in a ball bearing which is interposed with a retainer.

(2) Conventional technology Figures 17 and 18 show conventional angular contact type ball bearings.
A large number of balls 03゜03... in an annular arrangement interposed between a pair of opposing races 01, 02 are inserted into a large number of circular pockets 05, 05... provided in an annular glue retainer 04.
・One ball is accommodated in each ball, and the distance between adjacent balls is regulated.

(3) Problems to be Solved by the Invention In the ball bearing of the above structure, if the magnitude of the thrust load applied to the bearing is different between one half of the bearing and the other half R, the difference between the races 01 and 02 An axial moment) m is generated, and as a result, the contact angle α of each ball 03 changes as shown in FIG. That is, as shown in FIG. 19, the contact angle α increases on the side where the thrust load is large, and decreases on the opposite side. As a result, the radius of the rolling trajectory of the ball on the side where the thrust load is greater becomes shorter, and becomes longer on the opposite side.1. When both races 01 and 02 rotate relative to each other, assuming that each ball 03 is not restrained by the retainer 04 at all, the revolution angle of the balls 03 will be larger on the side where the thrust load is larger and smaller on the opposite side. Become.

However, in conventional ball bearings, all the balls 03, 03... are in the pockets 05.05 of the retainer 04.
..., the retainer 04 limits the revolution angle of the balls as described above, and as a result, a large frictional force is generated between the retainer 04 and each ball 03. The inventors have discovered that various loads are applied to the retainer from the group of balls, and that these are obstacles to prolonging the life of the bearing.

Therefore, it is conceivable to provide a large amount of play for the balls 03 in each pocket 05 of the retainer 04 to allow for the difference in the revolution angle of the balls. The number of balls 03 inevitably decreases, and therefore the number of balls 03 used decreases, reducing the load capacity of the bearing. Also, ball 03
If the retainer 04 is removed to maximize the number of balls used, there is a risk that all the balls will violently collide with each other, accelerating wear.

The present invention has been made in view of the above points, and it is possible to reduce the load capacity by hardly reducing the number of balls used, absorbing the difference in the revolution angle of the balls, and avoiding severe collisions between the balls. It is an object of the present invention to provide a ball bearing that does not deteriorate and has high durability. .

B8 Structure of the Invention (1) Means for Solving the Problems In order to achieve the above object, the present invention provides a structure in which each pocket of the retainer is configured to accommodate a plurality of balls with a prescribed play in the circumferential direction. It is characterized by being formed in an arc shape.

Note that the present invention is applicable to radial ball bearings, thrust ball bearings, angular contact ball bearings, and the like.

(2) Effect According to the above configuration, a large number of balls are divided into a plurality of sets by the plurality of arcuate pockets of the retainer, and the intervals between the sets of balls are regulated. Moreover, since each pocket is provided with play for one set of balls, each set of balls can freely revolve with almost no interference from the retainer or other sets of balls. The difference in the revolution angle of the ball between the ball and the other half is easily absorbed by the play within each pocket.

At that time, even if the balls collide with each other in the same pocket,
Since the number of balls stored in one pocket is small, the impact force is relatively small and does not cause any damage to the balls.

Furthermore, since the number of pockets is smaller than the number of balls, even if play is provided in each pocket, the number of balls used will be reduced due to the play, and sufficient load capacity can be ensured.

(3) Examples An embodiment of the present invention will be described below with reference to the drawings.

First, in FIG. 1, a motorcycle unit U consists of an engine E and a hydrostatic continuously variable transmission T, and the crankshaft l of the engine E and the transmission T are housed in a common casing 4. Contained and supported. The continuously variable transmission T has a human-powered cylinder shaft 5 and an output shaft 31 arranged parallel to the crankshaft 1, the crankshaft l drives the input cylinder shaft 5 via the primary reduction gear 2, and the output shaft 31 drives the input cylinder shaft 5 through the primary reduction gear 2. A rear wheel (not shown) of the motorcycle is driven via the secondary reduction gear 3.

In FIGS. 2 and 3, the continuously variable transmission T includes a constant displacement swash plate type hydraulic pump P and a variable displacement swash plate type hydraulic motor M.

The hydraulic pump P is connected to the output block 2 of the primary reduction gear 2.
a is connected to an input cylinder shaft 5 by a rivet 16; a pump cylinder 7 fitted to the inner circumferential wall of the input cylinder shaft 5 through a needle bearing 6 so as to be relatively rotatable; A large number of pump plungers 9, 9... which are slidably engaged with a large number of odd numbered cylinder holes 8, 8... arranged in an annular arrangement surrounding the axis, and these pump plungers 9,9... The pump swash plate 10 is held in a state tilted at a certain angle with respect to the axis of the pump cylinder 7 with the imaginary trunnion axis OI orthogonal to the axis of the pump cylinder 7 as the center. The pump swash plate holder 12 supports the back surface of the swash plate 10 via an angular contact ball bearing 11 according to the present invention.

Thus, when the input cylinder shaft 5 rotates, the pump swash plate 10 can cause the pump plungers 9, 9, . . . to reciprocate, thereby repeating the suction and discharge strokes.

In order to improve the ability of the pump plunger 9 to follow the pump swash plate 10, a coil spring 15 that biases the pump plunger 9 in the direction of extension is housed in the cylinder hole 8.

As shown in FIGS. 15 and 16, the angular contact ball bearing 11 includes races 131 and 132 integrally formed on opposing surfaces of the pump swash plate 10 and the pump swash plate holder 12, respectively, and these races 131. ．．
132 interposed between a large number of circular arrays (18 in the figure)
balls 133.133... and these balls 133
．． 133... and an annular retainer 134 that holds the components. The retainer 134 has a plurality of arc-shaped pockets 135 (six in the figure) arranged in a ring shape extending in the circumferential direction, and each pocket 135 accommodates a plurality of balls 133 (three in the figure). be done.

At this time, each pocket 135 is provided with a certain amount of play 136 necessary to absorb the difference in the revolution angle of the balls between one half of the bearing 11 and the other half.

Referring again to FIGS. 2 and 3, the hydraulic motor M includes a motor cylinder 17 disposed on the same axis as the pump cylinder 7 and to the left thereof, and an annular motor cylinder provided around the rotation axis of the motor cylinder 17. A large number of motor plungers 19, 19, which are respectively slid into an array of cylinder holes 18, 18, and a large number of odd numbers, and a motor swash plate that brings the outer end front surfaces of these motor plungers 19, 19, into contact. 20, a motor swash plate holder 22 that supports the back surface of this motor swash plate 20 via an angular contact ball bearing 21 according to the present invention, and a motor swash plate anchor 23 that further supports the back surface of this motor swash plate holder 22. configured. The ball bearing 21 has the same configuration as the ball bearing 11 on the hydraulic pump P side.

As clearly shown in FIG. 14, the opposing surfaces f+, f of the motor swash plate holder 22 and the motor swash plate anchor 23 that are in contact with each other
z is the axis of the motor cylinder 17 and the trunnion axis O2
It is formed into a spherical surface centered at the intersection with

Further, the motor swash plate holder 22 is integrally provided with a pair of semi-cylindrical trunnion shafts 22a, 22a at both ends, which are disposed on the trunnion axis 0□ orthogonal to the rotation axis of the motor cylinder 17, and these are attached to the motor swash plate anchor. It is rotatably engaged with a pair of semi-cylindrical recesses 23a, 23a formed at both ends of the recess 23, respectively. The trunnion shaft 22a and the recess 23a may have a shape other than a semi-cylindrical shape as long as their engagement can prevent the motor swash plate holder 22 from rotating around an axis other than the trunnion axis 02. For example, it may be in the shape of a semi-cone.

The motor swash plate anchor 23 is attached to a bolt 2 on the left side wall of the casing 4 together with a cylindrical cylinder holder 24 connected to its right end.
Fixed at 7. This cylinder holder 24 rotatably supports the outer peripheral surface of the motor cylinder 17 via a needle bearing 25 and a ball bearing 26.

The motor swash plate 20 is configured to move by rotation of the motor swash plate holder 22 between an upright position perpendicular to the axis of the motor cylinder 17 and a maximum tilt position where it is tilted at an angle. In that tilted state, as the motor cylinder 17 rotates, the motor plungers 19, 19...
It is possible to repeat the swelling and contraction processes by giving a reciprocating motion to the oil.

In order to improve the ability of the motor plunger 19 to follow the motor swash plate 2o, a coil spring 30 that biases the motor plunger 19 in the extension direction is housed in the cylinder hole 18.

The pump cylinder 7 and the motor cylinder 17 are integrally connected to each other to form a cylinder block B, and the output shaft 31 is passed through the center of the cylinder block B. Then, the outer end of the pump cylinder 7 is abutted against the two-split stopper ring 33 that is locked on the outer periphery of the output shaft 31, and the motor cylinder 17 is spline-fitted 3 to the output shaft 31.
2, the cylinder block B is fixed to the output shaft 31 by locking the circlip 35 which contacts the outer end of the motor cylinder 17 via the seat plate 34 to the output shaft 31.

The right end of the output shaft 31 also passes through the pump swash plate 10 and the pump swash plate holder 12, and integrally has a highly rigid flange 37 that supports the back surface of the pump swash plate holder 22 via a thrust roller bearing 40. We are prepared. The output shaft 31 also connects the pump swash plate holder 22 to the needle bearing 4.
It is rotatably supported via 2.

The left end of the output shaft 31 extends through the motor swash plate 20, the motor swash plate holder 22, and the motor swash plate anchor 23, and is connected to the outer periphery of this left end by a spline 43 and fixed with a splitter 44. A retainer 46 and a thrust roller bearing 47 are sequentially interposed between the support cylinder 45 and the motor swash plate anchor 23 from the swash plate anchor 23 side. Further, the output shaft 31 is rotatably supported by the swash plate anchor 23 via a needle bearing 48 and the retainer 46.

In this way, all the components of the transmission T, from the outlet block block 2a to the splitter 44, are assembled as one assembly on the output shaft 31, so that the transmission T can be attached to and removed from the casing 4. can be easily done.

When the transmission T is assembled to the casing 4, the pump swash plate holder 12 is supported on the right side wall of the casing 4 via a ball bearing 41, and the input cylinder shaft 5 is attached to a separable intermediate support of the casing 4. The motor swash plate anchor 23 is supported by the wall 4a via a ball bearing 39, and is fixed to the left side wall of the casing 4 by bolts 27. A cap 50 that closes a maintenance hole 49 opening therein is fixed to the right side wall of the casing 4 with a bolt 51, and an oil seal 56 that is in close contact with the outer peripheral surface of the support tube 45 is attached to the left side wall of the casing 4. is fitted. Furthermore, the input sprocket 3a of the secondary reduction gear 3 is fixed with bolts 38 on the outside of the casing 4. At this time, the input sprocket 3a presses the outer periphery of the splitter 44 to prevent it from coming off.

In order to rotate the pump swash plate 10 synchronously with the pump cylinder 7, the pump swash plate IO is formed with a spherical recess 10a in which the spherical end 9a of the corresponding pump plunger 9 engages.

Further, in order to rotate the motor swash plate 20 synchronously with the motor cylinder 17, a spherical recess 20a is formed in the motor swash plate 20 to accommodate the spherical end 19a of the corresponding motor plunger 19.

Each of the spherical recesses 10a, 20a is formed with a radius larger than the radius of the corresponding spherical end 9a, 19a, so that the spherical end 9a,
19a is ensured.

Furthermore, in the hydraulic motor M, the motor plunger 19
In order to ensure particularly reliable torque transmission between the motor swash plate 20 and the motor swash plate 20, the partition wall 20b between the spherical recesses 20a and 2Oa is formed in a mountain shape that protrudes toward the center (see FIGS. 11 to 13). ). Incidentally, such a structure may also be adopted on the hydraulic pump P side.

2 to 5, the cylinder block B has an output shaft 31 between the cylinder holes 8, 8... groups of the pump cylinder 7 and the cylinder holes 18, 18... groups of the motor cylinder 17. An 8-degree cylinder hole radially penetrates an annular inner oil passage 52 and an outer oil passage 53 concentrically centered on the annular partition wall between both oil passages 52 and 53 and the outer circumferential wall of the outer oil passage 53. . . . and 18.18 . . . and the same number of first valve holes 54, 54 . . . and second valve holes 55 .
55..., adjacent cylinder holes 8.8... and the first
Pump port a that communicates the valve holes 54, 54... with each other
, a..., and a large number of motor boats b, b... that communicate with each other the adjacent cylinder holes 18, 18... and second valve holes 55, 55... are provided.

The inner oil passage 52 is formed as an annular groove on the inner peripheral surface of the cylinder block B, and its open surface is closed by the outer peripheral surface of the output shaft 31.

The first valve holes 54, 54... are provided with spool-type first distribution valves 61, 61..., and the second valve holes 55, 55...
... is the same (spool type second distribution valve 62°62.
... are rubbed together. Then, the first distribution valve 61.
A first eccentric ring 63 surrounding the second distribution valves 62, 62, .
The outer ends of the first distribution valves 61, 61, . The outer end of the second distribution valve 62, 62... is connected to the second eccentric wheel 62.
, 62 . . . are interconnected by a second forcing ring 68 in a concentric relationship.

The first eccentric wheel 63 is fixed to the outer periphery of the input cylinder shaft 5 via a connecting pin 69, and is located eccentrically by a predetermined distance ε from the center of the output shaft 31 along the virtual trunnion axis 01 as shown in FIG. is maintained.

Therefore, when relative rotation occurs between the input cylinder shaft 5 and the pump cylinder 7, each first distribution valve 61 is stroked a distance twice the eccentricity ε1 in the first valve hole 54 by the first eccentric wheel 63. The pump cylinder 7 is reciprocated between a radially inner position and an outer position. As shown in FIG. 4, in the discharge area of the hydraulic pump P, the first distribution valve 61 moves to the inner position side, communicates the corresponding pump port a with the outer oil passage 53, and connects the inner side. The oil road 52 is cut off,
Hydraulic oil is force-fed from the cylinder hole 8 to the outer oil passage 53 by the pump plunger 9 during the discharge stroke, and in the suction area S, the first distribution valve 61 moves to the outer position side and closes the corresponding pump port 1- a is communicated with the inner oil passage 52 and disconnected from the outer oil passage 53, and hydraulic oil is sucked into the cylinder hole 8 from the inner oil passage 52 by the pump plunger 9 during the suction stroke.

As shown in FIGS. 5 and 6, the second eccentric wheel 64 has a pivot 3 parallel to the output shaft 31 on the cylinder holder 24.
0 to clutch on position In and clutch off position fff
are connected so as to be able to swing between them. In the clutch-on position n, the second eccentric wheel 64 is aligned with the trunnion axis o.
2, it occupies a position eccentric by a predetermined distance ε2 from the center of the output shaft 31, and at the clutch-off position f, it occupies a position eccentric by a distance ε3 larger than the eccentricity ε2 from the center of the output shaft 31. In order to regulate the position, a notch 71 is provided on the outer peripheral surface of the second eccentric ring 64, and stoppers 72 that can come into contact with both inner end surfaces of this notch 71 are integrally formed in the casing 4.

That is, when this stopper 72 comes into contact with one inner end surface of the notch 71, the clutch-on position n of the second eccentric wheel 64 is
However, by contacting the other inner end surface of the notch 71, the clutch-off position f of the second eccentric wheel 64 is regulated.

A camshaft 74 disposed parallel to the output shaft 31 is inserted into a through hole 73 formed on one side of the second eccentric wheel 64, and a slipper plate 75 that engages with this camshaft 74 is inserted through the through hole 73. It is fixed to the second eccentric wheel 64 with a port 76 so as to cover one side of the hole 73 .

As shown in FIG. 3, the camshaft 74 is supported by the casing 4 via a pair of left and right ball bearings 77, and when rotated by the operation of a clutch lever (not shown), pushes the slipper plate 75 and The second eccentric wheel 64 can be swung to the clutch-off position ilf.

Further, as shown in FIG. 5, a clutch spring 78 is connected to the second eccentric wheel 64 to bias it toward the clutch-on position n. Therefore, if the camshaft 74 is operated to retreat from the slipper plate 75, the second eccentric wheel 64 can be swung to the clutch-on position n by the force of the clutch spring 78.

Thus, when the second eccentric wheel 64 occupies the clutch-on position n (see FIG. 5), when the motor cylinder 17 rotates, each second distribution valve 62 is caused to close to the second valve hole by the second eccentric wheel 64. 55, the motor cylinder 17 is reciprocated between a radially inner position and an outer position with a stroke of twice the eccentricity ε2. Then, in the expansion region Ex of the hydraulic motor M, the second distribution valve 62 moves to the inner position side, communicates the corresponding motor port b with the outer oil passage 53, disconnects the inner oil passage 52, and disconnects the inner oil passage 52 from the outside. High-pressure hydraulic oil is supplied from the oil passage 53 to the cylinder hole 18 of the motor plunger 19 during the expansion stroke, and in the contraction region sh, the second distribution valve 62 moves to the outer position side and closes the corresponding motor port. b is communicated with the inner oil passage 52 and disconnected from the outer oil passage 53, and hydraulic oil is discharged from the cylinder hole 18 of the motor plunger 19 during the contraction stroke to the inner oil passage 52.

Further, when the second eccentric wheel 64 occupies the clutch-off position f (see FIG. 6), when the motor cylinder 17 rotates,
Each second distribution valve 62 is reciprocated between an inner position and an outer position in the radial direction of the motor cylinder 170 by a second eccentric wheel 64 with a stroke of twice the eccentricity ε in the second valve hole 55. , at its inner and outer positions, the second distribution valve 62 opens the outer oil passage 53 to the outside of the cylinder block B.

In the above configuration, when the input cylinder shaft 5 of the hydraulic pump P is rotated from the primary reduction gear 2 while the second eccentric wheel 64 is held at the clutch-on position n, the pump swash plate 10 causes the pump plungers 9, 9, . . . Exhalation and suction strokes are applied alternately.

The pump plunger 9 pumps hydraulic oil from the cylinder hole 8 to the outer oil passage 53 while passing through the discharge area, and pumps hydraulic oil from the inner oil passage 52 to the cylinder hole 8 while passing through the suction area S. Inhale.

The high pressure hydraulic oil sent to the outer oil passage 53 is supplied to the hydraulic motor M.
Hydraulic oil is supplied to the cylinder hole 18 of the motor plunger 19 in the expansion area Ex, while the hydraulic oil is discharged from the cylinder hole 18 to the inner oil passage 52 by the motor plunger 19 in the contraction area sh.

During this period, the pump cylinder 7 receives a reaction torque 7 from the pump swash plate 10 via the pump plunger 9 in the discharge stroke, and the motor cylinder 17 receives the reaction torque 7 from the pump plunger 1 in the fat expansion stroke.
The cylinder block B is rotated by the sum of the reaction torque received from the motor swash plate 2 through the motor swash plate 2 , and the rotational torque is transmitted from the output shaft 31 to the secondary reduction gear 3 .

In this case, the gear ratio of the output shaft 31 to the input cylinder shaft 5 is given by the following equation.

Capacity of Hydraulic Pump P Therefore, if the capacity of hydraulic motor M is changed to a value consisting of zero, the transmission ratio can be changed to a required value consisting of one. Moreover, since the capacity of the hydraulic motor M is determined by the stroke of the motor plunger 19, by tilting the motor swash plate 20 from the upright position to the inclined position, the gear ratio can be controlled steplessly at a value of 1. be able to.

By the way, while the hydraulic pump P is in operation, the angular contact ball bearing 11 is connected to the pump plungers 9, 9...
The thrust load received from the group is much larger on the discharge region side than on the suction region S side. Therefore, the contact angle α of the ball 133 increases on the side near the discharge area and decreases on the suction area S. As a result, when the pump swash plate 10 and the pump swash plate holder 12 rotate relative to each other, , D, there is a difference in the revolution angle of the ball 133, but this difference in revolution angle is absorbed by the play 136 in each pocket 135.

Therefore, the balls 133 of each group divided by the pockets 135 are connected to the retainer 134 and the balls 13 of other groups.
3. It can roll freely without being interfered with.

At that time, the balls 133 in the same pocket 135 may collide with each other, but since the number of balls 133 accommodated by one pocket 135 is extremely small, the impact force is relatively small, and the balls 133 collide with each other. It does not cause premature wear.

Furthermore, since the number of pockets 135 is smaller than the number of balls 133, each pocket 135 has a certain amount of play 136, but the amount of play 136 does not restrict the number of balls 133 that can be used, so the number of balls 1330 is smaller than that of the conventional It is possible to secure sufficient load capacity with almost no difference.

On the other hand, in the angular contact ball bearing 21 of the hydraulic motor M, the thrust load received from the motor plungers 19, 19... is larger on the expansion region Ex side than on the contraction region sh side. It can operate smoothly due to the same effect as the bearing 11.

During operation of the transmission T, the pump swash plate 10 receives thrust loads in opposite directions from the pump plungers 9, 9, etc., and the motor swash plate 20 receives thrust loads in opposite directions from the motor plungers 19, 19, . The thrust load that the swash plate 10 receives is supported by the output shaft 31 via the angular contact bearing 11, the pump swash plate holder 12, the thrust roller bearing 40, and the flange 37, and the thrust load that the motor swash plate 2o receives is supported by the angular contact bearing 21. , the motor swash plate holder 22 , the motor swash plate anchor 23 , the thrust roller bearing 47 , the support tube 45 , and the shaft 44 are supported by the output shaft 31 . However, the thrust load merely causes tensile stress on the output shaft 31 and does not act on the casing 4 supporting the shaft 31 at all.

In this case, the motor swash plate holder 22 supports the motor swash plate 20 on the front side via the thrust roller bearing 21, and is supported on the back side on the motor swash plate anchor 23, so that the motor plungers 19, 19... Even if a thrust load is applied through the motor swash plate 20, no deflection occurs. Moreover, the motor swash plate holder 22 and the motor swash plate anchor 23 have a spherical surface f1 centered at the intersection of the axis of the motor cylinder 17 and the trunnion axis 0□. rt are opposed to each other, the motor swash plate holder 22 exhibits an alignment function due to the interaction of these spherical surfaces. As a result, the motor swash plate holder 22 can smoothly rotate around the trunnion axis Ot, and the inclination angle of the motor swash plate 2° can be easily controlled. At this time, the engagement between the trunnion shaft 22a of the motor swash plate holder 22 and the recess 23a of the motor swash plate anchor 23 prevents the motor swash plate holder 22 from rotating around an axis other than the trunnion axis O2. Furthermore, the motor swash plate anchor 23 having the concave spherical surface f2 becomes thicker from the center toward the periphery and has high rigidity, so that it can sufficiently withstand a large load from the motor swash plate holder 22 and the thrust roller bearing 47. Can be done.

Furthermore, each spherical recess 20a on the motor swash plate 20.

Since the partition wall 20b between 20a is formed in a chevron shape, the effective engagement depth between the spherical recess 20a and the spherical end 19a of the motor plunger 19 can be increased without making the entire motor swash plate 20 thick. Therefore, even under high load, the motor plunger 19 can be set in the spherical recess 20a.
The motor swash plate 20 can be reliably rotated without slipping out.

Furthermore, in the hydraulic pump P and the hydraulic motor M, each swash plate 10.20 receives centering action from the front and back by the spherical ends 9a, 19a of the corresponding plunger 9.19 and the angular contact bearing 11.21. , the cylinder block B remains in its fixed position even in any inclined state.
It is possible to perform accurate synchronous rotation.

When the second eccentric wheel 64 is swung to the clutch-off position f during hydraulic pressure transmission from the hydraulic pump P to the hydraulic motor M, the high-pressure outer oil passage 53 is opened to the outside of the cylinder block B by the second distribution valve 62. Therefore, high-pressure hydraulic oil is no longer supplied to the hydraulic motor M, and power transmission between the hydraulic pump P and the hydraulic motor M is cut off. That is, a so-called clutch-off state is obtained.

1, 2, and 10, a speed change control device C for controlling the angle of the motor swash plate 20 is connected to the trunnion shaft 22a.

This speed change control device C includes an electric motor 80 capable of forward and reverse rotation such as a pulse motor, a DC morph, etc.
0, and a ball nut mechanism 82 that is connected to the reduction gear device 81. The pole nut mechanism 82 consists of a screw shaft 83 and a nut 85 that is screwed onto the screw shaft 83 via a circulation ball 84.The screw shaft 83 is connected to the output gear of the reduction gear device 81 and has both ends. Ball bearing 86°8
It is rotatably supported by the casing 4 via 6'. The nut 85 has a connecting arm 87 on one side, and this connecting arm 87 and a pair of connecting arms 8B and 88 that protrude from one side of the motor swash plate holder 22 and sandwich the connecting arm 87 are connected to the trunnion shaft 02. They are interconnected by parallel connecting pins 89. Such a connection prevents the nut 85 from rotating around the screw shaft 83.

When the screw shaft 83 is rotated in the normal direction by rotating the electric motor 80 in the normal direction, the nut 85 moves to the left in FIG. When the electric motor 80 is rotated in the opposite direction, the nut 85 moves to the right and the motor swash plate 20 can be tilted.

3 and 10, a rotary potentiometer 111 is attached to the casing 4 to detect the inclination angle of the motor swash plate 20 and send control signals to various control devices. This potentiometer 111 is equipped with a lever 113 at the tip of a rotating shaft 112, and this lever 113 is engaged with an engagement groove 114 formed in one trunnion shaft 22a of the motor swash plate holder 22. Therefore, when the motor swash plate holder 22 is rotated to tilt the motor swash plate 20, the rotating shaft 112 is rotated via the lever 113 accordingly, and the potentiometer 111 controls the motor swash plate 20 according to its angle. A signal is output.

2, 3, and 9, a central oil passage 90 is bored in the center of the output shaft 31, the lower end of which is closed by the bolt 49, and the other end is opened as an inlet. An oil filter 91 facing the cap 50
will be installed on the

The entrance of the central oil passage 90 is communicated with an oil reservoir 93 at the bottom of the casing 4 via an oil passage 92 formed in the casing 4.
A replenishment pump 95 driven by a gear 94 fixed to the pump swash plate holder 22 is interposed in the middle of the oil passage 92 . Therefore, while the engine E is rotating, the replenishing pump 95 continues to supply oil from the oil reservoir 93 to the central oil passage 90.

A valve cylinder 100 with both ends open is fitted in the center of the central oil passage 90, and the valve cylinder 100 is fixed to the output shaft 31 by passing through a fixing pin 101 that is press-fitted on its diameter line. The fixing pin 101 has a hollow part 102 that opens both ends to the inner oil passage 52, and this hollow part 102 is connected to the valve cylinder 10.
It has a plurality of through holes 103, 103, . . . that communicate with each other. Therefore, the center oil passage 90 and the inner oil passage 52 are communicated with each other via the valve cylinder 100 and the fixing pin 101.

Chamfered portions 104 , 104 are formed on the outer circumferential surface of the valve cylinder 100 to communicate the upstream and downstream sides of the central oil passage 90 .

In addition, inside the valve cylinder 100, there is a central oil passage 90 from the inner oil passage 52.
a pair of first check valves 105.10 to prevent backflow of oil to the
5 are arranged symmetrically across the fixing pin 101, and each check valve 105 is always urged in the valve closing direction by a valve spring 106.

Further, the output shaft 31 and the cylinder block B have a valve cylinder 1
A series of replenishment oil passages 107 are provided that connect the central oil passage 90 on the upstream side of 00 and the outer oil passage 53, and this replenishment oil passage 1
A second check valve 10B that prevents oil from flowing backward from the outer oil passage 53 to the central oil passage 90 is interposed in the middle of the oil passage 07, and this check valve 10B is always urged in the valve closing direction by a valve spring 109. Forced.

Furthermore, the output shaft 31 has a radial orifice hole 1 for supplying lubricating oil from a central oil passage 90 to each part of the transmission T.
10 are drilled in place.

During normal load operation in which the hydraulic motor M is hydraulically driven from the hydraulic pump P, the pressure in the inner oil passage 52 on the low pressure side increases to the pressure in the central oil passage 90 due to oil leakage from the hydraulic closed circuit between the two. When the oil pressure drops below this level, the first check valves 105 and 105 open, and hydraulic oil is replenished from the central oil passage 90 to the inner oil passage 52. On the other hand, at this time, the hydraulic oil in the outer oil passage 53 on the high pressure side is prevented from flowing into the central oil passage 90 by the second check valve 10B.

Furthermore, during reverse load operation, that is, during engine braking, the hydraulic motor M performs a pumping action, and the hydraulic pump P performs a motor action, thus changing the outer oil passage 53 to low pressure and the inner oil passage 52 to high pressure. Therefore, if the pressure in the outer oil passage 53 drops below the pressure in the central oil passage 90 due to oil leakage,
The second check valve 108 opens and the central oil passage 90 is opened to the outer oil passage 5.
Hydraulic oil is supplied to 3, and the center oil passage 90 is supplied from the inner oil passage 52.
The first check valves 105, 105 prevent the hydraulic oil from flowing out.

Furthermore, since the oil in the central oil passage 90 is supplied to each part of the transmission T while its flow rate is restricted by the orifice hole 110,
Due to this supply, the pressure in the central oil passage 90 does not drop excessively, and therefore, there is no problem in supplying hydraulic oil from the central oil passage 90 to the inner oil passage 52 and the outer oil passage 53.

The cylinder block B is also provided with a pressure regulating valve 120 that prevents an excessive rise in the oil pressure in the outer oil passage 53.

This pressure regulating valve 120 consists of a valve cylinder 121, a valve body 122, and a valve spring 123.

The valve cylinder 121 is press-fitted into the partition wall between the inner and outer oil passages 52 and 53 and the peripheral wall of the outer oil passage 53 so as to penetrate them in the radial direction. This valve cylinder 121 has a horizontal hole 124 that opens to the outer oil passage 53, a vertical valve hole 125 that communicates between this horizontal hole 124 and the outer oil passage 53, and a horizontal hole that has a slightly larger diameter than this valve hole 125. It has a guide hole 126 extending from 124 in the opposite direction to the valve hole 125, and a large diameter spring chamber 127 connected to the guide hole 126.

The valve body 122 faces the horizontal hole 124 and also faces the valve hole 125.
The valve part 122a has a valve part 122a that slides on the guide hole 126, a valve rod part 122b that slides on the guide hole 126, and a flange-shaped stopper part 122C that can come into contact with the step between the guide hole 126 and the spring chamber 127. is normally held in the abutting position with the stepped portion by a valve spring 123 housed in a spring chamber 127. The spring chamber 127 communicates with the inner oil passage 52 so as not to interfere with the operation of the valve body 122.

Therefore, the oil pressure of the outer oil passage 53 is applied to the step surface between the valve portion 122a and the valve rod portion 122b, and applies a valve opening force to the valve body 122, but the oil pressure of the outer oil passage 53 is below a specified value. In normal operating conditions, the force of the valve spring 123 that biases the valve body 122 in the valve closing direction is greater than the valve opening force, so the valve body 122 is in the closed state, that is, the valve hole 125 is closed. held in state. When the oil pressure in the outer oil passage 53 exceeds a specified value, the valve opening force increases more than the force of the valve spring 123, so the valve body 122 slides while compressing the valve spring 123 to open the valve, that is, the valve hole 125 and remove the excessive oil pressure in the outer oil passage 53 from the valve hole 1.
25 to the outside of the cylinder block B. Then, when the oil pressure in the outer oil passage 53 returns to the specified value, the valve spring 123
The force causes the valve body 122 to return to the closed state again. Therefore, even when the vehicle suddenly starts or accelerates, an excessive increase in the oil pressure in the outer oil passage 53 can be suppressed.

The cylinder block B further includes an inner oil passage 52 and a center oil passage 90 in order to prevent an excessive rise in the oil pressure in the inner oil passage 52.
A throttle hole 128 is provided that communicates between the two. therefore,
Even during sudden engine braking, the oil pressure in the inner oil passage 52 can be prevented from increasing excessively.

Referring again to FIG. 2, the flange 37 integrated with the output shaft 31
has a large number of teeth 117 carved on its outer periphery and serves as a pulse rotor, and a pickup coil 11 facing the outer periphery.
8 is screwed onto the casing 4. pink up coil 1
18 generates pulses in response to the rotation of the output shaft 31, which are converted into current or voltage and displayed as vehicle speed on a speedometer (not shown).

C2 Effects of the Invention As described above, according to the present invention, each pocket of the retainer is formed in an arc shape with a prescribed play in the circumferential direction to accommodate a plurality of balls, thereby reducing the number of balls used. It is possible to absorb the difference in the revolution angle of the balls with almost no reduction, and also to avoid severe collisions between the balls, and therefore it is possible to provide a ball bearing with sufficient load capacity and high durability.

[Brief explanation of the drawing]

The drawings show one embodiment of the present invention, and FIG. 1 is a plan view of a power unit for a motorcycle, FIG. 2 is an enlarged vertical sectional plan view of the main part of FIG. 1, and FIG. −■ line cross-sectional view,
4 is a sectional view taken along the line IV-TV in FIG. 3, FIG. 5 is a sectional view taken along the line V-V in FIG.
The figure is a sectional view similar to Fig. 5 shown in the clutch-off state, Fig. 7 is a front view of the second distribution valve, Fig. 8 is a sectional view taken along the line ■-■ in Fig. 7, and Fig. 9 is the same as Fig. 3. 10 is an enlarged view of the main parts of FIG. 3, FIG. 11 is a plan view of the motor swash plate, and FIGS. 12 and 13 are views of 14 is an exploded perspective view of the main parts of FIG. 2, FIG. 15 is an enlarged vertical sectional view of the angular contact ball bearing according to the present invention installed in a hydraulic pump, and FIG. 16 is the same. A plan view showing the relationship between the retainer and balls of the bearing, FIG. 17 is a vertical cross-sectional view of a conventional angular contact ball bearing, FIG. 18 is a plan view showing the relationship between the retainer and balls of the bearing, and FIG. 19 is the same bearing. 3 is a graph showing contact angle change characteristics of a ball when an unbalanced load is applied. 11.12...Ball bearing, 131,132.
...lace, 133...ball, 134...retainer, 135...pocket, 136...play patent applicant Honda Motor Co., Ltd. agent Patent attorney Takeoka Ochiai
1) Takashi Naka Figure 1 Figure 4 Figure 6 Figure 5 Figure 7 Group Figure 11 Figure 12 XII-i Figure 16 Figure 15 Figure 18 Figure 17

Claims (1)

[Claims] In a ball bearing in which a plurality of balls arranged in an annular arrangement and an annular retainer provided with pockets for accommodating these balls are interposed between a pair of opposing races, each pocket of the retainer is defined in the circumferential direction. A ball bearing characterized in that it is formed in an arc shape to accommodate a plurality of balls with play.