Note: Descriptions are shown in the official language in which they were submitted.
2~)07~94
BIDIRECTIONAL DIFFERENTIAL CLUTCH
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates to a bidirectional
differential clutch which enables to transmit or cutoff both
clockwise and counterclockwise rotation at the input side.
2. Description of the Prior Art
An over-running type clutch or a differential clutch which
enables to transmit driving force to front wheels automatically
at the instant of falling speed due to slip of rear wheels has
come to be employed on a part-time type four wheel driving car
(hereinafter also referred to as a 4WD car).
In this differential clutch, front wheel hubs are designed
to rotate faster than a drive shaft so that the rotation of -
the drive shaft may not be transmitted to front wheel hubs in
driving with two wheels. When rear wheels slip and the
rotation of the drive shaft increases, the drive shaft and the
front wheel hub come to engagement due to wedge like action
of rollers or balls inserted into the clearance of the drive
shaft and the front wheel hub, thus the rotation being
transmitted to the front wheel hub.
In order to produce this wedge-like action on the
differential clutch, the front surface of the drive shaft is
provided with a saw tooth like cam. As it operates only in
one way rotation, there was a problem that front wheels can
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not be driven in going backwards. Also in differential clutches
using sprags instead of rollers or balls, the operation of sprags
was limited to one direction, resulting in the same problem.
The present invention was made to solve the above-described
problem and it is an object to provide a bidirectional
differential clutch which enables to transmit or cutoff both
clockwise and counterclockwise rotation at the input side.
SUMMARY OF THE INVENTION
The bidirectional differential clutch comprises an input
gear having a first cylindrical surface, an output gear having
a second cylindrical surface disposed with a space to said first
cylindrical surface so as to be relatively rotatable, a plurality
of engaging members interposed in the space, a holding member
inserted into the space, the holding - her having a pocket
storing said engaging - her, the engaging member being for
operation from a neutral position in which both cylindrical
surfaces are not engaged with each other to a operational
position in which both cylindrical surfaces are engaged with
each other, a sub-gear producing differential velocity in
correspon~ence to the rotation of the input gear, and the holding
- ~-r being linked with said sub-gear to slide in a peripheral
direction by the differential velocity to operate the engaging
,- hPr to the operational position. The engaging members may
be rollers or sprags.
When the number of teeth of the sub-gear is greater than
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the number of teeth of the input gear, the sub-gear rotates
later than the input gear by the same rotation input, thus
producing differential velocity between both gears. Due to
this differential velocity, sprags, for example, are tilted
whichever the rotation is clockwise or counterclockwise to bring
about a state of engagement between the rotation shaft and the
output gear. Wherefore, the rotation of the input gear in the
clockwise or counterclockwise direction can be transmitted to
or cutoff from the output gear.
BRIEF DESCRIPTION OF THE DRAWINGS
The present invention will now be explained with reference
to the following drawings.
Fig.1 is a vertical section of the first embodiment
according to the invention.
Fig.2 is a transverse cross section taken along line A-A
of Fig.1.
~ Fig.3 and 4 illustrate operation.
; Fig.5 and 6 are enlarged views of the relevant parts.
Fig.7 is a vertical section of the second emho~i ~nt.
' Fig.8 is a vertical section of the third embodiment.
Fig.9 is a transverse cross section taken along line B-B
of Fig.8.
Fig.10 and 11 illustrate operation of the third --ho~; -nt.
Fig.12 and 13 are enlarged views of the relevant parts
of the third ~ hoA1 ~nC,
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Fig.14 and 15 are cross sectional views of the sprag alone
of the third embodiment.
Fig.16 is a vertical sectional view of the fourth
embodiment.
Fig.17 is a vertical sectional view of the fifth embodiment.
Fig.18 is a transverse cross section taken along line C-C
of Fig.17.
Fig.19 is an enlarged view of the relevant parts of Fig.18.
Fig.20 is a cross-section showing the operation of the
fifth - ho~i ~nt.
Fig.21 is an enlarged view of the relevant parts of the
sixth ~ hoAi ent.
Fig.2Z is a vertical sectional view of the seventh
embodiment.
DETAILED DESCRIPTION OF THE INVENTION
In Flg.1, 1 is a rotation shaft having various stepped
portions on the outer peripheral surface. 2 is an input gear
which is connected to one of the stepped portions of the rotation
shaft 1 through a spline 2a. 2b is a tooth formed on the outer
periphery of the input gear 2, which is engaged with a gear
of a drive shaft (not shown). 17 is an outer peripheral
cylindrical surface, which is formed on another stepped portion
of the outer periphery of the rotation shaft 1 in parallel to
the input gear 2. 4 is an output gear having an inner peripheral
cylindrical surface 18, which is disposed with clearance to
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26)07194
the outer periphery of the outer peripheral cylindrical surface
17. 4a is a tooth formed on the outer periphery of the output
gear 4, which is engaged with a gear of a driven shaft (not
shown).
As shown in an enlarged view of important parts of Fig.6,
a plurality of sprags 6 are disposed at fixed intervals in a
peripheral direction between the inner peripheral cylindrical
surface 18 of the output gear 4 and the outer peripheral
cylindrical surface 17 of the rotation shaft 1.
A circular surface 6a at the outer diameter side of the
sprag 6 and another circular surface 6b at the inner diameter
side are circular surfaces of a radius value r and designed
longer than a half of the interval d between the inner peripheral
cylindrical surface 18 of the output gear 4 and the outer
peripheral cylindrical surface 17 of the rotation shaft 1.
The length l in the direction of connecting the centers of the
radius values r of the circular surfaces 6a, 6b is somewhat
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shorter than the interval d. Therefore, in the neutral state
which the sprag 6 stands up between the opposing cylindrical
surfaces 17, 18, there is formed radial clearance between the
circular surfaces 6a, 6b of the sprag 6 and the cylindrical
surfaces 17, 18. When the sprag 6 falls down from the neutral
state in the peripheral direction of the cylindrical surfaces
17, 18, the circular surface 6a at the outer diameter side and
the circular surface 6b at the inner diameter side are engaged
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with the opposing cylindrical surfaces 17, 18.
End portions 6c, 6f at the inner diameter side of the sprag
6 are caught in a pocket 1Oa of the inside holding member 10
which is fixed on the outer peripheral cylindrical surface 17
of the rotation shaft 1 via pressing in or other methods. End
portions 6d, 6e at the outer diameter side are caught in a pocket
9a of the outside holding member 9 which is inserted between
the inside holding member 10 and the output gear 4 slidably
with reference to the rotation shaft 1. The length A between
the sides opposing in the peripheral direction of the pockets
9a of the outside holding members 9 is larger than the length
B between the sides opposing in the peripheral direction of
the pockets 1Oa of the inside holding - hers 1 O. In a recess
9b which is formed in the central portion of the opposing sides
in the peripheral direction of the pocket 9a of the outside
holding - her 9, a pair of elastic members 7 press the end
portions 6d, 6e at the outside diameter side of the sprag 6
from both sides to hold neutral the sprag 6 as shown in Fig.
6. The elastic 1- her can be made of leaf springs, coil springs
and others. In this embo~i ~t, a metal leaf spring as an
elastic - her 7 is fixed from the outer portion 9c of the
outside holding - her 9 as shown in Fig.5. However, it may
be fixed from the inner portion 9d of the outside holding member
9.
Back to Fig.1, 8 is a sub-gear which is inserted between
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26)~)7~94
the input gear 2 and the output gear 4. 8a is a tooth provided
on the outer periphery of the sub-gear 8 which engages with
a gear on the drive shaft ~not shown) as in the case of the
input gear 2. At the inner peripheral side of the sub-gear
8, the outside holding member 9 is inserted slidably around
the rotation shaft 1. The sub-gear 8 is pressed in contact
via a belleville spring 19 between a retaining ring 20 fixed
to the outside holding member 9 and the side surface of the
stepped portion of the outside holding - h~r 9. The inner
peripheral side of the outside holding - her 9 is partially
cut out to make a cutout 1 1. Opposing to the cutout 1 1, a
stopper 1a is protruded on the rotation shaft 1. 12 and 14
are bearings supporting the rotation shaft 1. 13 and 15 are
bearings supporting the output gear 4.
The operation of the bidirectional differential clutch
constituted as described in the above will now be explained.
In using this bidirectional differential clutch for the
power transmission of the part-time type 4WD car, for example,
the rotation of the drive shaft is transmitted to the input
gear 2 and the sub-gear 8 engaging therewith. However, the
rotation of the sub-gear 8 is later than the rotation of the
input gear 2 in spite of the rotation of the same drive shaft
because the teeth 2b of the input gear 2 are 53, for example,
against the teeth 8a of the sub-gear 8 are 54, for example.
Accordingly, as shown in Fig.4, the outside holding member 9
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being pressed in contact by the sub-gear 8 rotates relatively
in the clockwise direction with differential velocity against
the rotation of the rotation shaft 1 until the left side surface
of the cutout 11 of the outside holding member 9 abuts the
stopper 1a. The sprag 6 stored in the pocket 9a of outside
holding - ~er 9 falls down in the rotational direction of the
outside holding ~ her 9. Therefore, as shown in Fig.4, the
circular surface at the outer diameter side 6a of the sprag
6 and the circular surface at the inner diameter side 6b engage
with opposing cylindrical surfaces 17, 18 enabling the clutch
to operate in the direction shown by an arrow mark.
When the 4WD car is driving with two wheels, the rotation
of the output gear 4 is set to rotate faster than the input
gear 2 or the rotation of the rotation shaft 1. Accordingly,
the sprag 6 is effected by the frictional force to stand up
for idle running without bite in the cylindrical surfaces 17,
18~. On the other hand, when rear wheels slip, the rotation
of the drive shaft increases, the rotation of the input gear
2 or the rotation shaft 1 becomes faster than the rotation of
the output gear 4, and the clutch operates in the arrow-marked
dlrection, thus transmitting the rotational force of the rotation
shaft 1 to the output gear 4. After the stopper la abuts the
wall surface of the cutout 11, the outside holding ~ ~ r 9
runs idly, and there is no destruction on the sub-gear 8.
As described in the above, the clutch operational principle
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of the sprag 6 based on the differential velocity of the sub-
gear 8 has no relation with the direction of the rotation of
the output gear 2. Accordingly, the bidirectional differential
clutch is effective in going backwards of the part-time type
4 wheel drive car.
Fig.7 shows a second embodiment of this invention which
the bearings 13, 15 supporting the output gear 4 are replaced
by bearings 13'.
The bidirectional differential clutch of this invention
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has constitution that a cylindrical surface at an input gear
side and a cylindrical surface at an output gear side are
disposed with a space so that they can rotate relatively and
a plurality of sprags are interposed in the space, wherein the
sprags are stored in a pocket of a first holding member fixed
on the cylindrical surface at the input gear side and a pocket
of a second holding 1- h~r disposed adjacent to the cylindrical
surface at the output gear side and slidably in a peripheral
:
direction, the sprags are disposed so as to be tiltable from
a neutral position which is not engaged with the cylindrical
' surface at the input gear side nor the cylindrical surface at
~ the output gear side to a clutch operational position where
engages with both cylindrical surfaces, the second holding member
is linked with a sub-gear producing differential velocity in
correspo~dence to the rotation of the input gear, thus the second
holding member sliding in a peripheral direction by the
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differential velocity to tilt the sprag to the clutch operational
position .
Accordingly, the rotation of the input gear can be
transmitted to or cut off from the output gear wherever it is
clockwise or counterclockwise.
In Fig.8, 21 is a rotation shaft having various stepped
portions on the outer peripheral surface. 24 is an output gear
which is connected to one of the stepped portions of the rotation
shaft 21 through a spline 24a. 24b is a tooth formed on the
outer periphery of the output gear 24, which is engaged with
a gear of a driven shaft (not shown). 37 is an outer peripheral
cylindrical surface, which is formed on another stepped portion
of the outer periphery of the rotation shaft 21. 22 is an input
gear having an inner peripheral cylindrical surface 38, which
is disposed with clearance to the outer periphery of the outer
peripheral cylindrical surface 37. 22a is a tooth formed on
the outer periphery of the input gear 22, which is engaged with
a gear of a driving shaft (not shown).
As shown in an enlarged view of important parts of Fig.13,
a plurality of sprags 26 are disposed at fixed intervals in
:;
; a peripheral direction between the inner peripheral cylindrical
surface 38 of the input gear 22 and the outer peripheral
cylindrical surface 37 of the rotation shaft 21.
A circular surface 26a at the outer diameter side of the
sprag 26 and another circular surface 26b at the inner diameter
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2007194
side are circular surfaces of each radius value r1, r2 as shown
in Fig 14 The radius values of r2 may be r3 and r4
unsymmetrically in the right and left sides. Each value of
r1, r2, r3, and r4 is designed longer than a half of the interval
d between the inner peripheral cylindrical surface 38 of the
input gear 22 and the outer peripheral cylindrical surface 37
of the rotation shaft 21. The minimum height l in the direction
of opposing the circular surfaces 26a, 26b to each other is
sc qwl.at shorter than the interval d. Therefore, in the neutral
state which the sprag 26 stands up between the opposing
cylLndrical surfaces 37, 38, there is formed radial clearance
between the circular surfaces 26a, 26b of the sprag 26 and the
cylindrical surfaces 37, 38. When the sprag 26 falls down from
the neutral state in the peripheral direction of the cylindrical
sur~faces 37, 38, the circular surface 26a at the outer diameter
side and the circular surface 26b at the inner diameter side
are engaged with the opposing cylindrical surfaces 37, 38.
End portions 26d, 26e at the outer diameter side of the
sprag 26 are caught in a pocket 30a of the outside holding 1-- her
: . .
30 which is fixed on the inner peripheral cylindrical surface
38 of the input gear 22 via pressing in or other methods. End
portions 26c, 26f at the inner diameter side are caught in a
pocket 29a of the inside holding - her 29 which is inserted
between the outside holding - her 30 and the rotation shaft
21 slidably with reference to the rotation shaft 21. In this
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~107194
embodiment, the outside holding member 30 is secured to the
input gear 22 with a pin 36. The length A between the sides
opposing in the peripheral direction of the pockets 29a of the
inside holding members 29 is larger than the length B between
the sides opposing in the peripheral direction of the pockets
30a of the outside holding - hers 30. In a recess 29b which
is formed in the central portion of the opposing sides in the
peripheral direction of the pocket 29a of the inside holding
member 29, a pair of elastic - hers 27 press the end portions
26c, 26f at the inside diameter side of the sprag 26 from both
sides to hold neutral the sprag 26 as shown in Fig. 13. The
elastic 1- her 27 can be made of leaf springs, coil springs
and others. In this embodiment, a metal leaf spring as an
elastic 1- her 27 is fixed on the inner portion 29c of the inside
holding ~ her 29 as shown in Fig.12. However, it may be fixed
on the outer portion 29d of the inside holding - her 29.
Back to Fig.8, 28 is a sub-gear which is inserted adjoining-
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' the input gear 22. 28a is a tooth provided on the outer
periphery of the sub-gear 28 which engages with a gear on the
drive shaft (not shown) as in the case of the input gear 22.
r~u hers of the teeth of the sub-gear 28 are,set to be greater
than those of the input gear 22. At the inner peripheral side
of the sub-gear 28, the inside holding 1- her 29 is inserted
slidably around the rotation shaft 21. The sub-gear 28 is
pressed in contact via a belleville spring 39 between a retaining
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26)07194
ring 40 fixed to the inside holding member 29 and the side
surface of the stepped portion of the inside holding member
29. While a stopper 29e is protruded on the inside holding
member 29, a rectangular hole 31 is provided with a clearance
to the stopper 29e on the outside holding member 30 opposing
the stopper 29e.
32 and 34 are bearings supporting the rotation shaft 21.
33 and 35 are bearings supporting the input gear 22 and the
inside holding member 29 respectively.
The operation of the third embodiment constituted as
described in the above will now be explained.
In using this bidirectional differential clutch for the
power transmission of the part-time type 4WD car, for example,
the rotation of the drive shaft is transmitted to the input
gear 22 and the sub-gear 28 engaging therewith. However, the
rotation of the sub-gear 28 is later than the rotation of the
input gear 22 in spite of the rotation of the same drive shaft
because the numbers of teeth 28a of the sub-gear 28 are set
to be greater than the numbers of teeth 22a of the input gear
22 in the same -nner of the above-mentioned embodiments.
Accordingly, as shown in Fig.11, the inside holding member 29
being pressed in contact by the sub-gear 28 rotates relatively
in the counterclockwise direction with differential velocity
against the rotation of the input gear 22 until the stopper
29e of the inside holding - h~r 29 abuts the left side surface
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of the rectan~ular hole 31. The sprag 26 stored in the pocket29a of inside holding member 29 falls down in the
counter-rotational direction of the inside holding - -r 29.
Therefore, as shown in Fig.ll, the circular surface at the outer
diameter side 26a of the sprag 26 and the circular surface at
the inner diameter side 26b engage with opposing cylindrical
surfaces 37, 38 enabling the clutch to operate in the direction
shown by an arrow mark.
When the 4WD car is driving with two wheels, the rotation
of the output gear 24 or the rotation shaft 21 is set to rotate
faster than the input gear 22. Accordingly, the sprag 26 is
-
effected by the frictional force to stand up for idle running
without bite in the cylindrical surfaces 37, 38. On the other
hand, when rear wheels slip, the rotation of the drive shaft
increases, the rotation of the input gear 22 becomes faster
than the rotation of the output gear 24 or the rotation shaft
2~1, and the clutch operates in the arrow-marked direction, thus
transmitting the rotational force of the input gear 22 to the
output gear 24. After the stopper 29e abuts the wall surface
of the rectangular hole 31, the inside holding - '?r 29 runs
idly with respect to the sub-gear 28.
As described in the above, the clutch operational principle
of the sprag 26 based on the differential velocity of the sub-
gear 28 has no relation with the direction of the rotation of
the input gear 22. Accordingly, the bidirectional differential
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2~U7194
clutch of this embodiment is effective in going backwards of
the part-time type 4 wheel drive car.
Furthermore, the sprag 26 is effected by the centrifugal
force proportional to the rotational speed of the outside holding
- h~r 30 to contact to the inner peripheral cylindrical surface
38 of the input gear 22. Accordingly, when the rotational speed
of the input gear 22 comes over the setting speed, the total
moment of the centrifugal force acting the sprag 26 and the
pressing force of the spring 27 operates the sprag 26 to return
to the neutral position. Thus the embodi ~nt has an advantage
that the sprag 26 is free from abrasion when the input gear
22 and the rotation shaft 21 rotate idly at the high differential
velocity in the disoperational condition of the clutch.
Fig.16 shows the fourth embodi nt of this invention in
which the bearings 33 supporting the input gear 22 are replaced
by bearings 33', 41. In case of this embodiment, since the
inner and outer peripheral cylindrical surfaces 38, 37 are
suppG~Led at both sides of the sprag 26 through ball bearings
33', 41 respectively by the rotation shaft 21, the concentricity
of the surfaces is easy to obtain, and the locking effect of
which with the sprag 26 bec- -s more reliable.
In Fig.17, 51 ls a rotation shaft having various stepped
portions on the outer peripheral surface. 52 is an input gear
which is connected to one of the stepped portions of the rotation
shaft 51 through a spline 52a. 52b is a tooth formed on the
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200~19~
outer periphery of the input gear 52, which is engaged with
a gear of a drive shaft (not shown). 53 is a polygonal surface
cam, which is formed on another stepped portion of the outer
periphery of the rotation shaft 51 in parallel to the input
gear 52. 54 is an output gear, which is disposed with clearance
55 to the outer periphery of the polygonal surface came. 54a
is a tooth formed on the outer periphery of the output gear
54, which is engaged with a gear of a driven shaft (not shown).
As shown in an enlarged view of important parts of Fig.19,
a pair of rollers 56, 56' are disposed on a pair of surfaces
65, 66, and 65', 66' of a wedge-like sectional gap 55
(hereinafter referred to as a wedge-like surface) in the
clockwise and counterclockwise direction formed between the
inner peripheral cylindrical surface 66 of the output gear 54
and the polygonal cam surface 65 of the rotation shaft 51.
Each pair of the rollers 56, 56' is stored in the pocket 59a
of the holding ~ ~-r 59, and a spring 57 is inserted between
the rollers to press the rollers 56, 56' respectively toward
the walls opposed in parallel along the shaft direction of the
pocket 59a. The rollers 56, 56' in the neutral condition, as
shown in Fig.19, are not in contact with either wedge-like
surfaces 66, 66' in the clockwise or counterclockwise direction.
58 is a sub-gear which is inserted between the input gear
52 and the output gear 54. 58a is a tooth provided on the outer
periphery of the sub-gear 58 which engages with a gear on the
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2~07194
drive shaft (not shown) as in the case of the input gear 52.
At the inner peripheral side of the sub-gear 58, the holding
member 59 is inserted slidably around the rotation shaft 51.
The sub-gear 58 and the holding member 59 are pressed in contact
via a belleville spring 60 between the end surface of the stepped
portion of the rotation shaft 51 and the side surface of the
input gear 52. The inner peripheral side of the holding member
59 is partially cut out to make a cutout 61. Opposing to the
cutout 61, a stopper 51a is protruded on the rotation shaft
51. 62 through 64 are bearings supporting the rotation shaft
51.
The operation of the fifth embodiment constituted as
described in the above will now be explained.
In using this bidirectional differential clutch for the
power transmission of the part-time type 4WD car, for example,
the rotation of the drive shaft is transmitted to the input
gear 52 and the sub-gear 58 engaging therewith. However, the
rotation of the sub-gear 58 is later than the rotation of the
input gear 52 in spite of the rotation of the same drive shaft
because the numbers of teeth 58a of the sub-gear 58 are set
to be greater than those of the teeth 52a of the input gear
52 in the same manner of the above-mentioned embodiment.
Accordingly, as shown in Fig.20, the holding - her 59 pressed
in contact by the sub-gear 58 rotates relatively in the clockwise
direction, for example, with differential velocity against the
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2~)07~94
rotation of the rotation shaft 51 rotating counterclockwise
until the left side surface of the cutout 61 of the holding
member 59 abuts the stopper 51a of the rotation shaft 51. Then
the right side roller 56' as shown in a pair of the rollers
56, 56' stored in the pocket 59a of the holding - her 59 is
pressed to the wedge-like surfaces 65', 66' by the spring force
of the spring 57.
When the 4WD car is driving with two wheels, the rotation
of the output gear 54 is set to rotate faster than the input
gear 52. Accordingly, the roller 56' is effected to rotate
idle without bite in the wedge-like surfaces 65', 66'. It is
natural for the roller 56 not to bite the wedge-like surfaces
65, 66 because the roller 56 is not in contact with the surfaces.
On the other hand, when rear wheels slip, the rotation
of the drive shaft increases, the rotation of the polygonal
cam 53 be~ -s faster than that of the output gear 54, and the
roller 56' pressed to the wedge-like surfaces 65', 66' are
effected to bite them, wherefore the rotational force of the
rotation shaft 51 is transmitted to the output gear 54. After
the stopper 51a abuts the wall surface of the cutout 61, the
holding member S9 runs idly as regards the sub-gear 58, and
there is no destruction on the sub-gear 58.
As described in the above, the clutch operational principle
of the rollers 56, 56' based on the differential velocity of
the sub-gear 58 has no relation with the direction of the
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2007194
rotation of the input gear 52. Accordingly, the bidirectional
differential clutch of the fifth embodiment is effective in
going backwards of the part-time type 4 wheel drive car.
Fig.21 shows the sixth embodiment of this invention in
which the rollers 56, 56' in the neutral condition are in contact
with the wedge-like surface 65, 66, 65', 66' as a different
point comparing to the fifth embodiment, and the other structure
and operation are the same as the fifth embodiment.
Fig.22 shows the seventh embodiment of this invention in
which the structure for pressing of the holding - her 59 and
the sub-gear 58 is only different from that of the fifth
embodiment. That is, the sub-gear 58 is pressed in contact
via the belleville spring 60 between the retaining ring 67
secured to the holding member S9 and the side surface of the
stepped portion of the holding - ber 59.
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