SPECIFICATION
FLUID-TYPE RETARDING DEVICE
Technical Field
[OOO 1 ]
The present invention relates to a fluid-type retarding device mounted as an
auxiliary brake in means of transportation including vehicles such as trucks and
buses.
The present application claims priority based on Japanese Patent
Application No. 2012-179320 filed in Japan on August 13, 2012, the content of
which is incorporated herein by reference.
Background Art
[0002]
In general, auxiliary brakes for use in vehicles include a fluid-type retarding
device and an eddy-current retarding device.
As disclosed, for example, in Patent Documents 1 and 2, the fluid-type
retarding device includes paired impellers as used in a fluid coupling, which are
disposed so as to face each other within a working container connected to the rear
end of a transmission.
[0003]
The paired impellers disclosed in Patent Documents 1 and 2 each include
radially extending vanes, one of which is a fixed impeller fixed to the working
container and serving as a stator, and the other one of which is a rotating impeller
serving as a rotor and fixed directly with the output shaft (rotating shaft) of the
transmission or fixed through a speed-increasing gear mechanism. The fixed
impeller and the rotating impeller form a torus-shaped working chamber.
[0004]
In the configuration described above, at the time of braking, the working
chamber is supplied and filled with working fluid (oil, water, or mixture thereof)
through oil-hydraulic pressure or air pressure. Then, the rotating impeller is
rotating, while the fixed impeller is at rest. Thus, a difference in relative rotational
speed takes place between these impellers, and the working fluid circulates between
the rotating impeller and the fixed impeller within the working chamber, thereby
causing circulatory flow of the working fluid. At this time, the working fluid
functions as a resistance that prevents the rotating impeller from rotating. This
leads to a generation of braking force acting on the rotating impeller, whereby it is
possible to reduce the speed of rotation of the rotating shaft through the rotating
impeller.
[OOOS]
At this time, kinetic energy of the rotating shaft is converted into thermal
energy in association with the generation of braking force, whereby temperatures of
the working fluid increase to be a high temperature. Thus, it is necessary for the
fluid-type retarding device disclosed in Patent Document 1 to have an external
cooling system that discharges the working fluid, which has high temperatures, into
the outside of the working container, thereby cooling it with a heat exchanger.
[0006]
In the case of this retarding device, although high braking force can be
stably generated for a long period of time, a device for supplying and discharging the
working fluid as well as the heat exchanger are required in addition to the paired
impellers that directly contribute to the generation of braking force, so that the
device configuration is complicated, and the weight of the device itself increases.
Furthermore, even if it is possible to use the cooling water system that the vehicle
originally has, significant modifications are necessary for the vehicle. Thus, this
retarding device is not suitable for small to mid-sized vehicles, which have relatively
reduced vehicle weight and for which compact and simple assembly is desired.
[OOO7]
On the other hand, a fluid-type retarding device disclosed in Patent
Document 2 employs an internal cooling system in which a ring-shaped heat
exchanger is provided radially outside of the working chamber, and a fan driven by
electricity or the pressure of the working fluid is attached to a rotating shaft. With
this internal cooling system, the working fluid, which has high temperatures, is
guided to the ring-shaped heat exchanger, and the working fluid is air cooled by air
blow from the fan. In the case of this retarding device, the external heat exchanger
is not necessary, and pipes for connecting with this external heat exchanger can be
omitted. Furthermore, this retarding device is separated from the cooling water
system of the vehicle, thereby exhibiting excellent assembly properties.
[OOOS]
However. as with Patent Document I , with the fluid-type retarding device
disclosed in Patent Document 2, it is necessary to discharge the working fluid from
the working chamber during non-braking periods, and supply the working fluid to
the working chamber at the time of braking. Thus, it is essential to provide a
special mechanism such as a pneumatic system, a hydraulic pump, and a shutoff
valve to supply and discharge the working fluid to and from the working chamber,
and fi~rthermorea, reservoir container for storing the working fluid is essential.
This is a large obstacle to use in small to mid-sized vehicles for which further
reductions in the number of parts, weight, and size are desired. Furthermore, it is
necessary to supply or discharge the working fluid to or from the working chamber
at the time of switching from braking to non-braking and vice versa, and hence, it
takes certain time from the non-braking state to obtain a desired braking force or
from the braking state to fully become the non-braking state, which inconveniently
results in a delay in response.
100091
On the other hand, the eddy-current retarding device includes a brake
member connected to a rotating shaft, and causes eddy current on a surface of the
brake member facing magnets due to an effect of a magnetic field from permanent
magnets or electromagnet at the time of braking. With the eddy current, there
occurs braking force in a direction opposite to the rotational direction of the brake
member rotating integrally with the rotating shaft, thereby reducing the speed of
rotation of the rotating shaft (see, for example, Patent Documents 3 to 6).
[OO lo]
In the case of the eddy-current retarding device, with the eddy current
generated on the brake member at the time of braking, the kinetic energy of the
rotating shaft is converted into thermal energy. With this thermal energy, the brake
member is heated, and the heat generated is radiated through fins provided to the
brake member, which rotates at high speed.
[ O O l l ]
For these reasons, unlike the fluid-type retarding device, it is not necessary
to discharge the working fluid from the working chamber to cool it with the heat
exchanger, and the device configuration is simple. In particular, in the case of an
eddy-current retarding device employing strong permanent magnets, the permanent
magnets have significantly reduced size and reduced weight as compared with the
electromagnet that generates the same magnetic force, and hence, it is possible to
reduce the weight and the size. Thus, this eddy-current retarding device is
promising since it can be applied not only to large-sized vehicles but also to small to
mid-sized vehicles.
Related Art Documents
Patent Document
100121
Patent Document 1 : Japanese Unexarnined Patent Application, First
Publication No. 2002-87222
Patent Document 2: PCT International Publication No. W02006/027056
Patent Document 3 : Japanese Unexamined Patent Application, First
Publication No. HI-234043
Patent Document 4: Japanese Unexamined Patent Application, First
Publication No. H1-298948
Patent Document 5: Japanese Unexamined Patent Application, First
Publication No. 2002-5 1533
Patent Document 6: Japanese Unexamined Patent Application, First
Publication No. 20 11 -97696
Disclosure of the Invention
Problems to be Solved by the Invention
LO0 1 31
However, the permanent magnets having strong magnetic force contain a
large amount of rare earth metals such as neodymium, and hence, are extremely
expensive. Furthermore, prices thereof largely change due to effects of the balance
of supply and demand, and hence, the eddy-current retarding device employing the
permanent magnets has a problem in which costs thereof are not stable due to
dependence on specifications of the permanent magnets.
[00 141
Furthermore, in the case of conventional eddy-current retarding devices, it is
not necessary to discharge the working fluid from the working chamber to cool it
with the heat exchanger. However, a disc brake provided as a friction brake and a
brake member that causes braking force to occur with eddy current are disposed in
series in order to make them coaxial with the rotating shaft. Thus, it is difficult to
reduce the longitudinal size of the rotating shaft along the axial direction.
[OO 151
The present invention has been made in view of the situations described
above, and an object of the present invention is to provide a fluid-type retarding
device that has a simplified device configuration and has a reduced size along an
axial direction of a rotating shaft to be connected thereto, thereby achieving reduced
weight and reduced size.
Means for Solving the Problem
[00 161
Each aspect of the present invention is provided as follows:
(1) An aspect of the present invention provides a fluid-type retarding device
including: a rotating disk provided to a rotating shaft; a rotating housing that
includes paired disk portions and a cylinder portion connecting outer circumferential
portions of the disk portions so as to surround the rotating disk, and is rotatably
supported with the rotating shaft; and a friction brake that presses a friction member
against the rotating housing at a time of braking to bring the rotating housing to a
stop, in which, on at least one surface of the rotating disk, a disk vane extending
from an inner circumference of the surface toward an outer peripheral side is formed,
on an inner surface of each of the paired disk portions corresponding to the disk vane,
a housing vane extending from an inner circumference to an outer periphery is
formed, and working fluid is accommodated within the rotating housing.
100 171
(2) In the fluid-type retarding device according to (1) described above, the disk
vane may be formed on both sides of the rotating disk, and a through-hole may be
provided on an inner circumference portion of the rotating disk.
roo 181
(3) In the fluid-type retarding device according to (2) described above, the disk
vane may be formed 011 both sides of the rotating disk; and an outer peripheral side
of the disk vane formed on one surface of the rotating disk may be formed so as to
extend toward the rear in a rotational direction of the rotating disk, and an outer
peripheral side of the disk vane formed on the other surface may be formed so as to
extend toward the front in the rotational direction of the rotating disk.
[00 191
(4) In the fluid-type retarding device according to any one of (1) to (3)
described above, the rotating shaft supporting the rotating housing may have a
tubular body having a space accommodating the working fluid therein, and include a
communicating hole that allows an internal space of the rotating housing and an
internal space of the rotating shaft to communicate with each other.
[0020 J
(5) The fluid-type retarding device according to any one of (1) to (4) described
above may further include an impeller provided to the rotating shaft so as to be
proximate to an external surface of each of the paired disk portions.
[002 11
(6) In the fluid-type retarding device according to any one of (1) to (5)
described above, the friction brake may include: a brake caliper that is fixed to a
non-rotating portion of a vehicle provided with the rotating shaft and includes paired
brake pads that each serve as the friction member and squeeze the paired disk
portions; and an actuator that drives the brake caliper and moves the paired brake
pads toward the disk portions.
100221
(7) The fluid-type retarding device according to (6) described above may
further include: a temperature sensor that is brought into contact with an external
surface of each of the disk portions in association with movement of the brake pads
toward the disk portions, and detects a temperature of each of the disk portions; and
an actuator controlling unit that stops actuating the actuator in a case where the
temperature of each of the disk portions detected by the temperature sensor exceeds
a predetermined temperature.
[0023]
(8) The fluid-type retarding device according to (6) or (7) described above may
further include a cooling member that is brought into contact with an external
surface of each of the disk portions in association with movement of the brake pads
toward the disk portions.
[0024]
(9) In the fluid-type retarding device according to any one of (1) to (8)
described above, either one of a plurality of permanent magnets and an eddy-current
generating member may be formed on at least any one surface of both surfaces and
an outer peripheral surface of the rotating disk; an eddy-current generating member
may be formed on a surface selected from among inner surfaces of the disk portions
and an inner peripheral surface of the cylinder portion, each of which constitutes the
rotating housing, this selected surface corresponding to the surface of the rotating
disk having the plural permanent magnets formed thereon; plural permanent magnets
may be formed on a surface corresponding to the surface of the rotating disk having
the eddy-current generating member formed thereon; and the plural permanent
magnets may be arranged in a manner such that opposing magnetic poles are
alternately arranged in a circumferential direction of the rotating disk.
Effects of the Invention
100251
According to the fluid-type retarding device of the present invention, it is
possible to achieve miniaturization by reducing the size in the axial direction of the
device.
Furthermore, in the case where the internal space of the rotating housing and
the internal space of the rotating shaft are communicated with each other, the
external heat exchanger for cooling the working fluid having high temperatures at
the time of braking is not necessary, and a mechanism for supplying or discharging
the working fluid to or from the worklng chamber or a reservoir container for storing
the working fluid is not necessary. Thus, the device configuration can be simplified,
whereby it is possible to further achieve reduced weight and reduced size.
Brief Description of the Drawings
[0026]
FIG. 1A is a schematic view illustrating the entire configuration of a
fluid-type retarding device according to a first embodiment of the present invention,
and is a side view in which part of the device is sectionally illustrated.
FIG. 1B is a diagram illustrating the same fluid-type retarding device, and is
a diagram illustrating a cross section along IB-IB in FIG. 1A.
FIG. 1C is a diagram illustrating the same fluid-type retarding device. and is
a diagram illustrating a cross section along IC-IC in FIG. 1A.
FIG. 1D is a schematic view illustrating a schematic configuration of disk
vanes and housing vanes of the same fluid-type retarding device, and is an expanded
view illustrating disk vanes and housing vanes when viewed from the outer
peripheral side.
FIG. 1E is a schematic view illustrating a schematic configuration of disk
vanes and housing vanes according to a modification example of the same fluid-type
retarding device, and is an expanded view illustrating disk vanes and housing vanes
when viewed from the outer peripheral side.
FIG. 2 is a schematic view illustrating the entire configuration of a
fluid-type retarding device according to a second embodiment of the present
invention, and is a side view in which part of the device is sectionally illustrated.
FIG. 3A is a schematic view illustrating the entire configuration of a
fluid-type retarding device according to a third embodiment of the present invention,
and is a side view in which part of the device is sectionally illustrated.
FIG. 3B is a diagram illustrating the same fluid-type retarding device, and is
a diagram illustrating a cross section along IIIB-IIIB in FIG. 3A.
FIG. 3C is a diagram illustrating the same fluid-type retarding device, and is
a diagram illustrating a cross section along IIIC-IIIG in FIG. 3A.
FIG. 4A is a schematic view illustrating the entire configuration of a
fluid-type retarding device according to a fourth embodiment of the present
invention, and is a side view in which part of the device is sectionally illustrated.
FIG. 4B is a diagram illustrating the same fluid-type retarding device, and is
a diagram illustrating a cross section along IVB-IVB in FIG. 4A.
FIG. 5 is a schematic view illustrating the entire configuration of a
fluid-type retarding device according to a fifth embodiment of the present invention.
FIG. 6 is a schematic view illustrating the entire configuration of a
fluid-type retarding device according to a sixth embodiment of the present invention.
FIG. 7A is a schematic view illustrating the entire configuration of a
fluid-type retarding device according to a seventh embodiment of the present
invention.
FIG. 7B is a diagram illustrating the same fluid-type retarding device, and is
a diagram illustrating a cross section along VIIB-VIIB in FIG. 7A.
Embodiments of the Invention
lo0271
The present inventors carried out thorough investigations on the assumption
that the fluid-type retarding device is employed. As a result, they found that, in
order to achieve the object described above, it is effective to employ a friction brake
in which:
a disk is connected to a rotating shaft; a housing including paired disk portions and a
cylinder portion is rotatably supported with the rotating shaft in a manner that
surrounds the entire rotating disk; working fluid is contained in the rotating housing:
and a friction member is pressed directly to this rotating housing at the time of
braking to bring the rotating housing to a stop, and completed the present invention.
Hereinbelow, each embodiment of a fluid-type retarding device according to
the present invention will be described in detail.

Below, a fluid-type retarding device according to a first embodiment of the
present invention will be described with reference to FIG. 1A to FIG. 1E.
FIG. 1A is a schematic view illustrating the entire configuration of the
fluid-type retarding device according to the first embodiment of the present
invention. FIG. 1B is a diagram illustrating a cross section along IB-IB in FIG. IA.
FIG. 1C is a diagram illustrating a cross section along IC-IC in FIG. 1A. FIG. ID is
a schematic view illustrating a schematic configuration of disk vanes and housing
vanes in the fluid-type retarding device according to the first embodiment, and is an
expanded view illustrating disk vanes and housing vanes when viewed from the
outer peripheral side. Furthermore, FIG. 1E is a schematic view illustrating a
schematic configuration of disk vanes and housing vanes according to a modification
example of the fluid-type retarding device according to the first embodiment, and is
an expanded view illustrating disk vanes and housing vanes when viewed from the
outer peripheral side.
[00281
As illustrated in FIG. 1A to FIG. ID, the retarding device according to the
first embodiment includes a rotating disk 3 and a rotating housing that surrounds the
entire rotating disk 3.
In the first embodiment, the rotating disk 3 is configured so as to rotate
integrally with a rotating shaft 11 such as a propeller shaft. More specifically, a
tubular connecting shaft 12 is coaxially connected to the rotating shaft 11, for
example, with a bolt, and the rotating disk 3 is connected to the connecting shaft 12
through a sleeve 13 press-fitted to this connecting shaft 12. With this configuration.
the rotating disk 3 rotates integrally with the rotating shaft 11.
100291
The rotating housing 1 is configured to be able to rotate with respect to the
rotating shaft 11 while surrounding the rotating disk 3. More specifically, the
rotating housing 1 includes paired disk portions la and lb each having a doughnut
shape provided at the front and the rear in the axial direction of the rotating shaft 11
so as to face both surfaces of the rotating disk 3, and a cylinder portion l c that
connects the outer circumference portions of the disk portions la and lb and faces
the outer peripheral surface of the rotating disk 3.
[0030]
Each of the disk portions la and lb is supported through bearings 15a and
15b with the sleeve 13 integrated with the rotating shaft 11. With this configuration,
the rotating housing 1 can freely rotate with respect to the rotating shaft 11 in a state
where the paired disk portions la and 1 b and the cylinder portion l c are combined
with each other. In the example in FIG. IA, a mode is illustrated in which the disk
portion 1 a on the front side is formed integrally with the cylinder portion lc, and
they are combined with the disk portion 1b on the rear side with a bolt, for example.
1003 11
Here, in the first embodiment, in order to cause a space between both
surfaces of the rotating disk 3 and the inner surface of each of the disk portions la
and lb to function as a working chamber for the working fluid, disk vanes 4a and 4b
radially extending from the inner circumference to the outer periphery are provided
on both surfaces of the rotating disk 3 facing the disk portions la and lb (see FIG.
1A and FIG. 1C).
[0032]
Similarl_): in the rotating housing 1, housing vanes 5a and 5b corresponding
to the disk vanes 4a and 4b on both surfaces of the rotating disk 3 and radially
extending from the inner circumference to the outer periphery are provided on the
inner surfaces of the disk portions I a and lb facing both surfaces of the rotating disk
3 (see FIG. I A and FIG. 1 B).
100331
As illustrated in FIG. ID, the disk vanes 4a,4b and the housing vanes 5a, 5b
are disposed so as to be paired at positions adjacent to each other at the front and the
rear in the axial direction of the rotating shaft 11 in a manner such that they are used
as fluid couplings. Then, the disk vanes 4a and 4b, and the housing vanes 5a and
5b each have a surface directed so as to be perpendicular to the rotational direction
of each of the vanes. Areas lying across the circumferential direction are made
between the disk vanes 4a, 4b and the housing vanes 5a, 5b, and form torus-shaped
working chambers paired at the front and the rear therein.
100341
In FIG. LA, a mode is illustrated in which the disk vanes 4a and 4b are
formed as impellers separately from the rotating disk 3, and are attached to the
rotating disk 3. However, the disk vanes 4a and 4b may be formed integrally with
the rotating disk 3. Similarly, a mode is illustrated in which the housing vanes 5a
and 5b are formed as impellers separately from the disk portions 1 a and lb, and are
attached to the disk portions la and lb. However, the housing vanes 5a and 5b may
be formed integrally with the disk portions la and lb.
[003 51
The rotating housing 1 is filled with (accommodates) working fluid (oil,
water, or fluid obtained by combining them), not illustrated. This working fluid is
prevented from leaking by ring-shaped seal members not illustrated and disposed
adjacently to the bearings 15a and 15b supporting the disk portions la and lb.
With this configuration. the rotating housing 1, including the working chambers
between the disk vanes 4a and 4b and the housing vanes 5a and 5b, is filled with the
working fluid at all times.
(00361
The rotating housing 1 has an outer periphery provided with radiating fins 2
integrally formed with the cylinder portion LC. Note that, in the disk portions la
and lb of the rotating housing 1, the radiating fins 2 may be provided in an area that
does not interfere with formation of a friction member of a friction brake, which will
be described later, for example, in an area of an inner circumference portion of an
external surface. These radiating fins 2 function to cool the rotating housing 1, and
cool the working fluid within the rotating housing 1.
[0037]
The retarding device illustrated in FIG. 1A includes a friction brake that
brings the rotating housing 1 to a stop at the time of braking. This friction brake
includes: a brake caliper 7 that has brake pads 8a and 8b serving as friction members
and squeezing the outer circumference portion of the rotating housing 1, in other
words, the outer circumference portion of the external surface of each of the disk
portions la and lb; and an electrically driven direct-acting actuator 9 that drives this
brake caliper 7.
[003 81
The brake caliper 7 has the brake pads 8a and 8b paired at the front and the
rear, and is pressed and supported by a bracket 17, for example, with a bolt provided
with a spring, in a state where the rotating housing 1 is disposed between the brake
pads 8a and 8b with a predetermined gap. This bracket 17 is attached to a
non-rotating portion of the vehicle.
COO391
Furthermore, the bracket 17 is rotatably supported, through a bearing 18,
with the sleeve 13 integrated with the rotating shaft 11. However, in the case of a
retarding device mounted on the output side of a transmission of the vehicle, a
transmission cover is supported through the bearing, and hence, the bracket 17 may
be fixed to the transmission cover (non-rotating portion), and be supported without
intervention of the bearing 18.
[0040]
An actuator 9 is fixed to the brake caliper 7, for example, with a bolt. The
actuator 9 is actuated, for example, with an electrically driven motor 10, and
converts rotary motion by the electrically driven motor 10 to linear motion, thereby
linearly moving the brake pad 8b on the rear side toward the disk portion lb on the
rear side.
1004 11
With this movement, the brake pad 8b on the rear side presses the disk
portion lb on the rear side. Furthermore, with an effect of the resulting
counterforce, the brake pad 8a on the front side moves toward the disk portion la on
the front side. As a result, the rotating housing I is strongly squeezed by the brake
pads 8a and 8b on the front and the rear sides.
100421
With the retarding device according to the first embodiment having the
configuration as described above, the friction brake is not activated during
non-braking periods. At this time, as the rotating housing 1 is allowed to freely
rotate with respect to the rotating shaft 11, the rotating disk 3 rotates integrally with
the rotating shaft 1 I. In association with the rotation of the rotating disk 3, the disk
vanes 4a and 4b and the housing vanes 5a and 5b function as fluid couplings, and the
rotating housing 1 integrally rotates synchronously with the rotating disk 3. With
this configuration, there occurs no difference in relative rotational speed between the
disk vanes 4a and 4b and the housing vanes 5a and 5b, and hence, braking force does
not occur.
10043 ]
On the other hand, at the time of braking, the friction brake is activated, and
the rotating housing 1 is squeezed by the brake pads 8a and 8b serving as the friction
members. With this operation, the rotating housing 1 stops rotating, and the brake
member 1 is brought to a stop. If only the rotating housing 1 is brought to a stop
when the rotating disk 3 is rotating, a difference in relative rotational speed takes
place between the housing vanes 5a and 5b of the disk portions la and lb (rotating
housing 1) and the disk vanes 4a and 4b of the rotating disk 3. This causes the
working fluid within the working chamber to circulate between the disk vanes 4a and
4b and the housing vanes 5a and 5b, which generates flow of circulation of the
working fluid. At this time, the working fluid comes into collision with the disk
vanes 4a and 4b, and serves as a resistance that prevents the rotating disk 3 from
rotating integrally with the disk vanes 4a and 4b. This leads to a generation of
braking force on the rotating disk 3, whereby it is possible to reduce the rotational
speed of the rotating shaft 11 through the rotating disk 3.
100441
At this time, kinetic energy of the rotating shaft 11 is converted into thermal
energy in association of the generation of braking force, whereby temperatures of the
working fluid increase. The heat given to this working fluid is transferred to the
rotating housing 1, and is dissipated mainly through the radiating fins 2.
Furthermore, the heat generated at the time of braking is accumulated to some
degree in a form of an increase in temperatures of the working fluid and an increase
in temperatures of the rotating housing 1. Then, by cancelling the activation of the
friction brake during non-braking periods, the rotating housing 1 is made rotate at a
high speed, thereby actively radiating the heat from the radiating fins 2.
100451
According to the retarding device of the first embodiment, there is no need
for the external heat exchanger for cooling the working fluid having high
temperatures at the time of braking, and furthermore, there is no need for a special
mechanism for supplying or discharging the working fluid to or from the working
chamber or for a reservoir container for storing the working fluid. Thus, it is
possible to achieve a simplified device configuration, the reduced weight, and the
reduced size. Furthermore, the working chamber within the rotating housing 1 is
always filled with the working fluid regardless of whether the device is in a time of
switching from braking to non-braking and vice versa. Thus, it is not necessary to
supply or discharge the working fluid to or from the working chamber, thereby
exhibiting excellent responsivity in terms of switching.
[0046]
Next, a modification example of the first embodiment will be described with
reference to FIG. 1E.
FIG. 1E is a diagram illustrating a modification example of the first
embodiment. Here, reference characters 40a, 40b, 50a, and 50b correspond to
reference characters 4a, 4b, 5a, and 5b in FIG. 1A to FIG. ID.
[0047]
As illustrated in FIG. lE, in the modification example of the first
embodiment, a disk vane 40a, 40b and a housing vane 50a, 50b adjacent to each
other are disposed at the front and the rear in the axial direction of the rotating shaft
11, and form a pair so as to be used as fluid couplings. Then, each disk vane 40a
and 40b is made to slope toward the rear in the rotational direction as it approaches
each of the housing vanes 5Oa, 50b from the rotating disk 3.
Furthermore, each housing vane 50a and 50b is sloped toward the rear in the
rotational direction as it extends away from the disk vane 40a, 40b and it extends
toward the inner surface side of the rotating housing 1. Configurations other than
those described above are similar to those in the first embodiment, and hence,
explanation thereof will not be repeated.
[0048]
According to the modification example of the first embodiment having the
configuration as described above, each of the disk vanes 40a and 40b is sloped
toward the rear in the rotational direction with approach from the rotating disk 3
toward the housing vanes 50a and 50b, and each of the housing vanes 50a and 50b is
sloped toward the rear in the rotational direction with distance from the disk vane
40a, 40b and with approach toward the inner surface side of the rotating housing 1.
whereby it is possible to increase the braking force as compared with a case where
they are not sloped.
100491

Below, a fluid-type retarding device according to a second embodiment of
the present invention will be described with reference to FIG. 2.
FIG. 2 is a schematic view illustrating the entire configuration of the
fluid-type retarding device, which is the second embodiment of the present invention,
and is a side view in which part of the device is sectionally illustrated. The
retarding device according to the second embodiment is obtained by modifying the
configuration of the retarding device according to the first embodiment, and is
different from that in the first embodiment in the following points.
[OOSO]
As illustrated in FIG. 2, the retarding device according to the second
embodiment includes disk vanes 4b provided on one surface (rear side of the rotating
shaft 11) of the rotating disk, and housing vanes 5b on the rear side provided to the
disk portion lb on the rear side of the rotating housing 1. Furthermore, the second
embodiment has a configuration in which only one working chamber is disposed on
the rear side of the rotating disk 3 in the axial direction of the rotating shaft I I.
Configurations other than those described above are similar to those in the first
embodiment. Hence, the same reference characters are attached, and explanation
thereof will not be repeated. Note that it is optional whether the disk vanes and the
housing vanes are formed in a direction perpendicular to the rotational direction as
illustrated in FIG. ID, or are formed in a direction sloped with respect to the
rotational direction as illustrated in FIG. 1E.
[OOS 1 ]
With the second embodiment having the configuration as described above,
only one working chamber is provided, and hence, it is possible to reduce the size of
the rotating shaft 11 in the axial direction thereof.
lo0521

Below, a fluid-type retarding device according to a third embodiment of the
present invention will be described with reference to FIG. 3A to FIG. 3C.
FIG. 3A is a schematic view illustrating the entire configuration of the
fluid-type retarding device, which is the third embodiment of the present invention,
and is a side view in which part of the device is sectionally illustrated. FIG. 3B is a
diagram illustrating a cross section along IIIB-IIIB in FIG. 3A and FIG. 3C is a
diagram illustrating a cross section along IIIC-IIIC in FIG. 3A. The retarding
device according to the third embodiment is obtained by modifying the configuration
of the retarding device according to the first embodiment, and is different from that
in the first embodiment in the following points.
[0053]
In the retarding device according to the third embodiment, of the disk vanes
4-a and 4b formed on both surfaces of the rotating disk 3, each of the disk vanes 4a
on the front side provided on the surface that faces the disk portion la on the front
side of the rotating housing 1 extends in a spirally curved manner from the inner
circumference to the outer periphery toward a direction opposite to the rotational
direction (see the white arrow in FIG. 3B) of the rotating disk, as illustrated in FIG.
3A and FIG. 3B. On the other hand, as illustrated in FIG. 3A and FIG. 3C, each of
the disk vanes 4b on the rear side provided on the surface that faces the disk portion
lb on the rear side of the rotating housing 1 extends in a spirally curved manner
from the inner circumference to the outer periphery in the rotational direction (see
the white arrow in FIG. 3C) of the rotating disk 3.
[0054]
Furthermore, at an inner circumference portion of the rotating disk 3, plural
through-holes 3a having an oval shape are provided over the circumferential
direction.
[0055]
Furthermore, the connecting shaft 12 connected integrally with the rotating
shaft 11 is a tubular body having an internal space whose both ends are closed, and
this internal space is filled with and accommodates the working fluid. For the
connecting shaft 12 and the sleeve 13 press-fitted to the connecting shaft 12, plural
communicating holes 6a and 6b that each connect the internal space of the rotating
housing 1 and the internal space of the connecting shaft 12 are provided in the
circumferential direction and are located on both sides of the rotating disk 3 and at
the front and the rear of the connecting shaft 12 and the sleeve 13 in the axial
direction of the rotating shaft 11.
[0056]
With the retarding device according to the third embodiment having the
configuration as described above, as the rotating disk 3 (disk vanes 4a and 4b)
rotates integrally with the rotating shaft 11, the working fluid within the internal
space on the front side of the rotating housing 1 is transferred from the inner
circumferential side to the outer peripheral side by the disk vanes 4a on the front side,
and the working fluid transferred to the outer peripheral side is transferred to the
internal space on the rear side (see the right arrow with a solid line in FIG. 3A and
FIG. 3B). At the same time, within the internal space on the rear side of the
rotating housing 1, the working fluid is transferred from the outer peripheral side to
the internal peripheral side by the disk vanes 4b on the rear side (see the downward
arrow with a broken line in FIG. 3A and FIG. 3C). The working fluid transferred to
the inner circumference side passes through the through-holes 3a at the inner
circumference portion of the rotating disk 3, and is transferred to the internal space
on the front side of the rotating housing 1 (see the left arrow with a solid line in FIG.
3A). As described above, the working fluid circulates around the rotating disk 3
within the rotating housing 1.
[OO571
Furthermore, in the third embodiment, part of the working fluid transferred
to the inner circumferential side by the disk vanes 4b on the rear side passes through
the communicating holes 6b on the rear side that open to the inner circumference,
and is transferred to the inside of the connecting shaft 12 (rotating shaft 11) (see the
arrow with a dotted line in FIG. 3A and FIG. 3C). The working fluid transferred to
the inside of the connecting shaft 12 passes through the comm~lnicatingh ole 6a on
the front side, and is transferred to the internal space on the front side of the rotating
housing 1 (see the arrow with a dotted line in FIG. 3A and FIG. 3B). As described
above. it is possible to make the internal space of the connecting shaft 12 (rotating
shaft 11) function as a reservoir tank for the working fluid, and the working fluid
within the rotating housing 1 circulates throughout the space including through the
internal space of the connecting shaft 12 thereof.
[OOS 81
Thus, the retarding device according to the third embodiment also achieves
a similar effect obtained by the first embodiment.
100591
With the third embodiment, the working fluid within the rotating housing 1
entirely circulates, and hence, it is possible to prevent temperatures of the working
tluid from locally rising. Furthermore, it is possible to utilize the internal space of
the connecting shaft 12 (rotating shaft 11) as the reservoir tank. Thus, the thermal
capacity of the working fluid increases according to the volume of the internal space
of the connecting shaft 12, and hence, it is possible to prevent temperatures of the
working fluid from excessively rising in a short period of time. As a result, it is
possible to sufficiently maintain the duration of braking.
[0060]
It should be noted that it may be possible to exchange the positions of the
disk vanes 4a and 4b from front to rear and vice versa.
[006 11

Below, a fluid-type retarding device according to a fourth embodiment of
the present invention will be described with reference to FIG. 4A and FIG. 4B.
FIG. 4A is a schematic view illustrating the entire configuration of the
fluid-type retarding device, which is the fourth embodiment of the present invention,
and is a side view in which part of the device is sectionally illustrated. FIG. 4B is a
diagram illustrating a cross section along IVB-IVB in FIG. 4A. The retarding
device according to the fourth embodiment is obtained by modifying the
configuration of the retarding device according to the first embodiment.
LO0621
At the time of actual braking, the rotating housing 1 is heated due to slide
with the friction member of the friction brake. The heat generated in the rotating
housing 1 is radiated mainly from the radiating fins 2 as described above.
However, at the time of braking, the rotating housing 1 is not moving, and hence, the
cooling function of the radiating fins 2 works less effectively than when the rotating
housing 1 rotates synchronously with the rotating disk 3 such as during non-braking
periods. If the cooling function of the radiating fins 2 does not work sufficiently,
there is a possibility that the working fluid within the rotating housing 1 is not
sufficiently cooled. Thus, it is desirable to contrive to suppress the increase in
temperatures of the rotating housing 1.
10063)
The retarding device according to the fourth embodiment is obtained by
focusing on this point. More specifically, as illustrated in FIG. 4A and FIG. 4B, the
retarding device according to the fourth embodiment includes impellers 20a and 20b
disposed next to the external surface of each of the paired disk portions la and 1b
constituting the rotating housing 1. Each of the impellers 20a and 20b is
press-fitted and fixed to the connecting shaft 12 connected integrally with the
rotating shaft 11.
100641
With the retarding device according to the fourth embodiment having the
configuration as described above, even if the rotational speed of the rotating shaft 11
reduces during braking, the impellers 20a and 20b rotate if the rotating shaft 11
rotates. Thus, it is possible to blow air from the impellers 20a and 20b toward the
rotating housing 1 that is at rest (see the arrows with a solid line in FIG. 4A). This
makes it possible to forcibly cool the rotating housing 1, and prevent the
temperatures of the rotating housing 1 from rising.
10065 ]
It should be noted that the impellers 20a and 20b as described above are
applicable not only to the retarding device according to the first embodiment but also
to the retarding devices according to the second and the third embodiments.
(00661

Below, a fluid-type retarding device according to a fifth embodiment of the
present invention will be described with reference to FIG. 5.
FIG. 5 is a schematic view illustrating the entire configuration of the
fluid-type retarding device, which is the fifth embodiment of the present invention,
and is a side view in which part of the device is sectionally illustrated. As in fourth
embodiment, the retarding device according to the fifth embodiment is obtained by
focusing on suppressing the increase in temperatures of the rotating housing 1, and
by modifying the configuration of the retarding device according to the first
embodiment.
10067 )
More specifically, as illustrated in FIG. 5, the retarding device according to
the fifth embodiment includes a sheathed temperature sensor 21. This temperature
sensor 21 is connected with a temperature sensor holder 22 that moves in association
with either one of the brake pads 8a and 8b paired at the front and the rear and
serving as the friction member of the friction brake, for example, in association with
the brake pad 8b on the rear side. Here, the temperature sensor 21 is connected
with the temperature sensor holder 22, and at the time of braking, the top end of the
sheath of the temperature sensor 21 is brought into contact with the external surface
of the disk portion lb in association with movement of the brake pad 8b on the rear
side toward the disk portion lb on the rear side. Furthermore, the temperature
sensor 21 is connected with an actuator controlling unit 23 that controls actuation of
the actuator 9 of the friction brake.
[OO68]
With the retarding device according to the fifth embodiment having the
configuration as described above, during braking periods, the top end of the sheath
of the temperature sensor 21 is brought into contact with the disk portion lb
(rotating housing 1) on the rear side, and continuously detects temperatures of the
disk portion lb. At this time, the actuator controlling unit 23 monitors
temperatures of the disk portion Ib detected by the temperature sensor 21, and stops
actuating the actuator 9 if the temperature exceeds a predetermined temperature.
Once the actuation of the actuator 9 is stopped, the brake pads 8a and 8b and the
temperature sensor 21 move away from the disk portion Ib, and are switched into a
non-braking state. As a result, the rotating housing 1 rotates together with the
rotating shaft 1 I, and the rotating housing 1 is cooled with the radiating fins 2.
Then, the actuator controlling unit 23 actuates the actuator 9 again after a
predetermined period of time elapses after actuation of the actuator 9 is stopped, to
brake the brake member 1. With the operations described above, it is possible to
suppress the increase in temperatures of the rotating housing 1.
COO691
The predetermined temperature for the actuator 9 to stop activating and the
predetermined period of time for the actuator 9 to restart actuating are set as
appropriate according to materials or shapes or dimensions of the rotating housing 1
or the upper temperature limit of the fluid, and are set in advance in the actuator
controlling unit 23. For example, the predetermined temperature is set in the range
of approximately 170 to 180°C, and the predetermined period of time is set in the
range of approximately 5 to 10 seconds.
[0070]
It should be noted that the temperature sensor 21 as described above may be
configured to move integrally with the brake pad 8a on the front side. Furthermore,
the temperature sensor 21 is applicable not only to the retarding device according to
the first embodiment but also to the retarding devices according to the second to the
fourth embodiments.
[007 11

Below, a fluid-type retarding device according to a sixth embodiment of the
present invention will be described with reference to FIG. 6.
FIG. 6 is a schematic view illustrating the entire configuration of the
fluid-type retarding device, which is the sixth embodiment of the present invention,
and is a side view in which part of the device is sectionally illustrated. As in the
fourth embodiment, the retarding device according to the sixth embodiment is
obtained by focusing on suppressing the increase in temperatures of the rotating
housing I, and by modifying the configuration of the retarding device according to
the first embodiment.
100721
More specifically, as illustrated in FIG. 6, the retarding device according to
the sixth embodiment includes a water cooling body (cooling member) 24. This
water cooling body 24 is connected with a water-cooling-body holder 25 that moves
integrally with either one of the brake pads 8a and 8b paired at the front and the rear
and serving as the Giction member of the friction brake, for example, moves
integrally with the brake pad 8b on the rear side. Furthermore, at the time of
braking, the water cooling body 24 is brought into contact with the external surface
of the disk portion lb in association with movement of the brake pad 8b on the rear
side toward the disk portion lb on the rear side of the rotating housing 1.
100731
Furthermore, a water passage 26 is formed within the water cooling body
24, and has an inlet port and an outlet port each connected with pipes, not illustrated.
These pipes are connected with a cooling water system (for example, a radiator) of
the vehicle, and cooling water circulates through the water passage 26 within the
water cooling body 24, whereby low temperatures are maintained at all times.
100741
With the retarding device according to the sixth embodiment having the
configuration as described above, at the time of braking, the water cooling body 24
is brought into contact with the disk portion lb on the rear side (rotating housing 1).
Thus, the disk portion lb is forcibly cooled through heat exchange with the water
cooling body 24. As described above, it is possible to prevent the increase in
temperatures of the rotating housing 1.
100751
It should be noted that the water cooling body 24 as described above may be
configured to move integrally with the brake pad 8a on the front side. Furthermore,
the water cooling body 24 is applicable not only to the retarding device according to
the first embodiment but also to the retarding devices according to the second to the
fifth embodiments. Note that, instead of the water cooling body 24. a cooling
member in which cooling oil and the like flows may be used.
[0076]

Below, a fluid-type retarding device according to a seventh embodiment of
the present invention will be described with reference to FIG. 7A and FIG. 7B.
FIG. 7A is a schematic view illustrating the entire configuration of the
fluid-type retarding device, which is the seventh embodiment of the present
invention, and FIG. 7B is a diagram illustrating a cross section along VIIB-VIIB in
FIG. 7A. The retarding device according to the seventh embodiment is obtained by
modifying the configuration of the retarding device according to the first
embodiment, and adding an element of an eddy-current retarding device.
100771
More specifically, as illustrated in FIG. 7A and FIG. 7B, the retarding device
according to the seventh embodiment has the following configuration in order to
obtain braking force using fluid resistance of the working fluid, and at the same time,
obtain braking force using eddy current occurring due to an effect of a magnetic field.
For example, the disk vanes 4a and 4b are provided only to an inner circumference
portion of the rotating disk 3, and the housing vanes 5a and 5b paired with the disk
vanes 4a and 4b are provided only to an inner circumference portion of the disk
portions la and lb.
COO7 81
Plural permanent magnets 30a and 30b are arranged circumferentially on
outer circumference portions of both surfaces of the rotating disk 3. The permanent
magnets 30a and 30b are arranged in a manner such that magnetic poles (north pole
and south pole) are directed to an axial direction of the rotating shaft 1 I, in other
words, are directed to an axial direction of the rotating disk 3, and different magnetic
poles are alternately arranged in the circumferential direction.
100791
Furthermore, disk-shaped brake members (eddy-current generating portions)
3 la and 3 1b having a doughnut shape and paired with the permanent magnets 30a
and 30b are arranged on an outer circumference portion of an inner surface of each
of the disk portions la and fb facing the permanent magnets 30a and 30b. Each of
the brake members 3 la and 3 1b is formed with an electrically conductive material.
which includes a ferromagnetic material such iron, a soft magnetic material such as
ferritic stainless steel, and a non-magnetic material such as aluminum alloy and
copper alloy. Furthermore, it is more preferable that the surface layer portion of
the inner surface of each of the brake members 3 la and 3 1 b facing the permanent
magnets 30a and 30b is made out of a highly electrically conductive material such as
copper and copper alloy.
[0080]
With the retarding device according to the seventh embodiment having the
configuration as described above, during non-braking periods, the rotating housing 1
can freely rotate with respect to the rotating shaft 11. Thus, in association with the
rotating disk 3 rotating integrally with the rotating shaft 11, the disk vanes 4a and 4b
and the housing vanes 5a and 5b function as fluid couplings. At the same time, the
brake members 3 la and 3 1b of the rotating housing 1 receive a magnetic attraction
force (in the case where the brake member is made out of a magnetic material) of the
permanent magnets 30a and 30b held by the rotating disk 3, or the Lorentz force (in
the case where the brake member is made out of a non-magnetic material) due to an
effect of the magnetic field. For these reasons. the rotating housing 1 integrally
rotates synchronously with the rotating disk 3. In this case, no difference in
relative rotational speed substantially takes place between the disk vanes 4a and 4b
and the housing vanes 5a and 5b, as well as between the permanent magnets 30a and
30b and the brake members 31a and 3 1b. and hence, braking force does not occur.
(008 l]
Here, in the case where the brake members 3 1 a and 3 1 b are made out of a
non-magnetic material, no magnetic attraction force acts between the magnets 30a
and 30b and the brake members 31a and 31b. However, as the magnets 30a and
30b rotate and move while causing the magnetic filed on the brake members 31a and
3 1 b, the braking force occurs on the brake members 3 1 a and 3 1b due to the effect of
the magnetic field, and hence, the brake members 3 1 a and 3 1b rotate in the same
direction as the magnets 30a and 30b. More specifically, the rotating housing 1
rotates in the same direction as the rotating disk 3 with a slightly different relative
rotational speed so as to maintain a balance between the braking force generated as a
result of the difference in relative rotational speed between the brake members 3 la
and 31b and the magnets 30a and 30b, and a loss occurring at a bearing portion due
to rotation of the rotating housing 1 or drag force related to air resistance caused by
rotation of the rotating housing 1. In other words, in the case where the brake
members 31a and 3 1b are made out of a non-magnetic material, the rotating housing
1 does not rotate in a fully synchronized manner with the rotating disk 3 but
substantially synchronously rotates with a slight difference in rotational speed,
whereby non-braking state is maintained.
100 8 21
On the other hand, at the time of braking, only the rotating housing 1 is
brought to a stop with actuation of the friction brake. Once only the rotating
housing 1 is brought to a stop, a difference in relative rotational speed takes places
between the disk vanes 4a and 4b and the housing vanes 5a and 5b. This leads to a
generation of circulation flow of the working fluid in the working chamber, and a
fluid resistance that prevents the rotation of the rotating disk 3 (disk vanes 4a and
4b) takes places, whereby it is possible to obtain the braking force. At the same
time, there occurs a difference in relative rotational speed between the permanent
magnets 30a and 30b and the brake members 3 la and 31b, so that eddy current is
generated on the inner surfaces of the brake members 31a and 3 1b. Then, braking
force in a direction opposite to the rotational direction of the rotating disk 3 rotating
takes place in accordance with the Fleming's left-hand rule based on the synergistic
effect between the eddy current generated on the inner surfaces of the brake
members 3 la and 3 1b and the magnetic flux density from the permanent magnets
30a and 30b. As described above, by utilizing the eddy current generated with the
effect of the magnetic field from the permanent magnets 30a and 30b in addition to
the fluid resistance of the working fluid, it is possible to effectively obtain the
braking force.
[0083]
It should be noted that, as for the arrangement of the permanent magnets 30a
and 30b paired with the brake members 3 la and 3 lb, and the arrangement of the disk
vanes 4a and 4b paired with the housing vanes 5a and 5b, it may be possible to
interchange the outer circumference portion side with the inner circumference
portion side. Furthermore, as for the arrangement of the permanent magnets 30a
and 30b and the brake members 31a and 31b, it may be possible to interchange the
rotating disk 3 side with the rotating housing 1 side as long as they form a pair.
Furthermore, the permanent magnets 30a and 30b and the brake members 3 la and
31b described above are applicable not only to the retarding devices according to the
first embodiment but also to the retarding device according to the second to the sixth
embodiments.
10084 1
Although the retarding device according to the seventh embodiment
includes the permanent magnets 30a and 30b, the amount thereof is smaller than that
in a regular eddy-current retarding device. Thus, it is possible to reduce cost of the
permanent magnets 30a and 30b, and achieve stabilization. Furthermore, although
the brake members 3 1 a and 3 1 b are heated due to eddy current generated on the
brake members 3 la and 3 lb, the heat is transferred to the rotating housing 1, and is
radiated through the radiating fins 2. Thus it is possible to efficiently suppress the
increase in temperatures of the brake members 3 la and 3 1b due to the heat
generation.
[0085]
It should be noted that the present invention is not limited to each of the
embodiments described above, and various modifications thereto are possible
without departing from the scope of the present invention.
For example, in each of the embodiments described above, descriptions have
been made of the case where disk vanes 4a and 4b are formed on surfaces on both
sides of the rotating disk 3. For example, it may be possible to employ a
configuration in which the disk vanes are formed on one surface of the rotating disk
3. Furthermore, it may be possible to employ a configuration in which the
permanent magnets 30a and 30b are arranged only on one surface of the rotating disk
3. Note that, in the case where the disk vanes are formed only on one surface of the
rotating disk 3, it is preferable not to form the through-holes 3a described above.
[0086]
Furthermore, in the third embodiment described above, descriptions have
been made of the case where the communicating holes 6a and 6b that allow the
internal space of the rotating housing 1 and the internal space of the connecting shaft
12 to communicate with each other are formed. However, it is optional as to
whether to make the internal space of the rotating housing 1 and the internal space of
the connecting shaft 12 communicable to each other.
[0087]
Furthermore, it may be possible to employ a configuration in which thermal
treatment or surface treatment is applied to the outer circumference portions of the
external surfaces of the disk portion la and lb (rotating housing 1) against which the
friction members 8a and 8b are pressed at the time of braking, thereby increasing the
surface hardness thereof, or a steel sheet having excellent wear resistance is attached
on these outer circumference portions, thereby reducing the amount of wear. In the
case where the rotating housing 1 is made out of aluminum alloy, it may be possible
to apply an anodic oxide coating process to improve the wear resistance.
[0088]
Furthermore, it is optional as to whether to provide the impellers 20a and
20b connected to the rotating shaft 11, the actuator 9 that moves the paired brake
pads 8a and 8b toward the disk portions la and Ib, the actuator controlling unit that
stops actuating the actuator 9 in the case where temperatures of the disk portions la
and lb exceed a predetermined temperature, and the cooling member (for example,
the water cooling body 24) that is brought into contact with the external surface of
each of the disk portions la and lb.
100891
Furthermore, in the sixth embodiment described above, descriptions have
been made of the case where the permanent magnets 30a and 30b are disposed on
surfaces on both sides of the rotating disk 3, and the eddy-current generating
portions 3 la and 3 1b are disposed on inner surfaces of both sides of the disk portions
la and lb. However, it is possible to optionally determine whether the permanent
magnets are arranged on the surface of the rotating disk 4 perpendicular to the
rotating shaft 11 or on the outer peripheral surface of the rotating disk 4.
Furthermore, instead of the permanent magnets, it may be possible to form an
eddy-current generating portion.
Furthermore, in the case where the permanent magnets or the eddy-current
generating portion is formed on a surface of the rotating disk 3 facing each of the
disk portions la and lb, it may be possible to form the permanent magnets or the
eddy-current generating portion on the inner circumferential side of the disk vanes
4a and 4b.
[00901
Furthermore, as for the friction brake that brings the brake member to a stop
at the time of braking, it may be possible to use not only a friction brake that
employs the electrically driven direct-acting actuator as a driving source to press the
brake pads against the external surface of the brake member (disk portion) but also a
friction brake that employs an electromagnetic clutch mechanism with
electromagnets to press a clutch plate serving as the friction member against the
external surface of the brake member, or a configuration that employs a drum brake
mechanism and presses brake shoes serving as the friction member against the outer
peripheral surface of the brake member (cylinder portion).
Industrial Applicability
[009 11
According to the fluid-type retarding device of the present invention, it is
possible to provide a fluid-type retarding device that can achieve the reduced weight
and the reduced size by simplifying the device configuration and reducing the size in
the axial direction of the rotating shaft to be connected.
Brief Description of the Reference Symbols
LO0921
1: rotating housing
la, 1 b: disk portion
lc: cylinder portion
2: radiating fin
3: rotating disk
3a: through-hole
4a, 4b, 40a, 40b: vane (disk vane)
5a, 5b, 50a, 50b: vane (housing vane)
6a, 6b: communicating hole
7: brake caliper
8a, 8b: brake pad
9: electrically driven direct-acting actuator
10: electrically driven motor
1 1 : rotating shaft
12: connecting shaft
13: sleeve
15a, 15b: bearing
17: bracket
18: bearing
20a, 20b: impeller
21 : temperature sensor
22: temperature sensor holder
23: actuator controlling unit
24: water cooling body (cooling member)
25: water-cooling-body holder
26: water passage
30a, 30b: permanent magnet
3 la, 3 1b: brake member (eddy-current generating portion)
We claim:
1. A fluid-type retarding device, comprising:
a rotating disk provided to a rotating shaft;
a rotating housing that includes paired disk portions and a cylinder portion
connecting outer circumferential portions of the disk portions so as to surround the
rotating disk, and is rotatably supported with the rotating shaft; and
a friction brake that presses a friction member against the rotating housing
at a time of braking to bring the rotating housing to a stop, wherein
on at least one surface of the rotating disk, a disk vane extending from an
inner circumference of the surface toward an outer peripheral side is formed,
on an inner surface of each of the paired disk portions corresponding to the
disk vane, a housing vane extending from an inner circumference to an outer
periphery is formed, and
working fluid is accommodated within the rotating housing.
2. The fluid-type retarding device according to claim 1. wherein
the disk vane is formed on both sides of the rotating disk, and
a through-hole is provided on an inner circumference portion of the rotating
disk.
3. The fluid-type retarding device according to claim 1, wherein
the disk vane is formed on both sides of the rotating disk; and
an outer peripheral side of the disk vane formed on one surface of the
rotating disk is formed so as to extend toward the rear in a rotational direction of the
rotating disk, and an outer peripheral side of the disk vane formed on the other
surface is formed so as to extend toward the front in the rotational direction of the
rotating disk.
4. The fluid-type retarding device according to any one of claim 1 to claim 3,
wherein
the rotating shaft supporting the rotating housing has a tubular body having
a space accommodating the working fluid therein, and includes a communicating
hole that allows an internal space of the rotating housing and an internal space of the
rotating shaft to communicate with each other.
5. The fluid-type retarding device according to any one of claim 1 to claim 4,
further comprising:
an impeller provided to the rotating shaft so as to be proximate to an
external surface of each of the paired disk portions.
6. The fluid-type retarding device according to any one of claim 1 to claim 5,
wherein
the friction brake includes:
a brake caliper that is fixed to a non-rotating portion of a vehicle
provided with the rotating shaft and includes paired brake pads that each serve as the
friction member and squeeze the paired disk portions; and
an actuator that drives the brake caliper and moves the paired brake
pads toward the disk portions.
7. The fluid-type retarding device according to claim 6, f~~rthceorm prising:
a temperature sensor that is brought into contact with an external surface of
each of the disk portions in association with movement of the brake pads toward the
disk portions, and detects a temperature of each of the disk portions; and
an actuator controlling unit that stops actuating the actuator in a case where the
temperature of the disk portion detected by the temperature sensor exceeds a
predetermined temperature.
8. The fluid-type retarding device according to claim 6 or 7, further
comprising:
a cooling member that is brought into contact with an external surface of
each of the disk portions in association with movement of the brake pads toward
the disk portions.
9. The fluid-type retarding device according to any one of claim I to claim 8,
wherein
either one of a plurality of permanent magnets and an eddy-current
generating member is formed on at least any one surface of both surfaces and an
outer peripheral surface of the rotating disk;
an eddy-current generating member is formed on a surface selected from
among inner surfaces of the disk portions and an inner peripheral surface of the
cylinder portion, each of which constitutes the rotating housing, this selected
surface corresponding to the surface of the rotating disk having the plurality of
permanent magnets formed thereon;
a plurality of permanent magnets are formed oil a surface corresponding to
the surface of the rotating disk having the eddy-current generating member formed
thereon; and
the plurality of permanent magnets are arranged in a manner such that
opposing magnetic poles are alternately arranged in a circumferential direction of
the rotating disk.