 |
Description  |
|
|
BACKGROUND OF THE INVENTION
The present invention relates to improvements over the dust-proof structure
for a linear motion actuator with a carriage which is provided in a
casing, and is linearly moved in an axial direction.
In general, a linear motion actuator is provided with a type as shown in
FIGS. 6 and 7. A pair of parallel linear guides are disposed on an
elongated base 101. A carriage 105 is fastened to a slider 104, which
linearly moves along the guide rail 103. The carriage 105 is coupled with
a ball nut 107 of a ball-and-screw mechanism 106 as a rotation-linear
converting mechanism. An AC servo motor 108 drives a ball-screw shaft 109
to rotate. With rotation of the ball-screw shaft, the carriage 105 is
linearly moved along the guide rail 103 in the axial direction. A
workpiece W is fastened onto the driven member mounting portion 110
located on both sides of the carriage 105, by means of screws. The
accurate linear motion and the accurate positioning of the work can be
carried out repeatedly.
The actuator is covered with side covers 111, an upper cover 112, an end
cover 113, and the like, for the purposes of improving appearance and
protecting the inner accurate parts, such as the linear guides 102 and the
ball-and-screw mechanism 106, from incoming dust.
The driven member mounting portion 110 of the carriage 105 must be exposed
to, so slits are formed between each side cover and the upper cover 112.
The slits axially extend over the entire range of the movement of the
carriage 105. The slits S allows dust to enter the inside of the casing.
In this respect, the dust-proof measure is imperfect.
A linear motion actuator of the type in which the slits covering the
carriage movement range are covered with a movable belt is disclosed in
Unexamined Japanese Utility Model Publication No. Hei. 4-60642. As shown
in FIGS. 8 and 9, a carriage 121 is axially slidable within a cylinder
tube 120 with an axially elongated slit S formed in one side (upper
surface) thereof. The carriage 121 is coupled with a ball nut 124
receiving a screw shaft 123 of the ball-and-screw mechanism 122, and is
linearly moved in the axial direction by an AC servo motor 125.
A table body 126 is protrudes above the carriage 121, and is exposed over
the cylinder tube 120 through the slit S. An upper surface of the table
body 126 serves as a driven member mounting portion 128 with bolt holes
127 at the four corners.
A shaft receiving hole 130 through which the screw shaft 123 passes is
formed in the carriage 121, as shown in FIG. 9. A nut receiving space 131
for receiving the ball nut 124 is formed in the middle of the shaft
receiving hole 130. A square groove 131a is formed in the ceiling wall of
those walls defining the nut receiving space 131. The bottom of the nut
receiving space 131 is open. A ball nut 124 with a square stopper 132 is
placed in the nut receiving space 131 in a state that the protrusion 132
is fit to the groove 131a.
The carriage 121 having two downward extending slopes is shaped like V in
cross section. A slider member (not shown) is secured to the bottom edges
of the slopes of the carriage 121. In this state, the carriage 121 is
disposed within the cylinder tube 120 shaped like a diamond in cross
section.
The table body 126 which protrudes over the carriage 121 has a band
receiving hole 136 through which the seal band 135 passes. The band
receiving hole 136 has a gently upward curved band guide face 137, and
opens downward. The opening of the band receiving hole is longitudinally
elongated in the lower side of the table body. The seal band 135 made of a
thin steel band is inserted into the band receiving hole 136 from the
opening.
After the carriage 121 is assembled into the cylinder tube 120, the slit S
of the upper surface of the cylinder tube 120 is covered with the seal
band 135. A strip like rubber magnet is attached to the edge of the slit
S. The seal band 135 is magnetically attracted by the magnet rubber,
thereby improving the sealing performance by the seal band. The ends of
the seal band 135 are secured to the end cap 140 and the head cap 141. The
mid portion of the seal band 135 is located on the curved band guide face
137 of the carriage 121.
The AC servo motor 125 is turned forwardly or reversely, so that the screw
shaft 123 is driven. Then, the ball nut 124 is moved forward or backward.
In turn, the carriage 121 is moved forward or backward while being guided
by the cylinder tube 120. The workpiece mounted on the driven member
mounting portion 128 of the table body 126 is axially moved and stopped at
a desired position.
At this time, the seal band 135 prevents dust from entering through the
slit S of the cylinder tube 120. The table body 126 moves forward while
pushing upward with the curved surface of the band guide face 137.
The conventional dust proof structure of the type in which the slit S of
the cylinder tube 120 is sealed with the seal band 135 has a high dust
proofing capability, but has the following problems.
(1) Since the seal band 135 is passed within the carriage 121, the carriage
structure is complicated, and it is impossible to increase the rigidity of
the carriage 121.
(2) The band receiving hole 136 extends longitudinally to pass through the
central portion of the table body 126 of the carriage 121. The bolt holes
127 cannot be located in the central part of the driven member mounting
portion 128 which is advantageous in securing a high rigidity.
Accordingly, the bolt holes 127 must be located at the four corners of the
driven member mounting portion 128. This results in increasing the size of
the carriage 121.
In the case of a large linear motion actuator which transports a heavy
workpiece, a high rigidity is essential in order to move the work at a
high speed and to position it accurately. The carriage of the linear
motion actuator is a member which couples the linear guides with the
workpiece. Therefore, the carriage is the most important component in
determining the rigidity of the linear motion actuator. The structure
which is not capable of increasing the rigidity is not suitable for a
large actuator.
SUMMARY OF THE INVENTION
The present invention has been made in view of the above circumstances and
has an object to provide a dust-proof structure for a linear motion
actuator in which seal bands for sealing the slits allowing the carriage
to axially move are mounted outside the carriage, and the seal bands and
the carriage are axially movable in a cooperative manner, whereby the
dust-proof structure is simplified.
To achieve the above object, there is provided a linear motion actuator
having a casing, linear guides located within the casing, a carriage
axially movable with the assistance of the linear guides within the
casing, a driving device for axially moving the carriage through a
ball-and-screw mechanism, and slits elongating in the direction of the
movement of the carriage being formed in one of the sides of the casing,
the carriage including driven member mounting portions protruding above
the casing. In the linear motion actuator thus constructed, pulleys are
disposed on both ends of the casing as axially viewed. Further, one end of
the seal band is fastened to one end of the carriage, while the other end
thereof is fastened to the other end of the carriage in such a way that it
passes the pulleys, is turned back at one end of the casing, reaches the
other end of the casing, passes the pulleys, and is turned back thereat,
thereby forming a loop of the movable seal band. The slits are sealed with
the looped seal band.
The casing body is formed by an extrusion mold. An axially extending
through hole or groove is formed in the extrusion mold. The lower part of
the looped seal band passes through the through hole or groove.
Grooves may be formed in the end faces of the portions of the casing. The
grooves receive the side edge of the seal band, respectively.
A guide plate is mounted on the lower part of the looped seal band, which
passes through the through hole or groove of the casing body.
The lower side of the cover covering the upper side of the casing includes
a pair of L-shaped extensions. Sound absorbing material is placed within a
space formed by the extensions.
Thus, in the dust-proof structure for a linear motion actuator, the pulleys
are provided on both ends of the casing as axially viewed. The seal band
is looped in a manner that the seal band is fastened at one end to one end
of the carriage, and the other end is turned back. The looped seal band
circulates, together with the carriage reciprocatively moving linearly in
the axial direction, thereby sealing the slits therewith. Accordingly,
there is no need of passing the seal band through the carriage. The
carriage may have a solid and simple structure of high rigidity. The size
reduction of the linear motion actuator is easy.
By passing the lower part of the looped seal band through the through hole
or groove of the casing, the high rigidity and the light weight can both
be realized. The hollowed structure is well utilized.
Where the grooves receiving the side edges of the seal band are formed in
the end faces of the portions of the casing, which define each slit, the
sealing by the seal band is enhanced, and the abnormal shifting motion of
the seal band can be minimized. Further, the dust-proof and suppression of
noise leakage characteristics are enchanced.
With use of the guide plate to the lower part of the looped seal band, a
stable movement of the seal band is secured even if the seal band is long
for a large linear motion actuator.
Where the lower side of the cover covering the upper side of the casing
includes a pair of L-shaped extensions, and sound absorbing material is
placed within a space formed by the extensions, the rigidity of the cover
is increased and the noise proof performance is improved.
BRIEF DESCRIPTION OF THE DRAWINGS
In the accompanying drawings:
FIG. 1 is a cross sectional view showing a linear motion actuator according
to an embodiment of the present invention;
FIG. 2 is a longitudinal sectional view taken on line II--II in FIG. 1;
FIG. 3 is a longitudinal sectional view taken on line III--III in FIG. 1;
FIG. 4 is a front view, partially broken away, showing a linear guide of
the linear motion actuator;
FIG. 5 is a cross sectional view showing a second embodiment;
FIG. 6 is a plan view showing a conventional linear motion actuator;
FIG. 7 is a front view, partially broken away to illustrate the interior
structure, showing the linear motion actuator of FIG. 6;
FIG. 8 is a longitudinal sectional view showing a dust proof structure of
another conventional linear motion actuator; and
FIG. 9 is an enlarged perspective view showing a key portion of the dust
proof structure of FIG. 8.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
A first embodiment of a linear motion actuator according to the present
invention will be described with reference to FIGS. 1 through 4.
FIG. 1 is a cross sectional view showing a first embodiment of a linear
motion actuator of the present invention;
FIG. 2 is a longitudinal sectional view taken on line II--II in FIG. 1;
FIG. 3 is a longitudinal sectional view taken on line III--III in FIG. 1;
and
FIG. 4 is a front view, partially broken away, showing a linear guide of
the linear motion actuator.
In the linear motion actuator of the first embodiment, a pair of linear
guides 10 are provided within a casing 1 elongated in the axial direction
of the actuator. A carriage 20 is provided so as to move freely in the
axial direction along the linear guides 10.
A driving device 40 is provided which drives the carriage 20 through a
ball-and-screw mechanism 30 to axially move at a specified speed to a
specified position.
A pair of slits S, extending in the moving direction of the carriage 20,
are formed in the top surface of the casing 1. Each carriage 20 includes a
driven member mounting portion 24a protruded out of the casing 1 through
the corresponding slit S.
The dust-proof structure of the linear motion actuator is described below.
Pulleys 50 are located at both ends of the casing 1 (as viewed in the axial
direction), respectively. A seal band 60 has one end fastened to one end
of the carriage 20. The other end of the seal band 60 is turned up at one
end of the casing 1 through the pulley 50. The other end of the seal band
60 is further turned up at the other end of the casing 1 through another
pulley 50, so that the other end of the seal band 60 is fastened to the
other end of the carriage 20, whereby forming a movable loop of the seal
band 60. The slits S are sealed by the movable loop of the seal band 60.
The construction of the linear motion actuator will be described in more
detail below.
The casing 1 is made up of a casing body 2, a couple of side covers 3 and
3, an upper cover 4, an end cover 5, including a bearing, for closing one
end of the casing 1, and a motor bracket 6, including a bearing, for
closing the other end thereof.
In the first embodiment, the casing body 2, is extruded of aluminum. The
casing body 2 has an opening of the top thereof. A satisfactory rigidity
is required for the bottom of the casing body 2; otherwise it is deformed
by a load, thereby deteriorating the accuracy of the transportation by the
linear motion actuator. In the first embodiment, the thick part of the
bottom of the casing body 2 contains a plurality of through holes that are
axially extended. By providing these through holes, a satisfactory
rigidity and a reduction of weight are both secured.
Elongated sunken parts 8, extending over the entire length of the casing
body 2, are formed in the locations of the base of the casing body 2,
which are closer to the right and left sides thereof and symmetrical with
respect to the center of the actuator when viewed in cross section. Guide
rails 11 of the linear guide 10, respectively, are set in the sunken parts
8 and fastened thereto by bolts (not shown). Sliders 12 are slidably
mounted on the guide rails 11, respectively. In the first embodiment, a
couple of sliders 12 are mounted on each rail 11.
The structure of the linear guide 10 will briefly be described below. As
illustrated in an enlarged manner in FIG. 4, each of guide rails 11 is
substantially square in cross section. Ball rolling grooves 13 which are,
axially elongated, are formed in the upper parts of both sides of the
guide rail 11.
Each of the sliders 12, shaped like an inverted U in cross section,
consists of a horizontal portion 14 and leg portions 15 downward extended
from both ends of the horizontal portion 14. Ball bearing grooves 16 are
formed at the locations of the inner walls of the right and left leg
portions 15, which respectively confront with the ball rolling grooves 13
of the guide rails 11. Circulating paths 17, communicating with the ball
rolling grooves 13 and 16, are formed in the leg portions 15. A plurality
of balls 18, held by a holder 19, are inserted, in a rollable manner, in
the rolling paths defined by the ball bearing grooves 13 and 16, and the
circulating path 17. A plurality of holes 11a for rail mounting are formed
at proper intervals in each rail 11. Threaded holes 12a for receiving
bolts are formed at the four corners of the upper surface of each slider
12.
The carriage 20 includes a head plate 21 and a vertical portion 22 downward
extended from the bottom surface of the head plate 21. The width of the
head plate 21 is slightly shorter than the width of the inside of the
casing 1, and the length thereof is nearly equal to the total length of
the two sliders 12 longitudinally arrayed. Both sides of the head plate 21
are placed on the upper surfaces of the right and left sliders 12 of the
linear guide 10, and fastened thereto by means of bolts 27 screwed into
the threaded holes 12a. In this way, the carriage 20 is axially slidably
supported by the four sliders 12 within the casing 1.
An elongated sunken part 23 is formed at the central part of the upper
surface of the head plate 21 of the carriage 20, while extending over the
entire length of the head plate 21. Two elongated protruded portions 24,
upward protruded from the head plate 21 of the carriage 20, are located on
both sides of the sunken part 23. The protruded portions 24 extend over
the entire length of the head plate 21 of the carriage 20. The upper
surfaces of the protruded portions 24 are slightly higher than the upper
cover 4, and serve as the driven member mounting portions 24a. Stepped
portions 24b, stepped down from the driven member mounting portions 24a,
are formed at both ends of each of the protruded portions 24 when viewed
in the longitudinal direction.
The protruded portions 24 are located just above the right and left guide
rails 11 of the linear guide 10. That is, the driven member mounting
portions 24a of the carriage 20 are located on the axial lines of the
linear guide 10 where are the best locations for securing a rigidity. With
this layout of the protruded portions 24, the reduced thickness of the
head plate 21 of the carriage 20 can be used.
The ball-and-screw mechanism 30 includes a ball-screw shaft 31 and a
ball-screw nut 32. The ball-screw shaft 31, of which the outer surface is
helically threaded, is supported at one end by the end cover 5, and at the
other end by the motor bracket 6. More exactly, one end of the ball-screw
shaft 31 is received by the bearing of the end cover 5, while the other
end thereof is received by the bearing of the motor bracket 6. The
ball-screw shaft 31 is located at the central part of the casing 1 when
viewed in the width direction of the casing, while extending in parallel
with the guide rails 11 of the linear guide 10. The end portion of the
ball-screw shaft 31, supported by the motor bracket 6, protrudes out of
the motor bracket 6 and coupled with the output shaft of driving device
40, such as a drive motor.
The ball-screw nut 32 has a helical thread on the inner surface thereof,
which confront with the helical thread of the ball-screw shaft 31. The
ball-screw nut 32 engage the ball-screw shaft 31 to allow a plurality of
balls to roll between the confronting helical threads of them. The
ball-screw nut 32 is of the end-cap circulating type in which ball
circulating members (end caps) 35 are removably coupled with both ends of
the nut. A ball return path as an axially extending through-hole is formed
in the thick part of the nut body. A curved path, formed in the end face
of the end cap 35 where is in contact with the nut body, communicates with
the confronting helical threads and the return path.
With rotation of the ball-screw shaft 31 relative to the ball-screw nut 32,
steel balls forwardly roll within the helical space defined by the
confronting helical threads of the ball-screw shaft 31 and the ball-screw
nut 32. The balls emanate the helical space, travel through the curved
path of the end cap 35 and the return path of the nut body and returns to
the original position.
The ball-screw nut 32 may be of the tube circulating type or the piece
type, in place of the end-cap circulating type.
In the ball-screw nut 32 of the tube circulating type, a ball circulating
path shaped like U is assembled into the upper portion of the nut body.
The balls roll forward within the helical space defined by the confronting
helical threads, and pulled into the ball circulating tube. The balls
forwarded through the tube ride over the land of the ball-screw shaft 31,
and return to the helical space. In this way, the balls circulate through
the path endlessly.
In the ball-screw nut 32 of the piece type, a piece with a circulating
groove is embedded into the thick part of the nut body. The balls are
forwarded through the circulating groove of the piece, and ride over the
land of the ball-screw shaft 31, and return to the helical space.
An AC servo motor as the driving device 40 is firmly mounted on the outer
surface of the motor bracket 6. The output shaft of the AC servo motor 40
is coupled, through a coupling 39, with the ball-screw shaft 31 rotatably
supported by the bearing within the casing 1.
The ball-screw nut 32, which engages the ball-screw shaft 31 through the
balls, is embedded into and secured to the vertical portion 22 of the
carriage 20, whereby the carriage 20 is coupled with the ball-and-screw
mechanism 30.
When the ball-and-screw mechanism 30 is operated by the driving device 40,
the carriage 20 must be moved in the axial direction in connection with
the ball-screw nut 32. To this end, the slit S is formed between each side
cover 3 and the upper cover 4. Thus, a couple of slits S are provided
respectively in association with the couple of protruded portions 24.
The side covers 3 and the upper cover 4, which define the slits, are both
extruded of aluminum. The thick end faces, confronting with each other,
have guide grooves 3a and 4a as a guiding device for the seal band.
The upper cover 4 includes L-shaped extensions 4b and 4b in the central
portion thereof. The extensions 4b extend over the entire length of the
upper cover 4. The end faces of the extensions 4b and 4b confront with
each other, with a space therebetween being corresponding to the width of
the ball-screw nut 32. A space defined by the extension 4b and 4b and the
underside of the upper cover 4 is filled with sound absorbing material 70,
such as sponge.
A permanent magnet (not shown), for example, is secured to the underside of
the carriage 20. An proximity switch, such as a Hall effect element,
facing the permanent magnet, is mounted on the inner surface of the casing
body 2. The original position of the carriage 20 in the linear motion
axial direction is detected by the proximity switch and the permanent
magnet. The AC servo motor 40 is controlled by the detected original
position signal, thereby accurately positioning the linearly driven
carriage 20.
A contact position detector (not shown), such as a limit switch, which is
used for preventing an overrun of the carriage 20, may be provided at the
end of the casing 1. In this case, the lead wire of the limit switch may
be put in a groove 2A, formed in the outer surface of the casing body 2,
so as not interfere with other members.
In the linear motion actuator thus constructed, the casing 1 has a
substantially closed structure except for the slits S. These slits S are
closed by the seal band 60. With this construction, the linear motion
actuator is protected from dust.
The slit structures of the linear motion actuator will be described below.
Since the slit structures of the right and left slits S are substantially
the same, the slit structure of one of these slits will be described.
The pulleys 50 are provided at the four corners of the casing 1 (FIGS. 2
and 1). The pulley 50a at the upper corner of the motor bracket 6 is
provided at the location on the line extended from the slit S. The pulley
50b at the lower corner of the motor bracket 6 is provided right under the
pulley 50a. The pulley 50c at the upper corner of the end cover 5 is
provided at the location on the line extended from the slit S. The pulley
50d at the lower corner of the end cover 5 is provided right under the
pulley 50c.
The seal band 60 which is put on the four pulleys 50 is a flat sail cloth
band containing polyurethane. One end of the seal band 60 is fastened to
the stepped portion 24b formed at one end of the carriage 20, by means of
set screws 61. The other end of the seal band 60 is fastened to the
stepped portion 24b formed at the other end of the carriage 20, by means
of set screws 61. Thus, the seal band 60 forms a loop extending from one
end of the carriage 20 to the other end thereof through a route connecting
pulleys 50a, 50b, 50c, and 50d.
The side edges of the seal band 60 are inserted into the guide groove 3a of
the end face of the side cover 3 and the guide groove 4a of the end face
of the upper cover 4, respectively. With this structure, the sealing
effect by the seal band 60 is enhanced, and the seal band 60 is guided
without being shifted sideways. The lower portion of the loop of the seal
band 60, which ranges from the pulley 50b at the lower corner of the motor
bracket 6 to the pulley 50d at the lower corner of the end cover 5, pass
through a through-hole 7a located right under the guide rail 11, which is
one of the plurality of through-holes 7 longitudinally passing through the
casing body 2. A rectangular guide plate 63 is fastened to the location of
the middle of the loop of the seal band 60, viz., a position right under
the carriage 20 when the carriage passes the middle of the casing 1 when
viewed axially. A gap is present between each side of the guide plate 63
and the corresponding inner wall of the through-hole 7a, whereby the seal
band 60 is prevented from being shifted sideways.
After the carriage 20 is assembled to the sliders 12 of the linear guide
10, the ends of the seal band 60 are fastened to the stepped portions 24b
of the carriage 20, whereby forming the loop of the seal band 60.
Thereafter, the side covers 3 and the upper cover 4 are set to the casing
body.
A workpiece (not shown) as a driven member, is firmly secured by bolts onto
a pair of the driven member mounting portions 24a of the carriage 20,
which protrude above the upper cover 4 of the casing 1.
It is assumed now that the carriage 20 stops at a position close to the
motor bracket 6.
Under this condition, the AC servo motor 40 is forwardly turned. With the
forward turn of the driving device 40, the ball-screw shaft 31 of the
ball-and-screw mechanism 30 is forwardly turned. The rotary force of the
ball-screw shaft 31 is transmitted to the ball-screw nut 32 by the balls
33, which are inserted between the helical thread 31a of the ball-screw
shaft 31 and the helical thread 32a of the ball-screw nut 32. By the
rotary force, the ball-screw nut 32 moves axially, so that the carriage 20
secured to the ball-screw nut 32 moves also axially.
When the ball-screw nut 32 moves, the steel balls roll forward within the
ball threads, facing each other, of the ball-screw shaft 31 and the
ball-screw nut 32. Since the ball-and-screw mechanism 30 is of the end-cap
circulating type, the balls circulate in a manner that after reaching the
nut end, the balls moves through the curved path of the end cap 35 and the
return path of the nut body, and returns to the start position. If the
ball-and-screw mechanism of the tube circulating type, the balls roll one
or two and half turn through the helical path defined by the coupled
helical threads, and then are pulled into the ball circulating tube of the
nut. The balls obliquely ride over the lands of the ball-screw shaft 31
within the tube, and returns to the helical thread path. This circulation
of the balls is repeated.
Thus, a number of steel balls circulate through the helical thread path and
within the ball-screw nut 32, while rolling. Therefore, continuous
generation of noise is inevitable in the ball-screw nut 32 of the
ball-and-screw mechanism 30. The suppression of this noise will be
described later.
The carriage 20 is supported at both sides by the sliders 12 of the linear
guides 10. Accordingly, with the movement of the carriage 20, the sliders
12 move along the guide rails 11 of the linear guides 10. Thus, the
carriage 20 is guided along the guide rails 11, with the movement of the
sliders 12. In this way, the smooth movement of the carriage 20 is
guaranteed, and an exact linear movement of the workpiece attached to the
carriage 20 is secured.
When the sliders 12 move, a number of the steel round bodies 18 roll
forward within the ball rolling grooves 13 of the guide rails 11 and the
ball rolling grooves 16 of the sliders 12. The round bodies 18 are turned
back by way of the curved path provided at one end of each slider 12, pass
through the circulating paths 17 formed in the leg portions 15 of the
sliders 12, and reach the other ends of the sliders 12. The round bodies
18 are turned back again by way of curved paths of the other ends of the
sliders 12, and return to the coupled the ball rolling grooves 13 and 16.
In this way, a number of solid steel round bodies 18 circulates within the
sliders 12 while rolling. Accordingly, a continuous noise is generated
also in the slider 12 portions of the linear guides 10 when the linear
motion actuator is operating.
The noise suppression mechanism for suppressing the continuous noise will
be described below.
In the first embodiment, the sound absorbing material 70, mounted on the
underside of the upper cover 4, is used for suppressing the continuous
noise generated in the slider 12 portions of the linear guides 10 and the
ball-screw nut 32 portion of the ball-and-screw mechanism 30. Further,
noise suppression is ensured by sealing the slits S as the openings of the
closed casing 1 with the seal bands 60. It is noted that the sound
absorbing material 70 is disposed right above the ball-screw nut 32 where
noise generation tends to occur. Because of this feature, the noise
generated is effectively suppressed. A pair of extensions 4b and 4b,
shaped like L, elongating over the entire length of the lower surface of
the upper cover 4, are provided for supporting the sound absorbing
material 70. Provision of the extensions 4b and 4b increases the rigidity
of the upper cover 4.
The carriage 20 is driven by the driving device 40 through the
ball-and-screw mechanism 30, and moves axially in the casing 1 while being
guided by the linear guides 10. With the movement of the carriage, the
protruded portions 24 of the carriage, which bear the work and are
protruded from the surface of the upper cover 4, move axially within and
along the slits S. As the protruded portions 24 of the carriage move, the
looped seal bands 60 fastened at the ends to the protruded portions 24 are
also turned. When the carriage 20 moves to the right (FIG. 2), for
example, the seal bands 60 are turned back on the pulleys 50c and 50d,
disposed in this order in the carriage advancing direction. The seal bands
60 are turned back again on the pulleys 50b and 50a. In this way, the seal
bands 60 are turned clockwise in FIG. 2. With the turn of the seal bands
60, the guide plates 63 mounted on the lower parts of the seal bands 60
move in the direction opposite to the carriage advancing direction. The
distance the guide plates 63 move is equal to the stroke length of the
carriage 20. There is no fear that the guide plates 63 collide with the
end cover 5 and the motor bracket 6.
It is noted that the gap present between each the guide plates 63 and the
inner wall of the through-hole 7a associated therewith is very small.
Therefore, the looped seal bands 60 can be effectively prevented from
being shifted sideways.
Thus, the looped seal bands 60 turn in a considerably stable state with the
movement of the carriage 20, while at the same time seal the slits S,
which range within the moving range of the driven member mounting portions
24a of the carriage 20. The sealing is made in a manner that the side
edges of each seal band 60 are inserted into the guide groove 3a of the
end face of the side cover 3 and the guide groove 4a of the end face of
the upper cover 4. Extremely small gaps, shaped like U in cross section,
defined by the seal bands 60, the side covers 3, and the upper cover 4
connect the inside and the outside of the casing 1. The inner precise
parts of the linear motion actuator is reliably protected from fine
foreign matters, such as dust. Further, the seal bands 60, when turned,
are not shifted sideways. Furthermore, noise generated in the linear
guides 10 and the ball-and-screw mechanism 30 can be effectively confined
within the casing 1.
The linear motion actuator of the first embodiment is designed for the
transportation of large and heavy workpieces. To transport such a
workpiece at high speed and accurately to position it, a high rigidity is
required for the actuator. Particularly the carriage, which couples the
work with the linear guides, directly receives the load of the workpiece.
It is a very important component in determining the rigidity of the linear
motion actuator. In the first embodiment, special design efforts to
construct the structure to provide a high rigidity of the linear motion
actuator are made.
The first feature to obtain a high rigidity of the linear motion actuator
is the hollowed structure of the casing body 2 in which many through holes
7 are formed in the thick part of the bottom of the casing body 2. This
hollowed structure contributes to reduce the weight of the linear motion
actuator and to increase the rigidity thereof.
The second feature is that the driven member mounting portions 24a of the
carriage 20, which directly receive the load of the workpiece, are located
just above the guide rails 11 of the linear guides 10. With this feature,
the heavy workpiece placed on the driven member mounting portions 24a is
supported on the locations on the axial lines of the linear guides 10
where provide the most rigidity. The weight reduction by thinning the
carriage 20 and the substantial increase of the rigidity of the linear
motion actuator can both be achieved.
The third feature is that in the dust-proof structure for sealing the slits
S necessary for the movement of the carriage 20, which are formed in the
upper surface of the casing 1, the movable bands 60 are used by making
well use of the through-hole 7a formed in the casing body 2. Specifically,
the seal bands 60 are looped. One end of each looped seal band is fastened
to the carriage 20. With the movement of the carriage 20, the looped seal
bands 60 are circulated through the through-hole 7a. The structure of the
carriage 20 is much simpler than that of the conventional one. As a
result, a high rigidity of the carriage 20 is secured, and the size
reduction of thereof is realized.
A second embodiment of the linear motion actuator according to the present
invention will be described with reference to FIG. 5. The dust-proof
structure in the second embodiment is suitable for a linear motion
actuator for transporting a driven member of a relatively light weight.
A casing 1, having one piece construction consisting of the bottom portion,
side portions, and the upper portion, is formed by extrusion molding. A
slit S, axially extended, is formed in the upper portion. A shallow sunken
part 80, axially extended, is formed at the central part of the upper
surface of the bottom portion. The sunken part 80 serves as a path for the
seal band 60. A guide rail 11 is disposed on the surface of the bottom
portion of the casing 1. The guide rail 11 is U-shaped in cross section.
Ball rolling grooves 13, longitudinally extended, are formed in the inner
walls, facing each other, of the guide rail 11. The ball-screw nut 32 of a
ball-and-screw mechanism 30 is axially movably provided in the U-shaped
guide rail 11. In this case, the ball-screw nut 32 serves also as a slider
12 of the linear guide 10.
Ball rolling grooves (not shown) are formed in both sides of the ball-screw
nut 32, while confronting with the ball rolling grooves 13 of the guide
rail 11. The ball-screw nut 32 is engaged with the guide rail 11 through a
plurality of balls which roll along ball rolling paths formed by the ball
rolling grooves opposite to each other.
Ball circulating paths as through holes extending in parallel with the
respective ball rolling paths are formed in the thick parts of the right
and left sides of the ball-screw nut 32. End caps 32E are fastened to the
end faces of both ends of the ball-screw nut 32 when longitudinally
viewed, by means of bolts 32B, respectively. A curved groove is formed in
each end cap 32E. The curved grooves connect the ball rolling paths and
the ball circulating paths. The ball rolling paths, the ball circulating
paths, and the curved grooves cooperate to form a loop of the ball
circulating path. The ball-screw nut 32 is linearly moved while being
guided by the guide rail 11. At this time, a plurality of balls roll
forward within the looped ball circulating path.
A ball-screw shaft 31 is screwed into the ball-screw nut 32, with the balls
intervening therebetween. The ball-screw shaft 31 is rotatably supported
through the bearings (not shown) by the end cover and the motor bracket,
both are not shown, provided at the ends of the casing 1. The ball-screw
shaft 31 is driven by a drive motor, causing the ball-screw nut 32 to
linearly move in the axi | | |
