Information
-
Patent Grant
-
6241214
-
Patent Number
6,241,214
-
Date Filed
Monday, September 13, 199925 years ago
-
Date Issued
Tuesday, June 5, 200123 years ago
-
Inventors
-
Original Assignees
-
Examiners
Agents
- Dickstein Shapiro Morin & Oshinsky LLP
-
CPC
-
US Classifications
Field of Search
US
- 254 104
- 254 103
- 254 126
-
International Classifications
-
Abstract
To provide a structure supporting apparatus that enables an upper structure to be lifted up to a precise position with respect to a lower structure in a simple and reliable manner and also can be used as a supporting member as it is without fitting any stop members or equivalent, to provide improved workability. In a structure supporting apparatus in which an upper pressure-bearing member and a lower pressure-bearing member is moved relative to each other in the state of being laid one on another to vary the thickness of the upper pressure-bearing member and the lower pressure-bearing member in an overlaying direction, a driving device for driving the lower pressure-bearing member is so constructed that power input from a drive shaft can be transmitted to a feed screw through a reduction gear mechanism including intermediate gear elements.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates to a structure supporting apparatus and, more specifically, to a structure supporting apparatus interposed between an upper structure and a lower structure of a structure, such as a bridge and an express-highway, comprising the upper structure and the lower structure for supporting the upper structure.
2. Description of Background Art
A structure composed of an upper structure
1
and a lower structure
2
for supporting the upper structure
1
, such as, for example, a bridge and an express-highway, includes supporting members
3
which are interposed between the upper structure
1
and the lower structure
2
, as shown in
FIG. 1
, to surely transmit vertical load of the upper structure
1
to the lower structure
2
or absorb expansion of the upper structure
1
resulting from temperature change or horizontal swinging motion of the same.
The supporting members
3
become fatigued for many years of use and thus must be replaced with new ones after a set period of time. For this, there has been proposed a supporting apparatus disclosed by, for example, Japanese Laid-open Patent Publication No. Hei 7(1995)-166514 and shown in
FIGS. 10
to
12
.
As shown in
FIG. 10
, the supporting apparatus comprises an upper pressure-bearing member
5
having at its bottom surface a lower sliding surface
4
of a slant surface, a lower pressure-bearing member
7
laid over the upper pressure-bearing member
5
and having at its top surface an upper sliding surface
6
of a slant surface which is slidable over the lower sliding surface
4
of the upper pressure-bearing member
5
, and a hydraulic jack
8
for pulling the lower pressure-bearing member
7
to move it. In use, the supporting apparatus is first interposed between the upper structure
1
and the lower structure
2
in the state of the upper pressure-bearing member
5
and the lower pressure-bearing member
7
being displaced with each other in an axial direction. At that time, a tread
11
is interposed between the upper structure
1
and the upper pressure-bearing member
5
and also a base member
12
is interposed between the lower structure
2
and the lower pressure-bearing member
7
. The upper pressure-bearing member
5
, which has a projection
9
projecting from a bottom surface thereof, is laid so that the projection
9
can be inserted in a groove
10
formed in the upper pressure-bearing member
5
. Further, a reaction bearing member
13
is interposed between the upper pressure-bearing member
5
and the hydraulic jack
8
.
Subsequently, the hydraulic jack
8
is driven to pull the lower pressure-bearing member
7
toward the hydraulic jack
8
, as shown in FIG.
11
. The upper pressure-bearing member
5
is then pushed by the as-pulled lower pressure-bearing member
7
, but is not moved, because the upper pressure-bearing member
5
is received by the reaction bearing member
13
. Only the lower pressure-bearing member
7
is moved while the upper sliding surface
6
and the lower sliding surface
4
are in sliding engagement with each other. As a result of this, the thickness of the upper pressure-bearing member
5
and lower pressure-bearing member
7
in their overlaying direction becomes gradually increased. As a result of this, the supporting apparatus lifts up the upper structure
1
with respect to the lower structure
2
, while supporting the upper structure
1
thereon.
Then, after the upper structure
1
is raised up to a suitable position with respect to the lower structure
2
, stop members
14
are fitted into a space in the groove
10
in which the projection
9
is received, as shown in
FIG. 12
, to restrict relative movement between the upper pressure-bearing member
5
and the lower pressure-bearing member
7
, so as to keep the upper structure
1
in the suitable position with respect to the lower structure
2
.
This type of supporting apparatus enables the upper structure
1
to be lifted up in the state of being supported against the lower structure
2
and also can be used as the supporting member
3
as it is, thus having the advantage of permitting easy replacement of the supporting member
3
, even in a case where there is no working room for removing the existing supporting member
3
.
With this type of supporting apparatus, the upper structure
1
must be lifted up to a precise position with respect to the lower structure
2
and, accordingly, the lower pressure-bearing member
7
must be moved with accuracy. However, with the supporting apparatus disclosed by the JP Laid-Open Patent Publication No. Hei 7(1995)-166514 using the hydraulic jack
8
to move the lower pressure-bearing member
7
, in the event that for example a hose of the hydraulic jack
8
is damaged and hydraulic pressure is decreased, there can be produced the disadvantages that the lower pressure-bearing member
7
can not be moved precisely and that the upper structure
1
as lifted is lowered. Further, since the hydraulic pressure in the hydraulic jack
8
decreases over a period of time, it is necessary that after the upper structure
1
is raised up to a suitable position with respect to the lower structure
2
, the stop members
14
are fitted into the space in the groove
10
to restrict the relative movement between the upper pressure-bearing member
5
and the lower pressure-bearing member
7
. Thus, the known supporting apparatus has the disadvantages of taking many processes and troublesome works.
On the other hand, for example when a gear transmission mechanism or equivalent is used instead of the hydraulic jack
8
, the above-mentioned disadvantages caused by the decrease in hydraulic pressure may be avoided. But, since the gear transmission mechanism is, in general, not so high in the efficiency and also may cause the output power to vary with respect to the input power, it is hard to move the lower pressure-bearing member
7
with accuracy.
SUMMARY OF THE INVENTION
It is the object of the present invention to provide a structure supporting apparatus which is designed so that an upper structure can be lifted up to a precise position with respect to a lower structure in a simple and reliable manner and also can be used as a supporting member as it is without fitting any stop members or equivalent, to provide improved workability.
According to this invention, there is provided a structure supporting apparatus which comprises a first pressure-bearing member having a first sliding surface of a slant surface, a second pressure-bearing member laid on the first pressure-bearing member and having a second sliding surface of a slant surface slidably engaged with the first sliding surface, and a driving means for moving at least one of the first pressure-bearing member and the second pressure-bearing member and is so structured that the first sliding surface and the second sliding surface can be slid over each other by drive of the driving means, while the first pressure-bearing member and the second pressure-bearing member are moved relative to each other, whereby the thickness of the first pressure-bearing member and the second pressure-bearing member in an overlaying direction thereof can be varied, characterized in that the driving means includes an input shaft to which power from a power source is input, an output shaft mounted on the at least one of the first pressure-bearing member and the second pressure-bearing member, and a gear transmission mechanism that receives the power input from the input shaft to transmit it to the output shaft at a predetermined rotational ratio; that the gear transmission mechanism includes an input side gear provided on the input shaft, an output-side gear provided on the output shaft, and intermediate gear elements including intermediate gears engageable with at least the input-side gear and the output-side gear; and that the intermediate gear elements are provided between the input-side gear and the output-side gear.
With this construction, the power input from the input shaft is transmitted to the intermediate gears of the intermediate gear elements through the input-side gear and in turn the power transmitted to the intermediate gears is transmitted to the output shaft through the output-side gear. Then, the power transmitted to the output shaft drives at least one of the first pressure-bearing member and the second pressure-bearing member and thereby the first sliding surface and the second sliding surface are slid with each other, while the first pressure-bearing member and the second pressure-bearing member are moved relative to each other. As a result of this, the thickness of the first pressure-bearing member and the second pressure-bearing member in their overlaying direction varies.
According to this invention, since the power input from the input shaft is transmitted to the intermediate gears of the intermediate gear elements through the input-side gear and then is transmitted to the output shaft through the output-side gear, the input power can be output at a precise rotational ratio and with reliability. Hence, the first pressure-bearing member and/or the second pressure-bearing member on which the gear transmission mechanism is mounted can be moved with accuracy. Accordingly, for example, the upper structure can be lifted up to a precise position with respect to the lower structure.
With the gear transmission mechanism, damage that may be caused by using the hydraulic jack can be reduced, thus enabling the first pressure-bearing member and/or the second pressure-bearing member to be always moved with accuracy. Besides, for example, after the upper structure is raised up to a suitable position with respect to the lower structure, the inventive supporting apparatus can be used as the supporting member as it is without any stop members being fitted. Thus, improved workability can be produced.
According to this invention, it is preferable that the input shaft and the output shaft are aligned on the same axis.
With this construction, the power input from the input shaft is transmitted through the gear transmission mechanism to the output shaft arranged coaxially.
This construction that can bring the input shaft and the output shaft into axial alignment with each other can permit downsize of the gear transmission mechanism. Thus, improved capability of transmission and workability can be provided.
According to this invention, it is preferable that the intermediate gear elements are arranged in parallel around the axis on which the input shaft and the output shaft are aligned, and the intermediate gear elements are each composed of a first intermediate gear engageable with the input-side gear and a second intermediate gear engageable with the output-side gear, and the first intermediate gear and the second intermediate gear are aligned on the same axis in such a manner as to be non-rotatable thereto.
With this construction, the power input from the input shaft is transmitted through the input-side gear to the intermediate gear elements arranged in parallel around the axis on which the input shaft and the output shaft are aligned. In the intermediate gear elements, the power is transmitted to the first intermediate gears and second intermediate gears which are located on the concentric axes in such a manner as to be non-rotatable relative thereto. After that, the power is transmitted to the output shaft through the output-side gear.
With this construction, since the intermediate gear elements are so constructed that the first intermediate gears engageable with the input-side gear and the second intermediate gears engageable with the output-side gear are arranged on the concentric axes in such a manner as to be non-rotatable relative thereto and also the intermediate gear elements are arranged in parallel around the axis on which the input shaft and the output shaft are aligned, size reduction of the gear transmission mechanism can further be achieved and efficient power transmission can be achieved.
According to this invention, it is preferable that the intermediate gear elements include input-side gear elements located near the input shaft and arranged in parallel around the axis on which the input shift and the output shaft are aligned, a transfer gear element disposed between the input shaft and the output shaft and arranged on the axis on which the input shaft and the output shaft are aligned, and output-side gear elements located near the output shaft and arranged in parallel around the axis on which the input shaft and the output shaft are aligned; that the input-side gear elements include a first intermediate gear engageable with the input-side gear and a second intermediate gear engageable with the transfer gear element; that the transfer gear element includes a third intermediate gear engageable with the second intermediate gear and a fourth intermediate gear engageable with the output-side gear element; that the output-side gear elements include a fifth intermediate gear engageable with the fourth intermediate gear and a sixth intermediate gear engageable with the output-side gear; and that the first intermediate gear, the second intermediate gear, the fifth intermediate gear and the sixth intermediate gear are aligned on concentric axes; the first intermediate gear and the second intermediate gear are arranged in such a manner as to be non-rotatable relative to each other and the fifth intermediate gear and the sixth intermediate gear are arranged in such a manner as to be non-rotatable relative to each other.
With this construction, the power input from the input shaft is transmitted through the input-side gear to the input-side gear elements located near the input shaft and arranged in parallel. In the input-side gear elements, the power is transmitted to the first intermediate gears and the second intermediate gears which are arranged on concentric axes in such a manner as to be non-rotatable relative thereto. After that, the power is transmitted to the transfer gear element disposed between the input shaft and the output shaft. Then, the power is transmitted to the third intermediate gear and the fourth intermediate gear in the transfer gear elements and thereafter is transmitted to the output-side gear elements located near the output shaft and arranged in parallel. Then, the power is transmitted to the fifth intermediate gears and the sixth intermediate gears which are arranged on the concentric axes in such a manner as to be non-rotatable thereto in the output-side gear elements, respectively and thereafter is transmitted to the output shaft through the output-side gear.
With this construction, the intermediate gear elements are composed of the input-side gear elements, the transfer gear elements and output-side gear elements. In addition, the input-side gear elements are arranged near the input shaft and in parallel around the axis on which the input shaft and the output shaft are aligned and are composed of the first intermediate gears and the second intermediate gears arranged on the concentric axes in such a manner as to be non-rotatable relative thereto, and the output-side gear elements are arranged near the output shaft and in parallel around the axis on which the input shaft and the output shaft are aligned and are composed of the fifth intermediate gears and the sixth intermediate gears arranged on the concentric axes in such a manner as to be non-rotatable relative thereto. This construction can permit further size reduction of the gear transmission mechanism and also can achieve efficient power transmission. Besides, since the intermediate gear elements are structured to have more stages including the input-side gear elements, the transfer gear elements and the output-side gear elements, even when the torque of the input shaft is small, an increased output load can be output from the output shaft. Accordingly, for example, the upper structure can be lifted up to a precise position with respect to the lower structure readily and quickly by using a tool of small torque like an electric driver.
According to this invention, it is preferable that an overload protection mechanism is interposed in a transmission path of the gear transmission mechanism, for interrupting the transmission path when a load in excess of a rated load is applied.
With this construction, when a load in excess of a rated load is applied, the transmission path of the gear transmission mechanism is interrupted by the overload protection mechanism. Thus, damage of the apparatus due to the overload can be prevented and also can ensure the safety in working.
According to this invention, it is preferable that at least the components of the gear transmission mechanism consisting of the input-side gear, the output-side gear and gears included in the intermediate gear elements are coated with nickel-phosphorus plating.
With this nickel-phosphorus plating, part-to-part variations in coefficient of friction can be reduced. Thus, the power input from the input shaft can be transmitted to the output shaft with efficiency. Thus, the input power can be output at a more accurate rotational ratio and with further reliability.
According to this invention, it is preferable that fluorine components are mixed in the nickel-phosphorus plating, and a plating film in which fluorine components are eutectic dispersed in a matrix of nickel-phosphorus film is formed on the surfaces of the components.
The forming of the plating film in which fluorine components are eutectic dispersed in a matrix of nickel-phosphorus film can provide improvements of parts in wear resistance, sliding resistance and quiet. This can permit the power input from the input shaft to be transmitted to the output shaft with efficiency. Accordingly, the input power can be output at a more accurate rotational ratio and with further reliability.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1
is a front view showing an upper structure and a lower structure to which a supporting apparatus of one embodiment of the present invention is applied;
FIG. 2
is an exploded perspective view showing one embodiment of the supporting apparatus of the present invention;
FIG. 3
is an upper sectional view showing an inside structure of a driving device of the supporting apparatus of
FIG. 2
;
FIG. 4
is a side elevation view including a partly sectioned view of the supporting apparatus of
FIG. 2
which is in the state of use;
FIG. 5
is a side elevation view including a partly sectioned view of the supporting apparatus of
FIG. 2
which is in the state of use;
FIG. 6
is a side elevation view including a partly sectioned view of the supporting apparatus of
FIG. 2
which is in the state of use;
FIG. 7
is a diagram showing a characteristic of “Input Torque From Shaft—Output Load By Jack” of the driving device of the supporting apparatus of
FIG. 2
;
FIG. 8
is an upper sectional view showing an inside structure of a driving device of another embodiment different from the driving device of
FIG. 2
;
FIG. 9
is a diagram showing a characteristic of “Input Torque From Shaft—Output Load By Jack” of the supporting apparatus having the driving device of
FIG. 8
;
FIG. 10
is a side elevation view of a conventional type of supporting apparatus which is in the state of use;
FIG. 11
is a side elevation view of the conventional type of supporting apparatus which is in the state of use; and
FIG. 12
is a side elevation view of the conventional type of supporting apparatus which is in the state of use.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
FIG. 2
is an exploded perspective view showing one embodiment of the structure supporting apparatus of the present invention. In
FIG. 2
, the supporting apparatus
21
is used for replacing a supporting member
3
interposed between an upper structure
1
and a lower structure
2
for supporting the upper structure
1
of a structure, such as, for example, a bridge or an express-highway, with new one and is designed to be used as the supporting member
3
as it is, as shown in FIG.
1
.
In
FIG. 2
, the supporting apparatus
21
is composed of an upper pressure-bearing member
22
as a first pressure-bearing member, a lower pressure-bearing member
23
as a second pressure-bearing member, a driving device
24
as a driving means for driving the lower pressure-bearing member
23
, a tread
25
, a base member
26
and a reaction bearing member
27
.
The upper pressure-bearing member
22
, which is made of lightweight and hard synthetic resin material and is rectangular in plan configuration, is formed into a generally wedge-like plate form in side configuration, having a horizontally extending top surface
28
and a bottom surface
31
obliquely extending along its lengthwise direction so that a front side surface
29
is made larger in thickness than a rear side surface
30
. The bottom surface
31
of the slant surface operates as the first sliding surface. A U-like groove
32
extending from side to side along its longitudinal direction and opening downward is formed in a center of the upper pressure-bearing member
22
in a direction perpendicular to its lengthwise direction or in a widthwise direction. The groove
32
is so formed that a top surface
40
of the groove
32
can be made parallel with the top surface
28
of the upper pressure-bearing member
22
so that the interval between the top surface
40
and the top surface
28
of the upper pressure-bearing member
22
can be kept unchanged along the entire length. A recessed portion
33
, rectangular in plan configuration, for the tread
25
to be fitted therein, is formed in the top surface
28
of the upper pressure-bearing member
22
. To be more specific, the upper pressure-bearing member
22
is formed of laminate material of special fibers impregnated with phenol resin, and a U-like bearing plate
34
, made of iron and steel material, for bearing thereon the reaction bearing member
27
, is fitted in the front side surface
29
so as to be flush therewith.
The lower pressure-bearing member
23
, which is made of lightweight and hard synthetic resin material, as in the case with the upper pressure-bearing member
22
, and is rectangular in plan configuration, is formed into a generally wedge-like plate form in side configuration, having a horizontally extending bottom surface
35
and a top surface
36
obliquely extending along its lengthwise direction so that a rear side surface
37
is made larger in thickness than a front side surface
38
. The top surface
36
of the slant surface operates as the second sliding surface. The slanting angle of the top surface
36
is made substantially equal to the slanting angle of the bottom surface
31
of the upper pressure-bearing member
22
. A strip projection
39
, extending from side to side along its longitudinal direction and projecting upwards, is integrally formed in a center part of the lower pressure-bearing member
23
in a direction perpendicular to its lengthwise direction or in a widthwise direction. The strip projection
39
is of rectangular in section to fit in the groove
32
of the upper pressure-bearing member
22
and is so formed that a top surface
41
of the strip projection
39
(which is indicated by a different reference numeral in
FIG. 2
in order to discriminate between the top surface
36
of the lower pressure-bearing member
23
and the top surface
41
of the strip projection
39
) can be made parallel with the bottom surface
35
of the lower pressure-bearing member
23
so that the height between the bottom surface
35
and the top surface
41
can be kept unchanged along the entire length. A fitting hole
43
of an angled tube-like form for fitting therein a retaining member
42
of the driving device
24
as discussed later is formed in the strip projection
39
at a lengthwise midpoint thereof so that the top surface
41
can be opened. An insertion hole
45
for a feed screw
44
serving as an output shaft of the driving device
24
as discussed later to pass therethrough is bored between a center part of the front side surface
38
of the strip projection
39
and the fitting hole
43
along a lengthwise direction of the strip projection
39
. To be more specific, the lower pressure-bearing member
23
is formed of laminate material of special fibers impregnated with phenol resin, as is the case with the upper pressure-bearing member
22
, and a bearing plate
46
, made of iron and steel material, for bearing thereon the bottom surface
31
of the upper pressure-bearing member
22
in a slidable manner, is provided on the surface
36
of the lower pressure-bearing member
23
on both sides thereof facing across the strip projection
39
.
The tread
25
is made of hard rubber material and is rectangular in plan configuration which is fittable in the recessed portion
33
formed in the top surface
28
of the upper pressure-bearing member
22
. A bearing plate
47
, made of iron and steel material, for bearing thereon the upper structure
1
, is fitted in the top surface of the tread
25
.
The driving device
24
is provided with a drive shaft
52
serving as an input shaft to which the power from a power source is input; the retaining member
42
fitted in the fitting hole
43
formed in the strip projection
39
of the lower pressure-bearing member
23
; the feed screw
44
threadedly engaged on the retaining member
42
and serving as an output shaft; and a reduction gear mechanism
53
housed in a gear box
50
and serving as a gear transmission mechanism for receiving the power input from the drive shaft
52
and transmitting the input power to the feed screw
44
at a predetermined rotational ratio. The retaining member
42
is made of iron and steel material and is formed into a prismatic form fittable into the fitting hole
43
, and a threaded hole
54
is formed in a center part of the retaining member to extend therethrough in the thickness direction from the front.
The gear box
50
is a rectangular box made of iron and steel material and has, at a center part of the front wall
73
, an aperture opening to permit the drive shaft
52
to pass through, as shown in FIG.
3
. Provided in the aperture is a ring-like drive shaft supporting member
55
having a front insertion hole
58
for the drive shaft
52
to be passed through and supported therein. The gear box
50
has, at a center part of the rear wall
56
, a rear insertion hole
57
for the feed screw
44
to pass through. The front insertion hole
58
in the drive shaft supporting member
55
and the rear insertion hole
57
in the rear wall
56
are so formed as to be aligned with each other on the same axis. The gear box
50
is supported by four stay bolts
78
,
79
(only two stay bolts are shown in
FIG. 3
) connecting between the front wall
73
and the rear wall
56
.
As shown in
FIG. 3
, the feed screw
44
is threadedly engaged in the threaded hole
54
in the retaining member
42
fitted in the fitting hole
43
at one end portion thereof and is supported at the other end portion thereof in the rear wall
56
of the gear box
50
in a rotatable manner via a bearing metal
59
, passing through the rear insertion hole
57
. On the other hand, the drive shaft
52
mounts a handle
60
on one end portion thereof in a detachable manner and is supported at the other end portion thereof by the drive shaft supporting member
55
in a rotatable manner via a bearing metal
61
, passing through the front insertion hole
58
. Also, the drive shaft
52
has an end portion which has a smaller diameter than the feed screw
44
and is received in a recess formed in an end portion of the feed screw
44
in a rotatable manner via a bearing metal
82
. Thus, the drive shaft
52
is brought into alignment with the feed screw
44
on the same axis. The axis is indicated by reference numeral
66
in FIG.
3
.
The reduction gear mechanism
53
is composed of an input-side gear
63
, an output-side gear
62
and two intermediate gear elements
64
,
65
. The input-side gear
63
is formed at the end portion of the drive shaft
52
extending through the front insertion hole
58
, so as to be integral with the drive shaft
52
, in such a manner that the center of rotation can be formed by the axis of the drive shaft
52
. The output-side gear
62
is splined to the end portion of the feed screw
44
passing through the rear insertion hole
57
in such a manner that the center of rotation can be formed by the axis of the feed screw
44
. The two intermediate gear elements
64
,
65
are arranged in parallel with an axis
66
on which the drive shaft
52
and the feed screw
44
are aligned, with being shifted to each other at
180
degree across the axis
66
. In other words, the reduction gear mechanism
53
is composed of two gear shafts
67
,
68
arranged in parallel about the axis
66
; and the first intermediate gears
69
,
70
and the second intermediate gears
71
,
72
which are formed on the two gear shafts
67
,
68
, respectively.
The two gear shafts
67
,
68
are rotatably supported by the front wall
73
and the rear wall
56
of the gear box
50
via bearing metals
74
,
75
and
76
,
77
, respectively. The first intermediate gears
69
,
70
are integrally formed on one side end portion of the gear shafts
67
,
68
so that the centers of rotation can be formed by the axes of the gear shafts
67
,
68
and are so arranged as to be engaged with the input-side gear
63
. The second intermediate gears
71
,
72
, which are disposed adjoining to the first intermediate gears
69
,
70
in the axial direction of the gear shafts
67
,
68
, are integrally formed on the gear shafts
67
,
68
so that the centers of rotation can be formed by the axes of the gear shafts
67
,
68
and are so arranged as to be engaged with the output-side gear
62
. Thus, the first intermediate gears
69
,
70
and the second intermediate gears
71
,
72
are housed in the gear box
50
such as to be axially aligned with and non-rotatable relative to each other.
As shown in
FIG. 2
, the base member
26
is made of iron and steel material and is formed into a rectangular plate-like form in plan configuration so that the lower pressure-bearing member
23
can be born on the top surface
48
in a slidable manner. The base member
26
is provided, on its top surface
48
, with guide portions
49
projecting therefrom for guiding the lower pressure-bearing member
23
to be moved in the axial direction of the lower pressure-bearing member
23
only. The guide portions
49
are composed of a pair of strip projections extending in parallel in the longitudinal direction of the base member
26
and are arranged at positions corresponding to both widthwise ends of the lower pressure-bearing member
23
.
The reaction bearing member
27
is a member for bearing thereon the upper pressure-bearing member
22
pulled toward the driving device
24
by the drive of the driving device
24
and applying the reaction force to the upper pressure-bearing member
22
so as to permit the slide between the upper pressure-bearing member
22
and the lower pressure-bearing member
23
. The reaction bearing member
27
is made of iron and steel material and is formed in rectangular form in plan configuration so that it can be interposed between the bearing plate
34
in the front side surface
29
of the upper pressure-bearing member
22
and the gear box
50
of the driving device
24
. The reaction bearing member
27
has an insertion hole
80
formed at the center portion and a stepped portion
51
formed in the rear side surface at a lower end portion thereof so as to be engaged with the end of the base member
26
.
Next, the usage of the illustrated supporting apparatus
21
thus constructed will be described with reference to
FIGS. 4 through 6
.
FIG. 4
shows the state of the supporting apparatus
21
being set between the upper structure
1
and the lower structure
2
. The setting of the supporting apparatus
21
is performed by the following steps. First, the base member
26
is fixed to the lower structure
2
by use of bolts or equivalent, for example. If the base member
26
is failed to be placed in a horizontal position, the base member
26
must be level before the fixing by interposing suitable plates or equivalent therewith. Then, the lower pressure-bearing member
23
is put on the top surface
48
of the base member
26
within the range of the guide portions
49
. The retaining member
42
is fitted in the fitting hole
43
formed in the strip projection
39
of the lower pressure-bearing member
23
across the mount of the lower pressure-bearing member
23
. Then, after having been passed through the insertion hole
80
in the reaction bearing member
27
, one end portion of the feed screw
44
is passed through the insertion hole
45
formed in the strip projection
39
of the lower pressure-bearing member
23
, to be threadedly secured into the threaded hole
54
. Thus, the driving device
24
is fixedly mounted on the lower pressure-bearing member
23
. Then, the upper pressure-bearing member
22
is laid on the lower pressure-bearing member
23
in such a manner that the groove
32
of the upper pressure-bearing member
22
is fitted with the strip projection
39
of the lower pressure-bearing member
23
. The fit of the groove
32
with the strip projection
39
enables the upper pressure-bearing member
22
to slide over the lower pressure-bearing member
23
only in the direction of the strip projection
39
extending longitudinally. This brings the bottom surface
31
of the upper pressure-bearing member
22
and the top surface
36
of the lower pressure-bearing member
23
into sliding contact with each other. Then, the tread
25
is received with a press-fit into the recessed portion
33
formed in the top surface
28
of the upper pressure-bearing member
22
and thereby the setting of the supporting apparatus
21
is completed. The steps of a series of works for the setting do not matter. For example, all parts may be assembled together in advance to enable the setting at a stroke. In the setting, the upper pressure-bearing member
22
and the lower pressure-bearing member
23
are overlaid with being shifted to each other in the sliding direction in such a manner that a small gap is defined between the upper structure
1
and the tread
25
or the upper structure
1
and the tread
25
are brought into contact without being pressed with each other.
Then, the handle
60
is mounted on the drive shaft
52
and is turned clockwise (in the direction indicated by an arrow
81
) with human power as a power source. The power input from the drive shaft
52
is transmitted through the input-side gear
63
to the two intermediate gear elements
64
,
65
arranged in parallel around the axis
66
on which the drive shaft
52
and the feed screw
44
are aligned. In the intermediate gear elements
64
,
65
, the power is transmitted to the second intermediate gears
71
,
72
from the first intermediate gears
69
,
70
which are located on the axes of the gear shafts
67
,
68
in such a manner as to be non-rotatable relative thereto. After that, the power is transmitted from the intermediate gear elements
64
,
65
to the feed screw
44
through the output-side gear
62
.
When the power is transmitted to the feed screw
44
at a predetermined rotational ratio through the drive shaft
52
and the reduction gear mechanism
53
by the turning of the handle
60
, the retaining member
42
threadedly engaged with the feed screw
44
is screwed forward. As a result of this, the lower pressure-bearing member
23
is pulled toward the driving device
24
. When the lower pressure-bearing member
23
is thus moved, the upper pressure-bearing member
22
is pushed by the lower pressure-bearing member
23
but is not moved because it is born by the reaction bearing member
27
. As a result of this, while the upper pressure-bearing member
22
and the lower pressure-bearing member
23
are moved relatively to each other, the bottom surface
31
of the upper pressure-bearing member
22
and the top surface
36
of the lower pressure-bearing member
23
are slid over each other. As this relative movement occurs, the thickness of the upper pressure-bearing member
22
and lower pressure-bearing member
23
in their overlaying direction becomes gradually increased. This produces the result that the supporting apparatus
21
supports the upper structure
1
with respect to the lower structure
2
, while lifting up the upper structure
1
. Thus, when the turning of the handle
60
is stopped after the upper structure
1
is raised up to a suitable position with respect to the lower structure
2
, as shown in
FIG. 5
, the relative movement between the upper pressure-bearing member
22
and the lower pressure-bearing member
23
is restricted and thereby the upper structure
1
is kept in the suitable position with respect to the lower structure
2
.
Accordingly, the supporting apparatus
21
thus constructed can supports the upper structure
1
with respect to the lower structure
2
, while lifting up the upper structure
1
and can be used as the supporting member
3
as it is. This can permit easy replacement of the supporting member
3
, even in a case where there is no working room for removing the existing supporting member
3
. It is to be noted that after the upper structure
1
is supported in the suitable position with respect to the lower structure
2
, the handle
60
may be removed and for example a rotation regulating member
83
for regulating the rotation of the drive shaft
52
may be mounted on the drive shaft
52
, as shown in
FIG. 6
, when necessary.
According to the supporting apparatus
21
of the illustrated embodied form, since the power input from the single drive shaft
52
is transmitted to the two intermediate gear elements
69
,
70
through the input-side gear
63
and is in turn transmitted to the single feed screw
44
through the output side gear
62
, the input power can be output at a precise rotational ratio and
22
with reliability. Hence, the lower pressure-bearing member
23
can be moved with accuracy and, accordingly, the upper structure
1
can be lifted up to a precise position with respect to the lower structure
2
. Shown in
FIG. 7
is a characteristic of “input torque from shaft—output load by jack” showing the relation between the input torque from shaft (the torque input from the drive shaft
52
) and the output load by jack (the load that can be lifted up by the upper pressure-bearing member
22
) obtained when the driving device
24
of the illustrated embodiment is used. It will be understood in
FIG. 7
that the output load by jack correlates with the input torque from shaft with a high degree of accuracy, so that when the driving device
24
of the illustrated embodiment is used, the lift-up load can be afforded with accuracy and reliability with reference to the rotation of the drive shaft
52
.
Also, since the driving device
24
of the illustrated embodiment adopts the reduction gear mechanism
53
, the possible damage that can be caused by using the hydraulic jack can be reduced, thus enabling the lower pressure-bearing member
23
to be always moved with accuracy. Besides, after the upper structure
1
is raised up to a suitable position with respect to the lower structure
2
, the inventive supporting apparatus can be used as the supporting member
3
as it is, without any stop members being fitted. Thus, improved workability can be produced.
In addition, since the drive shaft
52
and the feed screw
44
are arranged on the same axis
66
, improved capability of transmission and workability resulting from the size reduction of the reduction gear mechanism
53
are provided. Further, since the intermediate gear elements
64
,
65
are so constructed that the first intermediate gears
69
,
70
and the second intermediate gears
71
,
72
are arranged on the concentric axes in such a manner as to be non-rotatable relative thereto and also the intermediate gear elements
64
,
65
are arranged in parallel around the axis
66
on which the drive shaft
52
and the feed screw
44
are aligned, efficient power transmission resulting from further size reduction can be achieved.
In the illustrated embodiment, the sliding members and engaging members in the driving device
24
, i.e., the output-side gear
63
, the feed screw
44
, the drive shaft
52
on which the input-side gear
63
is integrally formed, and the gear shafts
67
,
68
on which the first intermediate gears
69
,
70
and the second intermediate gears
71
,
72
are integrally formed, are coated with nickel-phosphorus plating. The nickel-phosphorus plating is conducted by, for example, the step that the parts to be plated are immersed in plating solution containing nickel and phosphorus to be coated with 2-100 μm, preferably 5-50 μm, of plating layers by means of electroless plating and thereafter the coated parts are heat-treated at 300-1,000° C., preferably 300-400° C., for 1-3 hours, when necessary.
With this nickel-phosphorus plating, part-to-part variations in coefficient of friction can be reduced. Thus, the power input from the drive shaft
52
can be transmitted to the feed screw
44
with efficiency. Thus, the input power can be output at a more accurate rotational ratio and with further reliability. The phosphorus content in the coating of the electroless plating is preferably 1-15 weight %, for example.
In this nickel-phosphorus plating given to the parts of the illustrated embodiment, fluorine components including particles of fluorine-contained resin and particles of graphite fluoride, such as polytetrafluoroethylene, tetrafluoroethylene/hexafluoropropylene copolymerizate and tetrafluoroethylene/perfluoroalkyl vinyl ether copolymerizate, are further mixed in the plating solution containing nickel and phosphorus, and an electroless plating film in which fluorine components are eutectic dispersed in a matrix of nickel-phosphorus film is formed on the surfaces of the parts. The eutectoid of the fluorine components can provide improvements of parts in wear resistance, sliding resistance and quiet. This can permit the power input from the drive shaft
52
to be transmitted to the feed screw
44
with efficiency. Accordingly, the input power can be output at a more accurate rotational ratio and with further reliability. The fluorine components in the electroless plating film is considered to be preferably 1-40 weight percent of eutectoid, further preferably 2-10 weight percent of eutectoid, of the whole film. In this plating, hardening and tempering may be performed, when necessary. It is preferable that the plating is conducted so that the electroless plating film can have the hardness of 300-1,000, further preferably 400-800 in Vickers hardness.
Shown in
FIG. 8
is an upper sectional view showing an inside structure of a driving device
100
of another embodiment different from the above-illustrated driving device
24
.
In
FIG. 8
, the driving device
100
is provided with the drive shaft
52
, the retaining member
42
(not shown in
FIG. 8
) and the feed screw
44
, as in the case of the above-illustrated driving device
24
, but the reduction gear mechanism
53
and the gear box
50
housing it therein are different in structure from those of the above-illustrated driving device
24
.
Specifically, the gear box
50
is a rectangular box made of iron and steel material and has, at a center part of the front wall
101
, an aperture opening for the drive shaft
52
to pass through. Provided in the aperture is a ring-like drive shaft supporting member
103
having a front insertion hole
102
for the drive shaft
52
to be passed through and supported therein. The gear box
50
has, at a center part of the rear wall
104
, a rear insertion hole
105
for the feed screw
44
to pass through. The front insertion hole
102
in the drive shaft supporting member
103
is axially aligned with the rear insertion hole
105
in the rear wall
104
. The gear box
50
has, at a generally center part thereof between the front wall
101
and the rear wall
104
, a holder plate
106
, arranged in parallel with the front wall
101
and the rear wall
104
, for holding gear shafts
113
,
114
,
145
and
146
as mentioned later. The gear box
50
is supported by four stay bolts not shown.
The feed screw
44
is supported in the rear wall
104
of the gear box
50
in a rotatable manner via a bearing metal
107
, passing through the rear insertion hole
105
. The drive shaft
52
is supported by the drive shaft supporting member
103
and the front wall
101
in a rotatable manner via a bearing metal
108
, passing through the front insertion hole
102
. Thus, the drive shaft
52
and the feed screw
44
are aligned with each other on the same axis. The axis is indicated by reference numeral
66
in FIG.
8
.
The reduction gear mechanism
53
is provided with the input-side gear
63
, the output-side gear
62
, two input-side gear elements
109
,
110
, a transfer gear element
111
and two output-side gear elements
142
,
143
.
The two input-side gear elements
109
,
110
are located near the drive shaft
52
and arranged in parallel with the axis
66
on which the drive shaft
52
and the feed screw
44
are aligned, with being shifted to each other at
180
degree across the axis
66
. In other words, the reduction gear mechanism
53
is composed of two gear shafts
113
,
114
arranged in parallel about the axis
66
and the first intermediate gears
115
,
116
and the second intermediate gears
117
,
118
which are formed on the two gear shafts
113
,
114
, respectively.
The two gear shafts
113
,
114
are rotatably supported by the front wall
101
of the gear box
50
and the holder plate
106
via bearing metals
119
,
120
, and
121
,
122
. The first intermediate gears
115
,
116
are integrally formed on the gear shafts
113
,
114
at one side end portions thereof so that the centers of rotation can be formed by the axes of the gear shafts
113
,
114
and are so arranged as to be engaged with the input-side gear
63
. The second intermediate gears
117
,
118
, which are disposed adjoining to the first intermediate gears
115
,
116
in the axial direction of the gear shafts
113
,
114
, are integrally formed with the gear shafts
113
,
114
so that the centers of rotation can be formed by the axes of the gear shafts
113
,
114
and are so arranged as to be engaged with the third intermediate gear
123
of the transfer gear element
111
as mentioned below. Thus, the first intermediate gears
115
,
116
and the second intermediate gears
117
,
118
are housed in the gear box
50
such as to be axially aligned with and non-rotatable relative to each other.
The transfer gear element
111
is composed of a transfer shaft
141
disposed between the drive shaft
52
and the feed screw
44
and arranged on the axis
66
on which the drive shaft
52
and the feed screw
44
are aligned and; an overload protection mechanism
124
arranged around the transfer shaft
141
; a third intermediate gear
123
arranged around the overload protection mechanism
124
; and a fourth intermediate gear
125
formed around the transfer shaft
141
.
The transfer shaft
141
is rotatably supported on the holder plate
106
of the gear box
50
via the bearing metal
126
. The transfer shaft
141
is formed to have a smaller diameter than the feed screw
44
, so that its one side end portion is received in a recessed portion in the end of the feed screw
44
in such a manner as to be rotatable via the bearing metal
127
and its other side end portion is abutted to the drive shaft
52
in such a manner as to be rotatable via the bearing metal
128
.
The overload protection mechanism
124
is provided with a hub member
129
arranged around the drive shaft
52
, a first lining plate
130
, a second lining plate
131
and a load setting mechanism
132
for setting a rated load. On the hub member
129
are integrally formed a flange portion
133
; a large-diameter cylindrical portion
134
projecting from the flange portion
133
toward the front wall
101
; and a small-diameter cylindrical portion
135
further projecting from the large-diameter cylindrical portion
134
toward the front wall
101
and formed to have a smaller diameter than the large-diameter cylindrical portion
134
. The hub member
129
is splined to the transfer shaft
141
in such a manner as to be non-rotatable relative thereto and axially movable. The small-diameter cylindrical portion
135
has, at an end portion thereof, a recessed portion, in which the bearing metal
128
interposed between the small-diameter cylindrical portion
135
and the drive shaft
54
is received to hold the hub member
129
on the drive shaft
54
via the bearing metal
128
. A female thread is formed around the outer surface of the small-diameter cylindrical portion
135
.
The third intermediate gear
123
, the first lining plate
130
and the second lining plate
131
are rotatably supported on the large-diameter cylindrical portion
134
of the hub member
129
, with the third intermediate gear
123
held between the first lining plate
130
and the second lining plate
131
.
The load setting mechanism
132
is composed of a lining keep plate
136
; a belleville spring
137
; a locking member
138
; and a tightening nut
139
. The lining keep plate
136
is rotatably supported on the small-diameter cylindrical portion
135
of the hub member
129
in the state of abutting with the first lining plate
130
. For biasing the lining keep plate
136
toward the first lining plate
130
, the belleville spring
137
is supported on the small-diameter cylindrical portion
135
of the hub member
129
in the state of abutting with the lining keep plate
136
. For adjusting the biasing force of the belleville spring
137
, the tightening nut
139
is threadedly engaged with the small-diameter cylindrical portion
135
of the hub member
129
such that the belleville spring
137
can be pressed through the locking member
138
.
Thus, when the tightening nut
139
is screwed forward along the small-diameter cylindrical portion
135
of the hub member
129
, the belleville spring
137
strongly presses the first lining plate
130
, the third intermediate gear
123
and the second lining plate
131
through the lining keep plate
136
. As a result of this, the third intermediate gear
123
is pressed by the first lining plate
130
and the second lining plate
131
and, accordingly, even when an increased load is applied on the feed screw
44
side, the third intermediate gear
123
can be prevented from being slipped against the first lining plate
130
and the second lining plate
131
to avoid interruption of the transmission of power between the drive shaft
54
and the feed screw
44
, thus permitting a rated load to be set high.
On the other hand, as the tightening nut
139
is screwed backward along the small-diameter cylindrical portion
135
of the hub member
129
, the pressing force to the first lining plate
130
, the third intermediate gear
123
and the second lining plate
131
between the tightening nut
139
and the flange portion
133
of the hub member
129
is reduced. When an increased load is applied on the feed screw
44
side, the third intermediate gear
123
is slipped against the first lining plate
130
and the second lining plate
131
to interrupt the transmission of power between the drive shaft
54
and the feed screw
44
, thus permitting a rated load to be set low.
The fourth intermediate gear
125
, which adjoins the overload protection mechanism
124
across the holder plate
106
in the axial direction of the transfer shaft
141
, is integrally formed on the transfer shaft
141
so that the center of rotation can be formed by the axis of the transfer shaft
141
and is so arranged as to be engaged with fifth intermediate gears
147
,
148
of the output-side gear elements
142
,
143
.
The two output-side gear elements
142
,
143
are located near the feed screw
44
and arranged in parallel with the axis
66
on which the drive shaft
52
and the feed screw
44
are aligned, with being shifted to each other at
180
degree across the axis
66
. In other words, the output-side gear elements
142
,
143
are composed of two gear shafts
145
,
146
arranged in parallel about the axis
66
; and the fifth intermediate gears
147
,
148
and the sixth intermediate gears
149
,
150
which are formed on the two gear shafts
145
,
146
, respectively.
The two gear shafts
145
,
146
are rotatably supported by the rear wall
104
of the gear box
50
and the holder plate
106
via bearing metals
151
,
152
, and
153
,
154
, respectively. The fifth intermediate gears
147
,
148
are integrally formed on the gear shafts
145
,
146
at one side end portions thereof such that the centers of rotation can be formed by the axes of the gear shafts
145
,
146
and are so arranged as to be engaged with the fourth intermediate gear
125
. The sixth intermediate gears
149
,
150
, which are disposed adjoining to the fifth intermediate gears
147
,
148
in the axial direction of the gear shafts
145
,
146
, are integrally formed on the gear shafts
145
,
146
so that the centers of rotation can be formed by the axes of the gear shafts
145
,
146
and are so arranged as to be engaged with the output-side gear
62
. Thus, the fifth intermediate gears
147
,
148
and the sixth intermediate gears
149
,
150
are housed in the gear box
50
such as to be axially aligned with and non-rotatable relative to each other.
To raise the upper structure
1
up to a suitable position with respect to the lower structure
2
by the driving device
100
thus constructed, turning of the drive shaft
52
is required, as is the case of the above. The power input from the drive shaft
52
is then transmitted through the input-side gear
63
to the two intermediate gear elements
109
,
110
located near the drive shaft
52
and arranged in parallel around the axis
66
on which the drive shaft
52
and the feed screw
44
are aligned. In the input-side gear elements
109
,
110
, the power is transmitted to the second intermediate gears
117
,
118
from the first intermediate gears
115
,
116
which are located on the axes of the gear shafts
113
,
114
in such a manner as to be non-rotatable relative thereto. After that, the power is transmitted from the second intermediate gears
117
,
118
of the input-side gear elements
109
,
110
to the third intermediate gear
123
of the transfer gear element
111
.
Then, the power transmitted to the third intermediate gear
123
of the transfer gear element
111
is transmitted from the third intermediate gear
123
to the fourth intermediate gear
125
, when the load is not in excess of the preset load of the overload protection mechanism
124
, such that the third intermediate gear
123
pressed and held by the first lining plate
130
and the second lining plate
131
is allowed to rotate together with the hub member
129
, the transfer shaft
141
splined to the hub member
129
, and the fourth intermediate gear
125
integrally formed on the transfer shaft
141
. After that, the power is transmitted from the fourth intermediate gear
125
of the transfer gear element
111
to the fifth intermediate gears
147
,
148
of the two output-side gear elements
142
,
143
located near the feed screw
44
and arranged in parallel around the axis
66
on which the drive shaft
52
and the feed screw
44
are aligned.
If the load is in excess of the preset load of the overload protection mechanism
124
, then the third intermediate gear
123
is slid against the first lining plate
130
and the second lining plate
131
, as aforementioned, so that the power is not transmitted from the third intermediate gear
123
to the fourth intermediate gear
125
. Thus, when a load in excess of a rated load is applied, the transmission path of the reduction gear mechanism
53
is interrupted by the overload protection mechanism
124
, so that damage of the apparatus due to the overload can be prevented and also can ensure the safety in working.
Then, the power transmitted to the fifth intermediate gears
147
,
148
of the two output-side gear elements
142
,
143
is transmitted to the sixth intermediate gears
149
,
150
from the fifth intermediate gears
147
,
148
which are arranged on the axes of the gear shafts
145
,
146
in such a manner as to be non-rotatable thereto in the output-side gear elements
142
,
143
, respectively. Then, the power is transmitted from the sixth intermediate gears
149
,
150
of the output-side gear elements
142
,
143
to the feed screw
44
through the output-side gear element
62
.
Then, in the illustrated driving device
100
, since the power input from the single drive shaft
52
is transmitted the two input-side gear elements
109
,
110
through the input-side gear
63
and then to the two output-side gear elements
142
,
143
through the transfer gear element
111
having the overload protection mechanism
124
and further to the single feed screw
44
through the output-side gear
62
, the input power can be output at an accurate rotational ratio and with reliability. Besides, since the reduction gear mechanism
53
is designed to have more stages than the aforementioned driving device
24
, even when the torque of the drive shaft
52
is small, an increased output load can be output from the feed screw
44
.
Shown in
FIG. 9
is a characteristic of “input torque from shaft—output load by jack” showing the relation between the input torque from shaft (the torque input from the drive shaft
52
) and the output load by jack (the load that can be lifted up by the upper pressure-bearing member
22
) obtained when the driving device
100
of the illustrated embodiment is used. It will be understood in
FIG. 9
that the output load by jack correlates with the input torque from shaft with a high degree of accuracy, so that, when the driving device
100
of the illustrated embodiment is used, the lift-up load can be afforded with accuracy and reliability with reference to the rotation of the drive shaft
52
and also even when the torque of the drive shaft
52
is small, an increased output load can be output from the feed screw
44
. Accordingly, the upper structure
1
can be lifted up with respect to the lower structure
2
readily and quickly by using a tool of small torque like an electric driver
155
, as indicated by a phantom line in
FIG. 8
, for example.
Also, since the diving device
100
of the illustrated embodiment has the go features that the drive shaft
52
, the transfer gear element
111
and the feed screw
44
are aligned on the same axis
66
; that the two input-side gear elements
109
,
110
are arranged in parallel around the axis
66
of the drive shaft
52
and feed screw
44
, such that the first intermediate gears
115
,
116
and the second intermediate gears
117
,
118
are arranged on the concentric axes in such a manner as to be non-rotatable relative thereto; and that the two output-side gear elements
142
,
143
are arranged in parallel around the axis
66
of the drive shaft
52
and feed screw
44
, such that the fifth intermediate gears
147
,
148
and the sixth intermediate gears
149
,
150
are arranged on the concentric axes in such a manner as to be non-rotatable relative thereto, a further improved efficiency in the power transmission originating from the further size reduction can be achieved.
For permitting the connection of the electric driver
155
to the drive shaft
52
, as mentioned above, for example a fitting portion fittingly engageable with a drive shaft of the electric driver
155
may be provided in the drive shaft
52
to permit the direct connection or a coupling may be interposed therebetween to permit the indirect connection.
To prevent reverse rotation of the feed screw
44
during the drive of the driving device
100
, in other words, to prevent height reduction of the upper structure
1
, the overload protection mechanism
124
may be provided with an one-way mechanism.
In the driving device
100
of the illustrated embodiment as well, as is the case with the aforementioned driving device
24
, the sliding members and engaging members, i.e., the output-side gear
63
, the feed screw
44
, the drive shaft
52
on which the input-side gear
63
is integrally formed, the gear shafts
113
,
114
on which the first intermediate gears
115
,
116
and the second intermediate gears
117
,
118
are integrally formed, the third intermediate shaft
123
, the transfer shaft
141
on which the fourth intermediate shaft
125
is integrally formed, and the gear shafts
145
,
146
on which the fifth intermediate gears
147
,
148
and the sixth intermediate gears
149
,
150
are integrally formed may be plated with nickel-phosphorus or with the components in which fluorine components are further mixed in the nickel-phosphorus.
According to the present invention, no particular limitation is imposed on the number of gears of the reduction gear mechanism. For example, a single gear may be used for the intermediate gear element, but five or more gears are of preferable though it may be properly selected in accordance with the purpose and the use. As for the rotational ratio between the input shaft and the output shaft, a desired gear ratio may be suitably selected in accordance with the purpose and the use. Further, a planetary gear mechanism may be adopted as the gear transmission mechanism.
While the structure supporting apparatus of the illustrated embodiments is used in such as manner as to be interposed between the upper structure
1
and the lower structure
2
, it may be used in such a manner as to be interposed between a right-side structure and a left-side structure. Also, the structure supporting apparatus may be simply used as a jack, rather than the supporting member
3
. While the driving device
24
or the driving device
100
is mounted on the lower pressure-bearing member
23
in the illustrated embodiments, it may be mounted on the upper pressure-bearing member
22
or on both of the upper pressure-bearing member
22
and the lower pressure-bearing member
23
.
While the illustrative embodiment of the present invention is provided in the above description, such is for illustrative purpose only and it is not to be construed restrictively. Modification and variation of the present invention that will be obvious to those skilled in the art is to be covered in the accompanying claims.
Claims
- 1. A structure supporting apparatus which comprises a first pressure-bearing member having a first sliding surface of a slant surface, a second pressure-bearing member laid on the first pressure-bearing member and having a second sliding surface of a slant surface slidably engaged with the first sliding surface, and a driving means for moving at least one of the first pressure-bearing member and the second pressure-bearing member and is so structured that the first sliding surface and the second sliding surface can be slid over each other by drive of said driving means, while the first pressure-bearing member and the second pressure-bearing member are moved relative to each other, whereby the thickness of the first pressure-bearing member and the second pressure-bearing member in an overlaying direction thereof can be varied, characterized in:that said driving means includes an input shaft to which power from a power source is input, an output shaft mounted on said at least one of the first pressure-bearing member and the second pressure-bearing member, said input shaft and said output shaft being aligned on the same axis, and a gear transmission mechanism that receives the power input from said input shaft to transmit it to said output shaft at a predetermined rotational ratio; that said gear transmission mechanism includes an input-side gear provided on said input shaft, an output-side gear provided on said output shaft, and intermediate gear elements including intermediate gears engageable with at least said input-side gear and said output-side gear; and that said intermediate gear elements are provided between said input-side gear and said output-side gear and arranged in parallel around the axis on which said input shaft and said output shaft are aligned, and said intermediate gear elements are each composed of a first intermediate gear engageable with said input-side gear and a second intermediate gear engageable with said output-side gear, and said first intermediate gear and said second intermediate gear are aligned on the same axis in such a manner as to be non-rotatable thereto.
- 2. A structure supporting apparatus which comprises a first pressure-bearing member having a first sliding surface of a slant surface, a second pressure-bearing member laid on the first pressure-bearing member and having a second sliding surface of a slant surface slidably engaged with the first sliding surface, and a driving means for moving at least one of the first pressure-bearing member and the second pressure-bearing member and is so structured that the first sliding surface and the second sliding surface can be slid over each other by drive of said driving means, while the first pressure-bearing member and the second pressure-bearing member are moved relative to each other, whereby the thickness of the first pressure-bearing member and the second pressure-bearing member in an overlaying direction thereof can be varied, characterized in:that said driving means includes an input shaft to which power from a power source is input, an output shaft mounted on said at least one of the first pressure-bearing member and the second pressure-bearing member, said input shaft and said output shaft being aligned on the same axis, and a gear transmission mechanism that receives the power input from said input shaft to transmit it to said output shaft at a predetermined rotational ratio; that said gear transmission mechanism includes an input-side gear provided on said input shaft, an output-side gear provided on said output shaft, and intermediate gear elements including intermediate gears engageable with at least said input-side gear and said output-side gear; and wherein said intermediate gear elements are provided between said input-side gear and said output-side gear and include input-side gear elements located near said input shaft and arranged in parallel around said axis on which said input shaft and said output shaft are aligned, a transfer gear element disposed between said input shaft and said output shaft and arranged on the axis on which said input shaft and said output shaft are aligned, and output-side gear elements located near said output shaft and arranged in parallel around the axis on which said input shaft and said output shaft are aligned; wherein said input-side gear elements include a first intermediate gear engageable with said input-side gear and a second intermediate gear engageable with said transfer gear element; wherein said transfer gear element includes a third intermediate gear engageable with the second intermediate gear and a fourth intermediate gear engageable with said output-side gear element; wherein said out-put side gear elements include a fifth intermediate gear engageable with the fourth intermediate gear and a sixth intermediate gear engageable with said output-side gear; and wherein the first intermediate gear, the second intermediate gear, the fifth intermediate gear, and the sixth intermediate gear are aligned on concentric axes; the first intermediate gear and the second intermediate gear are arranged in such a manner as to be non-rotatable relative to each other; and the fifth intermediate gear and the sixth intermediate gear are arranged in such a manner as to be non-rotatable relative to each other.
- 3. A structure supporting apparatus which comprises a first pressure-bearing member having a first sliding surface of a slant surface, a second pressure-bearing member laid on the first pressure-bearing member and having a second sliding surface of a slant surface slidably engaged with the first sliding surface, and a driving means for moving at least one of the first pressure-bearing member and the second pressure-bearing member and is so structured that the first sliding surface and the second sliding surface can be slid over each other by drive of said driving means, while the first pressure-bearing member and the second pressure-bearing member are moved relative to each other, whereby the thickness of the first pressure-bearing member and the second pressure-bearing member in an overlaying direction thereof can be varied, characterized in:that said driving means includes an input shaft to which power from a power source is input, and output shaft mounted on said at least one of the first pressure-bearing member and the second pressure-bearing member, and a gear transmission mechanism that receives the power input from said input shaft to transmit it to said output shaft at a predetermined rotational ratio; that said gear transmission mechanism includes an input-side gear provided on said input shaft, and output-side gear provided on said output shaft, and intermediate gear elements including intermediate gears engageable with at least said input-side gear and said output-side gear; said intermediate gear elements being provided between said input-side gear and said output-side gear, and an overload protection mechanism interposed in a transmission path of said gear transmission mechanism, for interrupting the transmission path when a load in excess of a rated load is applied.
- 4. A structure supporting apparatus according to claim 1, wherein at least the components of said gear transmission mechanism consisting of said input-side gear, said output-side gear and gears included in said intermediate gear elements are coated with nickel-phosphorus plating.
- 5. A structure supporting apparatus according to claim 4, wherein fluorine components are mixed in the nickel-phosphorus plating, and a plating film in which fluorine components are eutectic dispersed in a matrix of nickel-phosphorus film is formed on the surfaces of the components.
Priority Claims (1)
Number |
Date |
Country |
Kind |
10-264243 |
Sep 1998 |
JP |
|
US Referenced Citations (3)
Number |
Name |
Date |
Kind |
3244401 |
Ilmura |
Apr 1966 |
|
4559986 |
Svensson et al. |
Dec 1985 |
|
5781830 |
Gaylord et al. |
Jul 1998 |
|