Information
-
Patent Grant
-
6331010
-
Patent Number
6,331,010
-
Date Filed
Wednesday, July 22, 199826 years ago
-
Date Issued
Tuesday, December 18, 200122 years ago
-
Inventors
-
Original Assignees
-
Examiners
- Dickson; Paul N.
- Klebe; Gerald
Agents
- Woodcock Washburn Kurtz Mackiewicz & Norris LLP
-
CPC
-
US Classifications
Field of Search
US
- 403 122
- 403 123
- 403 124
- 403 128
- 403 140
- 403 135
- 403 143
- 403 142
- 403 141
- 280 6154
- 280 616
- 280 124159
- 280 12416
- 280 615
- 280 124112
- 267 6416
- 267 6417
-
International Classifications
-
Abstract
An industrial vehicle has a frame and an axle swingalbly connected with the frame, wherein a cylinder interposed between the frame and the axle selectively extends and retracts so as to absorb a swinging motion of the axle. The cylinder is coupled to the frame and the axle in a rotatable manner within a plane intersecting an axis of a center about which the axle swings.
Description
BACKGROUND OF THE INVENTION
The present invention relates to a structure for supporting cylinders, which are employed in vehicles such as forkifts and arranged between axles and body frames to restrict the movement of the axles.
Forklifts having rear axles that are supported pivotally with respect to its body frame to permit tilting, or roll, of the forklift are known in the prior art (e.g., Japanese Unexamined Patent Publication No. 58-183307). In such a forklift, a hydralic cylinder is arranged between the body frame and the axle to restrict the pivoting of the axle with respect to the body frame. The hydraulic cylinder locks the axle and restricts tilting of the forklift to maintain stability. For example, the tilting of the forklift is restricted when the forklift carries heavy loads, holds loads at high positions, or turns to change directions at high traveling speeds.
The hydraulic cylinder may be connected to the body frame and to the rear axle. In such case, a bracket having a connecting shaft, which extends in the longitudinal direction of the forklift (the direction of the roll axis), is fixed to the body frame. The hydraulic cylinder has a cylindrical housing. One end of the housing is secured to an anchor. The anchor is pivotally connected to the connecting shaft by means of a bearing such that the hydraulic cylinder is pivotal with respect to the body frame about the connecting shaft. A piston rod extending from the other end of the housing is connected to the rear axle such that the piston rod is pivotal. That is, like the housing of the hydraulic cylinder, the piston is pivotal about an axis that extends in the longitudinal direction of the forklift. Accordingly, the hydraulic cylinder is pivoted relative to the body frame and the rear axle, a pair of axes that extend in the direction of the roll axis.
The rear axle is assembled as a unit, or an assembly, before being connected to the body frame. The dimensional tolerances allowed for the components constituting the rear axle assembly may offset the position of the rear axle relative to the body frame from the ideal location in the longitudinal direction of the forklift. Furthermore, parts connecting the rear axle to the body frame may become loose during use of the forklift. This may also offset the relative position of the rear axle and the body frame. Such conditions would apply excessive force on the connecting shaft, the anchor, the bracket, and other parts of the hydraulic cylinder.
These problems may be solved by a structure such as that shown in FIG.
5
. In a similar manner to the structure of the Japanese publication, a bracket
70
fixed to a body frame
75
has two support plates
72
to support a connecting shaft
71
. A hydraulic cylinder
77
secured to a rear axle
76
is connected to the connecting shaft
71
with a bearing
74
. The structure of
FIG. 5
differs from the structure of the Japanese publication in that the distance between the support plates
72
is longer and that the connecting shaft
71
is longer than the diameter of the anchor
73
. This permits the anchor
73
to move in the axial direction of the connecting shaft
71
, or longitudinal direction of the vehicle. Thus, if the position of the rear axle
71
relative to the body frame
75
is offset longitudinally from the ideal location, the movement of the anchor
73
with respect to the connecting shaft
71
compensates for the offset distance. This prevents excessive force from acting on the bracket
70
, the anchor
73
, and other parts, while permitting the hydraulic cylinder
77
to pivot about a pair of longitudinally extending axes.
In the structure of
FIG. 5
, the hydraulic cylinder
77
is moved with its anchor
73
connected to the long connecting shaft
71
. Thus, when the rear axle
76
is pivoted with respect to the body frame
75
, a bending force is applied to the connecting shaft
71
by the anchor
73
. The bending force may deform the connecting shaft
71
. Therefore, the dimensions of the connecting shaft
71
and the bracket
70
must be enlarged to withstand the bending force. This increases the space required by the bracket
70
.
SUMMARY OF THE INVENTION
Accordingly, it is an objective of the present invention to provide a cylinder supporting structure that prevents the application of excessive force on parts used to support the cylinder without enlarging the dimensions of the supporting structure.
To achieve the above objective, the present invention provides an industrial vehicle having a frame and an axle swingably connected with the frame. The vehicle includes a center shaft of the swinging motion of the axle. The center shaft has an axis. The frame is connected with the axle by the center shaft. The axle swings about the center shaft. A cylinder is interposed between the frame and the axle. The cylinder is arranged to selectively extend and retract so as to absorb the swinging motion of the axle. A coupling device couples the cylinder with the frame and the axle. The cylinder is rotatable within a plane intersecting the axis of the central shaft.
Other aspects and advantages of the present invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.
BRIEF DESCRIPTION OF THE DRAWINGS
The features of the present invention that are believed to be novel are set forth with particularity in the appended claims. The invention, together with objects and advantages thereof, may best be understood by reference to the following description of the presently preferred embodiments together with the accompanying drawings in which:
FIG. 1
is a schematic side view, partially in cross-section, showing a cylinder supporting structure according to the present invention, as seen in a direction normal to the longitudinal direction of the vehicle;
FIG. 2
is a diagrammatic rear view showing the body frame and the rear axle of
FIG. 1
;
FIG. 3
is a rear view, partially in cross-section, showing the hydraulic cylinder of
FIG. 1
, as seen in the direction of the longitudinal axis of the vehicle;
FIG. 4
is a schematic rear view, partially in cross-section, showing a further embodiment of a cylinder supporting structure according to the present invention; and
FIG. 5
is a schematic side view, partially in cross-section, showing a prior art cylinder supporting structure, as seen in a direction normal to the longitudinal direction of the vehicle.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
A cylinder supporting structure according to the present invention will now be described with reference to
FIGS. 1
to
3
. The supporting structure is employed in industrial vehicles such as a forklift.
FIG. 2
is a schematic view showing the rear view of a forklift. As shown in the drawing, the forklift has a body frame
1
. A rear axle
2
is arranged at the rear lower section of the forklift. The rear axle
2
is supported such that it is pivotal about a center pin
3
in the roll direction of the forklift. In other words, the rear axle
2
moves relatively to the body frame
1
in a plane extending normal to the longitudinal axis of the vehicle. An elastic member
4
for dampening the impact produced by the pivoting of the rear axle
2
is provided between the body frame
1
and the rear axle
2
. Wheels
5
, which are steered to change the direction of the forklift, are mounted on each end of the rear axle
2
.
A multiple action type hydraulic cylinder
6
is arranged between the body frame
1
and the rear axle
2
. As shown in
FIG. 3
, the cylinder
6
includes a housing
7
, which accommodates a piston
8
. The piston
8
defines a lower chamber Ri and an upper chamber R
2
in the housing
7
. A piston rod
9
is fixed to the piston
8
. As shown in
FIG. 1
, the piston rod
9
is connected to a bracket
10
, which is fixed to the rear axle
2
. An end piece
11
is provided at the upper end of the housing
7
. The end piece
11
is connected to a bracket
12
, which is fixed to the body frame
1
.
As shown in
FIG. 2
, the lower chamber R
1
is connected to an electromagnetic control valve
14
through a passage
13
a,
while the upper chamber R
2
is connected to the control valve
14
through a passage
13
b.
The control valve
14
is further connected to an accumulator
15
. The control valve
14
is normally closed. Therefore, when the control valve
14
is de-excited, the control valve
14
is shifted to a disconnected position
14
a.
At the disconnected position
14
a,
movement of hydraulic oil between the lower and upper chambers R
1
, R
2
is prohibited. The control valve
14
is shifted to a connected position
14
b
when excited. At the connected position
14
b,
hydraulic oil is permitted to move between the lower and upper chambers R
1
, R
2
.
A controller
16
is electrically connected to the control valve
14
. When the forklift engine (not shown) is running, the controller
16
continuously excites the control valve
14
. However, if certain conditions are satisfied, the controller
16
de-excites the control valve
14
.
As shown in
FIG. 1
, the bracket
12
fixed to the body frame
1
has two support plates
18
,
19
. An upper connecting shaft
20
extending parallel to the longitudinal axis (the roll axis) of the forklift is supported by the two support plates
18
,
19
. A threaded portion
20
a
is defined on one end of the connecting shaft
20
. A nut
23
is engaged with the threaded portion
20
a
to fasten the connecting shaft
20
to the bracket
12
. A washer
22
is held between the support plate
18
and the nut
23
. Another washer
21
is held between the support plate
19
and the connecting shaft
20
.
Two identical collars
24
are fitted to the connecting shaft
20
between the support plates
18
,
19
. Each collar
24
has a large diameter portion
25
and a small diameter portion
26
. Each large diameter portion
25
is located on the outer side of the collar
24
adjacent to the associated support plate
18
,
19
. A spacer
27
is fitted on each large diameter portion
25
. Each spacer
27
contacts the inner wall of the associated support plate
18
,
19
.
A male bushing
28
is fitted on the small diameter portions
26
of the two collars
24
. That is, the male bushing
28
is held between the large diameter portion
25
of the collars
24
and between the support plates
18
,
19
. The male bushing
28
has a convex surface
28
a
and is made of a sintered metal, in which lubricating oil is impregnated.
An upper anchor
17
is defined at the upper portion of the end piece
11
. The upper anchor
17
has a bore
29
through which the connecting shaft
20
is inserted. A large diameter portion
30
and a small diameter portion
31
are defined in the support bore
29
. A female bushing
32
is fitted in the large diameter portion
30
and abuts against the wall, or step, formed between the large and small diameter portions
30
,
31
. The abutment of the female bushing
32
against the wall determines the position of the female bushing
32
. In the same manner as the male bushing
28
, the female bushing
32
is made of a sintered metal, in which lubricating oil is impregnated, and has a concave surface
32
a.
The concave surface
32
a
slides against the convex surface
28
a
of the male bushing
28
.
The end piece
11
is connected to the connecting shaft:
20
by engaging the male bushing
28
with the female bushing
32
such that the convex surface
28
a
comes into spherical surface contact with the concave surface
32
a.
The engagement between the male and female bushings
28
,
32
permits the upper anchor
17
to pivot relative to the connecting shaft
20
when the end piece
11
and the bracket
12
are connected to each other. In other words, the angle defined between the axis of the bore
29
and the axis of the connecting shaft
20
can be changed arbitrarily in accordance with the pivoting of the hydraulic cylinder
6
. The male and female bushings
28
,
32
are commercially available and sold in sets. Furthermore, the male and female bushings
28
,
32
define a universal joint.
The bracket
10
fixed to the rear axle
2
also has two support plates
34
,
35
. A lower connecting shaft
36
extending parallel to the longitudinal axis of the forklift is supported by the support plates
34
,
35
. A bearing portion
37
is defined at the axially middle part of the connecting shaft
36
. The bearing portion
37
has a curved surface
37
a.
A flange
38
extends radially and integrally from one end of the connecting shaft
36
. A bolt
39
fastens the connecting shaft
36
to the bracket
10
with the flange
38
engaged with the support plate
35
. The other end of the connecting shaft
36
projects from the support plate
34
. A cotter pin
48
is inserted radially through the connecting shaft
36
to keep the connecting shaft
36
held in the bracket
10
.
A spacer
40
is fitted on the connecting shaft
36
at each side of the bearing portion
37
. Each spacer
40
contacts the inner wall of the associated support plate
34
,
35
. An oil conduit
41
extends through the connecting shaft
36
from its flanged end to the curved surface
37
a
of the bearing portion
37
. An oil supplying device (not shown) delivers lubricating oil to the oil conduit
41
.
A lower anchor
42
is defined on the end of the piston rod
9
projecting from the cylinder housing
7
. The lower anchor
42
includes a bore
43
through which the connecting shaft
36
is inserted. A small diameter portion
44
is defined at the axially middle section of the bore
43
, while a large diameter portion
45
is defined at each end of the bore
43
. A bearing sleeve
46
is fitted into the small diameter portion
44
. The inner wall of the bearing sleeve
46
defines a slide surface
46
a.
The lower anchor
42
is connected to the connecting shaft
36
by engaging the bearing portion
37
with the bearing sleeve
46
such that the curved surface
37
a
slides against the slide surface
46
a.
The engagement between the bearing portion
37
and the bearing sleeve
46
permits the lower anchor
42
to pivot relative to the lower connecting shaft
36
. In other words, the angle defined between the axis of the bore
43
and the axis of the lower connecting shaft
36
can be changed arbitrarily in accordance with the pivoting of the hydraulic cylinder
6
. A seal
47
is arranged in each large diameter portion
45
to seal the space formed between the curved surface
37
a
and the slide surface
46
a.
The seal
47
may be made of synthetic rubber. The connecting shaft
36
and the bearing sleeve
46
define a universal joint.
Accordingly, the hydraulic cylinder
6
is supported between the body frame
1
and the rear axle
2
by two universal joints such that the cylinder
6
is pivotal about each joint in a plane that intersects the roll axis of the vehicle.
As shown in
FIG. 3
, the housing
7
of the hydraulic cylinder
6
has a lower opening closed by a rod piece
50
and a higher opening closed by a head piece
51
.
A guide rod
52
is fixed to the upper end of the piston
8
in the housing
7
, as viewed in FIG.
3
. The cross-sectional area of the guide rod
52
is equal to that of the piston rod
9
. The piston rod
9
has an upper end that extends through the piston
8
and into the upper chamber R
2
. A threaded section
9
a is defined on this end. The other end of the piston rod
9
extends through the rod piece
50
and out of the housing
7
. The guide rod
52
has a lower end located in the upper chamber R
2
. A threaded bore
52
a
is defined in this end. The threaded bore
52
a
is fastened to the threaded section
9
a
of the piston rod
9
. Accordingly, the piston rod
9
and the guide rod
52
are fastened to each other with the piston
8
held in between. In the hydraulic cylinder
6
, the pressure-receiving area of the upper end of the piston
8
is equal to that of the lower end of the piston
8
. In other words, their axially projected areas are the same. Also, the cross-sectional areas of the chambers R
1
, R
2
are the same.
The head piece
51
has a support bore
51
a
to slidably accommodate the upper end of the guide rod
52
. The end piece
11
has a retaining bore
11
a
for retaining the upper end of the guide rod
52
. The guide rod
52
moves axially in the retaining bore
11
a.
When assembling the rear axle
2
to the body frame
1
, the machining tolerances allowed for each component and the assembling tolerances allowed for the assembled components may offset the position of the rear axle
2
relative to the body frame
1
from the desirable position in the longitudinal direction of the forklift, or in a direction parallel to the roll axis. In such case, if the hydraulic cylinder
6
is connected to the bracket
12
of the body frame
1
and to the bracket
10
of the rear axle
2
, the hydraulic cylinder
6
will be tilted in a vertical plane that is parallel to the roll axis as shown in FIG.
1
. That is, the upper and lower ends of the hydraulic cylinder
6
will be pivoted about horizontal axes that are normal to the roll axis. Furthermore, if the position of the rear axle
2
relative to the body frame
1
is offset from the ideal position in the lateral direction of the forklift, the hydraulic cylinder can also be tilted in a vertical plane, that is normal to the roll axis.
In there is lateral offset and if the rear axle
2
is pivoted relative to the body frame
1
, the lower anchor
42
pivots about the connecting shaft
36
as the slide surface
46
a
of the bearing sleeve
46
slides against the curved surface
37
a
of the bearing portion
37
while the axis of the bore
43
pivots relative to the axis of the connecting shaft
36
. Simultaneously, the end piece
11
is pivoted about the connecting shaft
20
as the convex surface
28
a
of the male bushing
28
slides against the concave surface
32
a
of the female bushing
32
while the axis of the bore
29
pivots relative to the axis of the connecting shaft
20
.
Accordingly, the pivoting of the rear axle
2
relative to the body frame
1
permits the brackets
10
,
12
to pivot in two parallel planes, respectively, that are each perpendicular to the roll axis if the brackets
10
,
12
are offset from each other in the direction parallel of the rolling axis. The piston rod
9
is projected from or retracted into the hydraulic cylinder
6
in accordance with the pivoting of the rear axle
2
relative to the body frame
1
.
Since the pressure-receiving area of the upper end of the piston
8
is equal to that of the lower end of the piston
8
, and the cross-sectional area of the upper chamber R
2
is the same as that of the lower chamber R
1
, the amount of hydraulic oil discharged from one of the chambers R
1
R
2
is equal to that sent into the other chamber R
1
, R
2
during actuation of the hydraulic cylinder
6
. Therefore, the piston
8
moves in the same manner whether the piston rod
9
projects out of or retracts into the hydraulic cylinder
6
. This permits smooth pivoting of the rear axle
2
relative to the body frame
1
.
When the controller
16
de-excites the electromagnetic control valve
14
, the control valve
14
is shifted from the connected position
14
b
to the disconnected position
14
a.
This prohibits the movement of hydraulic oil between the lower and upper chambers R
1
, R
2
in the hydraulic cylinder
6
and locks the hydraulic cylinder
6
. Accordingly, the hydraulic cylinder
6
prohibits pivoting of the rear axle
2
relative to the body frame
1
.
The preferred and illustrated embodiment of the cylinder supporting structure has the advantages described below.
(a) The rear axle
2
is pivotal relative to the body frame
1
in the roll direction of the forklift. The universal joints (the joints defined by the bushings
28
,
32
and by the connecting shaft
36
and the bearing sleeve
46
) further support the hydraulic cylinder
6
such that the cylinder
6
is permitted to pivot in a vertical plane intersecting the rolling axis. Accordingly, if the positions of the joint between the cylinder
6
and the body frame
1
and the joint between the cylinder
6
and the rear axle
2
are offset from the ideal location in the longitudinal direction of the forklift, the rear axle
2
is pivoted relative to the body frame
1
while the cylinder
6
pivoted in a plane that is parallel to the rolling axis. This structure prevents the application of excessive force to the brackets
10
,
12
, the anchors
17
,
42
, and other parts.
Furthermore, a mechanism for connecting the brackets
10
,
12
with the associated anchors
17
,
42
of the hydraulic cylinder
6
to permit relative movement therebetween in the longitudinal direction of the vehicle, like the vehicle of
FIG. 5
, becomes unnecessary. Thus, the brackets
10
,
12
need not be enlarged to support such connecting mechanisms.
(b) The connecting shaft
20
, which extends in the longitudinal direction of the forklift, is supported by the body frame bracket
12
with the male bushing
28
fitted on the connecting shaft
20
. The female bushing
32
is fitted into the bore
29
of the upper anchor
17
such that the concave surface
32
a
of the female bushing
32
engages the convex surface
28
a
of the male bushing
28
. Thus, the upper anchor
17
of the hydraulic cylinder
6
is connected to the connecting shaft
20
of the bracket
12
such that the axis of the bore
29
is permitted to pivot to an arbitrary angle relative to the axis of the connecting shaft
20
. In this state, the bushings
28
,
32
are in spherical surface contact with each other. Accordingly, the force produced when the rear axle
2
pivots relative to the body frame
1
is applied to the hydraulic cylinder
6
over a wide area. This enhances the durability of the bushings
28
,
32
. Furthermore, the bushings
28
,
32
are easily obtained since they are commercially available.
(c) The connecting shaft
36
, which extends in the longitudinal direction of the forklift, is supported by the rear axle bracket
10
. The lower anchor
42
of the hydraulic cylinder
6
is connected to the connecting shaft
36
with the cylindrical slide surface
46
a
of the bearing sleeve
46
engaged with the curved surface
37
a
defined on the bearing portion
37
of the connecting shaft
36
. Thus, the lower. anchor
42
is connected to the bracket
10
such that the axis of the bearing sleeve
46
is permitted to pivot to an arbitrary angle relative to the axis of the connecting shaft
36
. Accordingly, production costs are saved by supporting the hydraulic cylinder
6
with the connecting shaft
36
and the bearing sleeve
46
.
(d) In the hydraulic cylinder
6
, the pressure-receiving area of the upper end of the piston
8
is equal to that of the lower end of the piston
8
. Also, the cross-sectional area of the upper chamber R
2
is the same as that of the lower chamber R
1
. Accordingly, the amount of hydraulic oil discharged from one of the chambers R
1
, R
2
is equal to that sent into the other chamber R
1
, R
2
during actuation of the hydraulic cylinder
6
. Therefore, the hydraulic cylinder
6
operates smoothly and allows smooth pivoting of the rear axle
2
.
(e) The preferred embodiment according to the present invention is applied to the hydraulic cylinder
6
employed in a forklift that restricts the pivoting of the rear axle
2
relative to the body frame
1
. This structure prevents excessive force from being applied to the brackets
10
,
12
, the anchors
17
,
42
, and other parts. Furthermore, this cylinder supporting structure compensates for the offset distance of the rear axle
2
with respect to the body frame
1
in either the longitudinal or the lateral direction of the vehicle.
It should be apparent to those skilled in the art that the present invention may be embodied in many other specific forms without departing from the spirit or scope of the invention.
In the preferred and illustrated embodiment, the present invention is applied to a vehicle having only one cylinder for restricting the movement of the axle. However, there are vehicles that require two cylinders to restrict the movement of the axle. In such vehicles, the present invention may be applied to each cylinder.
The male bushing
28
having the convex surface
28
a
and the female bushing
32
having the concave surface
32
a
may be employed to connect the hydraulic cylinder
6
to the rear axle
2
. On the other hand, the connecting shaft
36
and the bearing sleeve
46
may be employed to connect the hydraulic cylinder
6
to the body frame
1
. In other words, the hydraulic cylinder may be inverted from the position illustrated.
The connecting shafts
20
,
36
need not extend parallel to the longitudinal axis of the vehicle. For example, the connecting shafts
20
,
36
may be inclined with respect to the longitudinal axis. This would also prevent the application of excessive force on parts used to support the cylinder
6
, while compensating for the offset distance of the rear axle
2
relative to the body frame
1
without increasing the amount of occupied space.
The male and female bushings
28
,
32
need not be made of sintered metal. For example, the bushings
28
,
32
may be made of a synthetic resin that has a self-lubricating property and superior wear resistance property.
An oil conduit may be formed extending through the connecting shaft
20
and the collars
24
to supply lubricating oil to the convex and concave surfaces
28
a,
32
a
of the bushings
28
,
32
.
The electromagnetic control valve
14
may be normally opened.
As shown in
FIG. 4
, the hydraulic cylinder
6
may be connected to the body frame
1
or the rear axle
2
by employing a ball joint
55
having a spherical socket
53
and a joint
56
having a spherical surface
54
. The engagement of the spherical cavity
53
with the spherical surface
54
would permit the hydraulic cylinder to pivot in any direction.
The application of the present invention is not limited to forklifts. For example, the present invention may be applied to other types of industrial vehicles such as shovel loaders.
In addition to the hydraulic cylinder
6
, the present invention may be applied to other cylinders that dampen impacts.
The present invention may be applied to other types of cylinders used in industrial vehicles. For example, the present invention may be applied to suspending cylinders, vertical motion dampening cylinders, and vertical motion restricting cylinders.
The present invention may also be applied to cylinders operated by liquid pressure and gas pressure (e.g., pneumatic pressure) instead of hydraulic pressure.
The application of the present invention is not limited to industrial vehicles. For example, the present invention may also be applied to any type of industrial machinery that employs cylinders connected to two members that move relatively to each other.
Therefore, the present examples and embodiments are to be considered as illustrative and not restrictive, and the invention is not to be limited to the details given herein, but may be modified within the scope and equivalence of the appended claims.
Claims
- 1. An industrial vehicle having a frame and an axle pivotally connected with the frame, said vehicle comprising:a center shaft about which the axle pivots, said center shaft having an axis, wherein said frame is connected with the axle by the center; a first bracket fixed to the frame; a second bracket fixed to the axle; a cylinder located between the frame and the axle, said cylinder being arranged to selectively extend and retract to absorb the pivotal motion of the axle and being pivotable about axes that are normal to the axis of the center shaft, said cylinder having (i) a first end pivotally coupled to the first bracket and including a first through hole having an inner surface; (ii) a second end pivotally coupled to the second bracket; (iii) a cylinder case; (iv) a piston located in the case; (v) a first piston rod connected with the piston and slidably connected to the first end; (vi) a second piston rod connected with the second end; and (vii) two hydraulic chambers selectively receiving and discharging hydraulic fluid to extend and retract the cylinder, respectively, wherein the piston is located between the two hydraulic chambers, and the piston has a first pressure-receiving area that faces one of the two hydraulic chambers and a second pressure-receiving area that faces the other of the two hydraulic chambers, and wherein the first pressure-receiving area is substantially equal in size to the second pressure-receiving area; and joints that couple the cylinder with the frame and the axle, said joints including: a first coupler for coupling the first end to the first bracket, said first coupler including: (i) a first support shaft supported by the first bracket, wherein the first support shaft extends through the first through hole; (ii) a collar mounted on the first support shaft, wherein the collar includes a pair of large diameter portions and a small diameter portion located between the large diameter portions; (iii) a convex portion provided with the small diameter portion; and (iv) a concave portion provided with the inner peripheral surface of the first through hole, wherein said concave portion engages and slides with respect to the convex portion; and a second coupler for coupling the second end to the second bracket.
- 2. The industrial vehicle as set forth in claim 1, further comprising:said second end including a second through hole, said second through hole having an inner peripheral surface; and said second coupling means including: the second support shaft supported by the second bracket and extending through the second through hole; a spherical portion provided with the second support shaft; and a contacting surface provided with the inner peripheral surface of the second through hole, said contacting surface engaging the spherical portion.
- 3. An industrial vehicle having a frame and an axle pivotally connected with the frame, said vehicle comprising:a center shaft about which the axle pivots, said center shaft having an axis, wherein said frame is connected with the axle by the center shaft; a first bracket fixed to the frame; a second bracket fixed to the axle; a cylinder located between the frame and the axle and being pivotable about axes that are normal to the axis of the center shaft, said cylinder having (i) a first end in association with the first bracket and including a first through hole having an inner peripheral surface; (ii) a second end in association with the second bracket; (iii) a cylinder case; (iv) a piston located in the case; (v) a first piston rod connected with the piston and slidably connected to the first end; (vi) second piston rod connected with the second end; (vi) a second piston rod connected with the second end; and (vii) two hydraulic chambers selectively receiving and discharging hydraulic fluid to extend and retract the cylinder, respectively, wherein the piston is located between the two hydraulic chambers, and the piston has a first pressure-receiving area that faces one of the two hydraulic chambers and a second pressure-receiving area that faces the other of the two hydraulic chambers, and wherein the first pressure-receiving area is substantially equal in size to the second pressure-receiving area; a first joint coupling the first end to the first bracket, said first joint including: a first support shaft supported by the first bracket and extending through the first through hole; a collar mounted on the first support shaft, said collar having a pair of large diameter portions and a small diameter portion disposed between the large diameter portions; a convex portion provided with the small diameter portion; and a concave portion provided with the inner peripheral surface of the first through hole, said concave portion slidably engaging the convex portion; and a second joint coupling the second end to the second bracket.
- 4. The industrial vehicle as set forth in claim 3, further comprising:said second end including a second through hole, said second through hole having an inner peripheral surface; and said second joint including: the second support shaft supported by the second bracket and extending through the second through hole; a spherical portion provided with the second support shaft; a contacting surface provided with the inner peripheral surface of the second through hole, said contacting surface engaging the spherical portion.
- 5. The industrial vehicle as set forth in claim 4, wherein said cylinder is actuated by hydraulic force.
Priority Claims (1)
Number |
Date |
Country |
Kind |
9-197206 |
Jul 1997 |
JP |
|
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JP |
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JP |
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