JP2001132809A - Stroke length adjusting device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a stroke length adjusting device for reducing the usage of a lubrication oil, improving a lubrication effect and realizing a simple and small structure. SOLUTION: In this stroke length adjusting device, the lead screw for vertically moving a crank member is inserted in the through hole provided on the center of the crank member for converting to a reciprocation. Then, the lead screw connection part on the crank member can be lubricated, as the inside of the through hole of the crank member dipped in the lubrication oil by the operation of a screw pump is lubricated by the rotation of the lead screw.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a stroke length adjusting device, and more particularly, to a structure in which the amount of lubricating oil used can be reduced and lubricating oil can be more effectively supplied to bearings and the like. The present invention relates to a stroke length adjusting device that can be simplified and can be downsized.

[0002]

2. Description of the Related Art Conventionally, for example, in a stroke length adjusting type reciprocating pump or the like employing a stroke length adjusting device, the pump is provided on an outer peripheral portion of a lead screw, a lead screw connecting portion, or the like. As a method of lubricating the bearing, for example, (a) a method of increasing the oil level of the lubricating oil so that the bearing or a part of the bearing is immersed in the lubricating oil stored in the oil storage tank, (B) a method in which an oil impeller, a lubricating oil supply impeller, or the like is attached to a worm shaft and lubricating oil is supplied to the bearing by an oil impeller, a lubricating oil supply impeller, or the like through an oil circulation hole provided in the frame; A method of attaching a slinger, a lubrication disk, etc. to a rotating part and supplying lubricating oil to the bearing from a sump by a slinger, a lubrication disk, etc .; Scan (which may also be referred to as "sealing bearings".) Grease-filled shield bearing formed by filling had method using the a.

However, the method (a) has a problem that, for example, a large amount of lubricating oil, specifically, for example, lubricating oil must be used to almost completely fill the oil storage tank. Since a large amount of lubricating oil is required, there are problems such as excessive supply of lubricating oil and leakage of lubricating oil. In the method (b), for example, an oil impeller, a lubricating oil supply impeller, It is necessary to provide a lubricating oil supply means such as an oil circulation hole, and there is a problem that the apparatus becomes complicated. In the method (c), for example, a lubricating oil supply means such as a slinger, a lubricating disk, and an oil sump is used. There is a problem that it is necessary to provide
In the above method (d), for example, a ball bearing is usually used as a shield bearing, so there is a load limit. There is a problem that the pump cannot be used.

An object of the present invention is to solve the above problems.

SUMMARY OF THE INVENTION It is an object of the present invention to reduce the amount of lubricating oil used, more effectively supply lubricating oil to bearings and the like, simplify the structure, and reduce the size. An object of the present invention is to provide a stroke length adjusting device that can be realized.

Another object of the present invention is to provide a stroke length adjusting device which has a smaller number of parts than a conventional device and is therefore easy to assemble.

[0007]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention is provided with a through-hole arranged rotatably about a central axis in a vertical direction, penetrating from an upper end to a lower end, and provided in an oil storage tank. A crank member having a lower end portion immersed at least at the top dead center in the stored lubricating oil; and a crank member disposed at an upper end of the crank member so as not to rotate via a bearing with respect to rotation of the crank member. A lead screw that is screwed into a female screw hole provided in the lead screw connection portion and has a lower end portion that is inserted into the through hole and is always immersed in the lubricating oil; The rotational motion of the crank member is transmitted in different stroke lengths according to the vertical position of the crank member, which is transmitted to the motion and moves up and down by the rotation of the lead screw. And a reciprocating body that converts the movement into motion.In another preferred aspect of the present invention, the through hole has a female screw formed on an inner peripheral surface thereof. In a further preferred aspect of the present invention, the female screw formed on the inner peripheral surface of the through hole is a reverse screw.

[0008]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. In addition, this invention,
The present invention is not limited to the following specific description.

As shown in FIGS. 1 to 6, a stroke length adjusting device 1 according to an embodiment of the present invention is rotatably formed by a rotation driving means 2 for applying a rotating force, and is rotatable by a supporting means 3. A cylindrical member 4 supported by a shaft member and a crank member 6 formed to be vertically movable by an axial moving means 5
A cam 7 mounted on the crank member 6 in a direction perpendicular to the axis of the crank member 6, a reciprocating body 8 reciprocating by the rotation of the cam 7, and an oil storage tank 9. .

The cylindrical body 4 is fixed to a lid 11 fitted in an opening 10 opened on the upper surface of the oil storage tank 9 and has a cylindrical sleeve portion 12 capable of supporting the cylindrical body. And a cylindrical mounting portion 13 provided on the bottom surface of the oil storage tank 9 and capable of supporting the cylindrical body 4 at a predetermined position in the oil storage tank 9 via a bearing. , And is rotatably held upright.

The combination of the sleeve portion 12 and the mounting portion 13 is such that the cylindrical body 4 is fixed in the oil storage tank 9.
Is rotatably supported, and is also a cylinder mounting means for rotatably mounting the cylinder 4 in the oil storage tank 9.

The length of the cylindrical body 4 is such that when the cylindrical body 4 is in the upright state, the crank member 6 to be described later is moved by the axial moving means 5 at both the bottom dead center and the top dead center. It is determined that part or all of the member 6 exists in the cylindrical body 4. When the entire crank member 6 exists in the cylindrical body 4, there is an advantage that the load and couple can be dispersed more.

As shown in FIG. 3, two openings are formed in the center of the cylindrical body 4 so as to be opposed to each other. These are referred to as a first opening 14a and a second opening 14b. Both the first opening 14a and the second opening 14b have the same square shape when viewed from the front. A part of the cam 7 is inserted into the first opening 14a and the second opening 14b as described later.

As shown in FIG. 1 and FIG.
The worm wheel 15 is attached to the lower part of the worm wheel.
That is, the worm wheel 15 has a circular mounting hole 16 formed so that the cylindrical body 4 can be fitted therein.
Are fitted at the bottom. A key 17 is attached to the lower part of the outer peripheral surface of the cylindrical body 4, so that when the worm wheel 15 rotates, the cylindrical body 4 can also rotate. The worm wheel 15 has teeth formed on an outer peripheral surface thereof, and a worm shaft 18 connected to a rotating shaft of a driving means such as a motor (not shown).
And this tooth are engaged. Therefore, when a motor (not shown) is driven, the cylindrical body 4 can rotate together.

In this embodiment, the rotary drive means 2 for transmitting the rotational force of the drive means to the cylindrical body 4 is formed by a series of combinations including the motor, the worm shaft 18 and the worm wheel 15. .

The crank member 6 is arranged in the cylindrical body 4 in a fitted state. As shown in FIG. 4, the crank member 6 forms a part of the outer peripheral surface of a cylindrical body having the same axis as the cylindrical body 4 and can slide with the inner peripheral surface of the cylindrical body 4. And a pair of oblique first and second grooves 60a and 6 formed in a groove shape from one end to the other end of the cylindrical body on the circumferential side surface of the cylindrical body.
0b. The first groove 60a and the second groove 60b are formed back to back.

The first groove 60a is connected to the crank member 6
First sloping surface 61a skewed at a predetermined angle with respect to the axis of
And a second sloping surface 61b sloping parallel to and opposed to the first sloping surface 61a, and a first sloping surface 61a and a second sloping surface 61b formed to be the bottom surface of the first groove 60a. A first bottom surface 62a, which is a plane orthogonal to the sloping surface 61b, is formed in a concave shape on the peripheral surface of the crank member. In a cross section of the crank member 6 in a direction perpendicular to the axis thereof, the edge line of the first inclined surface 61a is orthogonal to the edge line of the first bottom surface 62a, and the edge line of the second inclined surface 61b. And the edge line of the first bottom surface 62a appears orthogonally.

The second groove 60b is provided in the crank member 6
Third sloping surface 61c skewed at a predetermined angle with respect to the axis of
A fourth sloping surface 61d sloping opposite to and parallel to the third sloping surface 61c, and a third sloping surface 61c and a fourth sloping surface 61c formed to be the bottom surfaces of the second grooves 60b. A second bottom surface 62b, which is a plane orthogonal to the four inclined surfaces 61d, is formed in a concave shape on the peripheral surface of the crank member 6. In a cross section of the crank member 6 in a direction perpendicular to the axis thereof, an edge line of the third inclined surface 61c is orthogonal to an edge line of the second bottom surface 62b, and an edge line of the fourth inclined surface 61d. And the edge line of the second bottom surface 62b appears orthogonally.

The first bottom surface 62a and the second bottom surface 62b are formed parallel to each other and back to back. In this example, the first oblique surface 61a and the third oblique surface 61c are on the same plane, and the second oblique surface 61b and the fourth oblique surface 61d are on the same plane.

In this embodiment, the first groove 60a
And the second groove 60b corresponds to the cam guide portion in the present invention. More specifically, the first inclined surface 61a and the second inclined surface 61b in the first groove 60a and the third inclined surface 61c and the fourth inclined surface 61d in the second groove 60b are formed by the cylindrical body 4
Is a rotational force transmission surface for rotating the cam member 7 by rotating the crank member 6 in accordance with the rotation about the axis of the cam member 7, and the cam member is moved in accordance with the movement of the crank member 6 in the cylindrical body 4. It is also a cam moving force transmission surface that eccentrically moves the cylinder 7 in a plane perpendicular to the axis of the cylinder 4.

In other words, from a different point of view, the crank member 6 extends from one end to the other end of a cylindrical body slidably formed on the inner peripheral surface of the cylindrical body 4 and is provided on the peripheral side surface of the cylindrical body. A pair of first skewed back-to-back and sideways
This is a crank member having a groove 60a and a second groove 60b.

In the center of the crank member 6,
A through hole 65 is formed so as to penetrate from the upper end to the lower end of the crank member 6 (see FIGS. 1 and 2). The lead screw 53 of the axial moving means 5 described later is inserted into the through hole 65. The length of the lead screw 53 is long enough for at least the tip of the lead screw 53 to be immersed in the lubricating oil stored in the oil storage tank 9. Also, from a different perspective,
The lead screw 53 is arranged such that the tip is immersed in the lubricating oil.

The diameter of the lead screw 53 is shorter than the diameter of the through hole 65 by 0.6 mm to 1 mm. In other words, when the lead screw 53 is inserted into the through hole 65, the lead screw 53 and the through hole 65
And a gap of 0.3 mm to 0.5 mm is generated between them.
Due to such a gap, the lubricating oil rises in the gap due to its viscosity and hydrodynamic effects.

The crank member 6 is formed so as to be able to reciprocate along the axis in the cylindrical body 4 by the axial moving means 5. Therefore, when the lead screw 53 of the axial moving means 5 rotates, the crank member 6 moves up and down in accordance with the rotation direction, and the lubricating oil existing in the gap between the lead screw 53 and the through hole 65 rises. In other words, when the crank member rotates, the viscous lubricating oil present in the gap between the through hole and the lead screw also makes a rotational motion, and the rotation direction is the direction in which the screw of the lead screw is lifted. Ascending in the gap.

As shown in FIGS. 1 and 2, the axial moving means 5 is provided with a cylindrical shaft 51 and a lead screw connecting portion (on the crank member 6 so as to cover the upper surface of the crank member 6). Therefore, it may be referred to as a “cap portion”.) 52, a lead screw 53, a lock nut 54, and a handle portion 56. In this embodiment, a crank member moving means for moving the crank member 6 in the up and down direction is constituted by including the cylindrical shaft body 51, the lead screw connecting portion 52, the lock nut 54, and the handle portion 56. ing.

The cylindrical shaft 51 is erected on the upper surface of the crank member 6 so as to have the same axis as the crank member 6, and has an upper end larger than the outer periphery of the cylindrical shaft 51. A disk-shaped flange 51c having a diameter is attached. In the center of the cylindrical shaft 51, a lead screw insertion hole 51b through which the lead screw 53 is inserted is formed along the axis.
The lead screw insertion hole 51b is
Has the same diameter as the through hole 65 of the above.

The lead screw connecting portion 52 is a closed-end cylindrical body having a closed surface formed at the upper end and opening downward, and a female screw hole with which the lead screw 53 is screwed is formed in the closed surface. Have been. A disc-shaped holding plate having a circular hole into which the cylindrical shaft body 51 can be inserted is attached to the lower end of the opening of the lead screw connecting portion 52. The holding plate is inserted between the upper end face of the crank member and the flange 51c, and the crank member 6 can be rotated by the bearing 51a attached to the holding plate. The portion 52 is configured not to rotate, that is, not to rotate.

The lead screw connecting portion 52 is provided with a fixing member so that the lead screw connecting portion 52 does not rotate when the lead screw 53 rotates, and the position of the lead screw connecting portion 52 is fixed. 52a are provided.

At a substantially upper end of the lead screw 53, a flange 53a extending outward in the radial direction is provided. A male screw thread is formed on the outer peripheral surface between the flange 53a and the lower end of the lead screw 53. The lead screw 53 is screwed into the male screw thread and the female screw hole in the lead screw connection part 52.

The lead screw 53 is formed by a cover 11 at a portion near the flange 53a opposite to the side where the lead screw connection portion 52 is screwed with the flange 53a interposed therebetween. It is held rotatably. A nut (not shown) and a lock nut 54 are screwed above the lid 11 of the lead screw 53. Thereby, the lead screw 53
Are held so that they do not move or drop off in the axial direction.

A gear 55a is fixed above the lock nut 54 of the lead screw 53. The gear 55a meshes with a drive gear of a stroke display counter 55b provided on a side surface of a bottomed cylindrical bearing cover 11a screwed to the upper surface of the lid 11. Further, the lead screw 53
Is rotatably penetrated through an opening formed at the center of the closed surface located at the upper end of the bottomed cylindrical bearing cover 11a. At the upper end of the lead screw 53 in FIG. 1 and FIG. 2, a bottomed cylindrical handle portion 56 that opens downward is attached.

When the handle 56 is rotated, the lead screw 53 rotates, and the lead screw 53 is rotated.
The lead screw connecting portion 52 screwed with the lead screw descends or rises according to the rotation direction of the lead screw 53. When the lead screw connection part 52 is lowered or raised, the cylindrical shaft body 51 is lowered or raised accordingly, and the crank member 6 is also lowered or raised. Further, since the cylindrical shaft body 51 is rotatably mounted on the lead screw connecting portion 52 via the bearing 51a as described above, the crank member 6 rotates around its axis. Also, the lead screw connecting portion 52 and the lead screw 53 maintain their positions without rotating, and exhibit the function of a screw pump.

As shown in FIGS. 5 and 6, the cam 7 has a first cam member 30a and a second cam member 30b.

The first cam member 30a is formed when the second cam member 30b abuts with the cylindrical member 4a.
A first inner peripheral surface portion 31a that is a part of a circle having a diameter larger than the diameter of the first inner peripheral surface portion 31a
It has an outer peripheral surface portion 32a, a first guide flat portion 63a that fits into the first opening portion 14a, and a first oblique projecting portion 64a that protrudes from the first guide flat portion 63a. Also, the second cam member 30b is formed when the second cam member 30a abuts with the first cam member 30a, and forms a second inner peripheral surface 31b which is a part of a circle having a diameter larger than the diameter of the cylindrical body 4. A second outer peripheral surface 32b corresponding to the second inner peripheral surface 31b;
A second guide flat portion 63b that fits in the opening 14b, and a second oblique projecting portion 64b that protrudes from the second guide flat portion 63b.
And

The diameter of the first inner peripheral surface 31a of the first cam member 30a is the same as the diameter of the second inner peripheral surface 31b of the second cam member 30b. As shown in FIG. 5 and FIG.
When the cam member 30a and the second cam member 30b abut against each other, the diameter R of a pair of opposed arcs formed by the first inner peripheral surface portion 31a and the second inner peripheral surface portion 31b is within the cylindrical body 4. In the state where the first oblique projecting portion 64a is fitted into the first groove 60a of the mounted crank member 6 and the second oblique projecting portion 64b is fitted into the second groove 60b, the inside of the cylindrical body 4 is set. By moving the crank member 6 along the axis, the cylinder 4 can linearly move relative to the crank 6 in a plane perpendicular to the axis. It is designed so as to have a dimension that does not collide with the first inner peripheral surface 31a or the second inner peripheral surface 31b.

The first guide flat portion 63a and the second guide flat portion 63b are formed by the first cam member 30a and the second cam member 30.
On the inner peripheral surface of b, they are formed facing each other in parallel. The first guide plane 63a and the second guide plane 63b
Means that the crank member 6 mounted in the cylindrical body 4 is
The cam 7 is guided so that the cam 7 can linearly move in a plane perpendicular to the axis of the cylindrical body 4 when the cam 7 moves along the axis.

The first sloping projection 64a and the second sloping projection 64b are formed in a first groove 60a formed in the crank member 6.
The cam 7 is linearly moved in a plane perpendicular to the axis of the cylindrical body 4 when the crank member 6 moves in the cylindrical body 4 and is fitted in the second groove 60b.

Accordingly, the first oblique projecting portion 64a and the second oblique projecting portion 64b have a width that fits into the first groove 60a and the second groove 60b, and furthermore, the first oblique projection 64a and the second oblique projection 64b have the same width.
It is formed on an inclined plate inclined at the same inclination angle as the groove 60b. The sliding of the first oblique projecting portion 64a in the first groove 60a enables the linear movement of the cam 7, in other words, the eccentricity of the cam 7 becomes possible. It can be said that 64a is a guided portion guided by the first groove 60a. The second oblique projecting portion 64b is the same as the first oblique projecting portion 64a, and can be said to be a guided portion.

As shown in FIGS. 5 and 6, the cam 7 has a cam holding portion 37 having a circular opening 36 for mounting and holding the cam 7, and one end of the cam 7 is integrated with the cam holding portion 37. And a reciprocating body 8 formed by a connecting rod 39 connected to a piston (not shown) fitted at the other end to a cylinder (not shown). The cam 7 is attached so as to be rotatably fitted to a cam holding portion 37 of the reciprocating body 8. The reciprocating body 8 has a function of converting the eccentric rotational movement of the cam 7 into a reciprocating movement.

In this embodiment, the cylindrical body 4 is rotated by the rotation of the worm wheel 15 on which the cylindrical body 4 is fitted and mounted so that the shaft center is the same and the body is rotatable integrally. The crank member 6 also rotates with the rotation of the cylindrical body 4. When the crank member 6 at a predetermined position is moved up and down by the axial moving means 5 to rotate, the cam 7 eccentrically moves in accordance with the position of the cam 7 with respect to the crank member 6, and as a result, the reciprocating body 8 The stroke length of the piston is adjusted according to the position of the crank member 6.

Next, the lubrication operation of the stroke length adjusting device 1 shown in FIGS. 1 and 2 will be described.

In the stroke length adjusting device 1,
At least the lower ends of the lead screw 53 and the crank member 6 are immersed in lubricating oil. In that state,
When the crank member 6 rotates, the lubricating oil present in the gap between the through hole in the crank member 6 and the lead screw 53 also rotates. Then, the lubricating oil rises on the screw of the lead screw 53 in the through hole due to the viscous effect and the hydrodynamic effect of the lubricating oil. The rising lubricating oil overflows from the upper end opening of the through hole. The lubricating oil leaked from the gap at the upper end surface of the crank member 6 flows out to the gap between the inner peripheral surface of the cylindrical body 4 and the outer peripheral surface of the crank member 6 to lubricate them, and the upper end surface of the crank member 6 Also lubricate the bearing 51a.

After all, when the crank member 6 rotates around the lead screw crank 53, the lubricating oil also rotates, and the pumping action is exerted as a whole, and the lubricating oil flows out from the upper end surface of the crank member 6, and The bearings and the sliding surfaces associated with 4 and the crank member 6 are lubricated with lubricating oil.

In this case, the larger the viscosity of the lubricating oil, the smaller the difference between the inner diameter of the through hole and the outer diameter of the lead screw, and the higher the relative rotational speed between the lead screw and the crank member, Large hydrodynamic effect.

Hereinafter, another operation of the stroke length adjusting device 1 shown in FIGS. 1 and 2 will be described.

The stroke length adjusting device 1 can continuously adjust the stroke length from 0% to 100% irrespective of whether it is stopped or running. The principle is
The vertical movement of the crank member 6 causes the crank member 6 to move.
The stroke length is adjusted by making the rotation center of the cam 7 coincide with or separate from the rotation center of the cam 7.

FIG. 7A shows a state where the stroke is 0%. At this time, the crank member 6 is at the lowest position. At this time, when a motor (not shown) is driven, the worm shaft 18 also rotates, and the worm wheel 15 having teeth that mesh with the worm shaft 18 also rotates. Since the worm wheel 15 and the cylindrical body 4 are connected by the key 17, the cylindrical body 4 also rotates according to the rotation of the worm wheel 15. The first oblique projecting portion 64 a of the cam 7 is inserted into the inside of the cylindrical body 4 from the first opening 14 a of the cylindrical body 4, and the first groove 6 a of the crank member 6 is provided.
0a. Similarly, the second oblique projecting portion 64b
Is inserted into the inside of the cylindrical body 4 from the second opening 14 b of the cylindrical body 4 and is fitted into the second groove of the crank member 6. Therefore, the crank member 6 also rotates around the axis h1 of the cylindrical body 4 according to the rotation of the cylindrical body 4. When the crank member 6 rotates, the eccentric shaft sandwiched between the first groove 60a and the second groove 60b rotates eccentrically. However, in FIG. 7A, the axis h2 of the cam 7 is the axis h1 of the cylindrical body 4.
Located on top. Accordingly, since the cam 7 rotates around the axis h1, the stroke of, for example, the piston connected to the connecting rod 39 becomes zero.

FIG. 7B shows a state where the stroke is 100%. At that time, the crank member 6 is at the highest position. Even in this state, the first skewing protruding portion 64a of the cam 7 is provided as in the case of the stroke amount of 0%.
Is inserted into the inside of the cylindrical body 4 from the first opening 14a of the cylindrical body 4 and fitted in the first groove 60a of the crank member 6. Then, the second oblique projecting portion 64b is inserted into the inside of the cylindrical body 4 from the second opening 14b of the cylindrical body 4,
It is fitted into the second groove of the crank member 6.
Therefore, when the cylinder 4 rotates, the crank member 6 also rotates around the axis h1 of the cylinder 4 according to the rotation of the cylinder 4. Here, the axis h2 of the cam 7 is separated from the axis h1. Therefore, the cam 7 is connected to the axis h1 and the axis h.
The eccentric radius given by the distance between the axis h1
The piston connected to the connecting rod 39 reciprocates with the maximum stroke length.

Therefore, when the cam 7 is adjusted to an arbitrary position on the eccentric shaft by moving the crank member 6 up and down by the axial moving means 5, the stroke of the piston 38 connected to one end of the connecting rod 39 is adjusted. The length can be adjusted to any value in the range of 0-100%.

At this time, in the stroke length adjusting device 1, the load transmitted through the cam 7 which is forcibly rotated eccentrically by the rotation of the eccentric shaft interlocked with the rotation of the crank member 6 is applied to the outer peripheral surface of the crank member 6. It is transmitted to the cylindrical body 4 through 19. The load transmitted to the cylindrical body 4 is dispersed and transmitted to the sleeve 12 and the mounting portion 13.

Further, since the outer peripheral surface portion 19 of the crank member 6 slides and rotates in contact with the inner peripheral surface of the cylindrical body 4, a couple generated in the eccentric rotation of the eccentric shaft is dispersed and applied to the cylindrical body 4. Therefore, since couples do not concentrate on a specific member, the stroke length adjusting device 1
Has few causes of failure.

In the stroke length adjusting device 1 according to this embodiment, even if the position of the crank member 6 changes due to the vertical movement of the crank member 6, the load by the crank member 6 is not changed by the cylindrical body accommodating the crank member 6. 4 joins the inner surface. The cylindrical body 4 itself receives the load of the crank member 6 in a dispersed manner. Therefore, the stroke length adjusting device 1 in this embodiment does not receive a load on the entire holding member for accommodating the rotor as in the conventional stroke length adjusting device, and the load receiving range is smaller than that of the conventional device. Can be. Also in this respect, the stroke length adjusting device 1 of this embodiment is reduced in size.

In the stroke length adjusting device 1,
When the handle portion 56 is rotated, the lead screw 53 rotates, and the lead screw connecting portion 52 mounted on the cylindrical shaft body 51 of the crank member 6 moves up and down according to the rotation direction of the lead screw 53. Accordingly, the crank member 6 also moves up and down. Therefore, the handle portion 56
Even if the crank member 6 is moved up and down by rotating the left or right direction, the handle portion 56 and the lead screw 53 do not move up and down, so that the entire axial direction moving means 5 can be made smaller. Further, when the cam 7 makes an eccentric rotational movement, an upward force and an downward force act on the crank member 6 alternately.
Since the fixing member 52a is provided in 2, the lead screw connecting portion 52 does not rotate due to the pushing-up force and the pushing-down force. Therefore, the lead screw 5 screwed into the lead screw connecting portion 52
3 also does not rotate due to the pushing-up force and the pushing-down force. Therefore, it is not necessary to provide a rotation stopper for the lead screw 53 to prevent the rotation of the lead screw 53. Therefore, also in this point, the axial direction moving means 5 in the stroke length adjusting device 1 is reduced in size.

The present invention is not limited to the above embodiment, and the design can be changed as appropriate within the scope of the present invention.

[0055]

According to the stroke length adjusting apparatus of the present invention, the amount of lubricating oil used can be reduced, lubricating oil can be more effectively supplied to bearings and the like, and the structure can be simplified. According to the present invention, which can realize a downsizing, it is possible to provide a stroke length adjusting device which has a smaller number of parts than a conventional device and is therefore easy to assemble.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a stroke length adjusting device as an example of the present invention.

FIG. 2 is a longitudinal sectional view showing a stroke length adjusting device as an example of the present invention.

FIG. 3 is a perspective view showing a cylindrical body that can be employed in the stroke length adjusting device as an example of the present invention.

FIG. 4 is a perspective view showing a crank member that can be employed in the stroke length adjusting device as an example of the present invention.

FIG. 5 is a perspective view showing a cam that can be employed in a stroke length adjusting device as an example of the present invention.

FIG. 6 is a schematic diagram showing a cam and a reciprocating body that can be employed in a stroke length adjusting device as an example of the present invention.

FIG. 7 is an explanatory view showing a state in which the stroke length is 0% and a state in which the stroke length is 100% by combining a cylinder, a crank member, and a cam in the stroke length adjusting device as an example of the present invention; FIG.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Stroke length adjusting device, 2 ... Rotation drive means, 3 ... Support means, 4 ... Cylindrical body, 5 ... Axial direction moving means, 6 ... Crank member, 7 ... ·cam,
8 reciprocating body, 9 oil reservoir, 10 opening, 11 lid, 12 sleeve, 13.
・ Installation part, 14 ・ ・ ・ Cylindrical body, 14a ・ ・ ・ First opening, 14b ・ ・ ・ Second opening, 15 ・ ・ ・ Warm wheel, 16 ・ ・ ・ Mounting hole, 17 ・ ・ ・ Key, 18
... Warm shaft, 19 ... Outer peripheral surface, 20a
... 1st slope, 20b ... 2nd slope, 21 ...
・ Inner wall surface, 22a: first concave portion, 22b: second concave portion, 30a: first cam member 30a, 30b: second cam member, 31a: first inner peripheral surface portion .., 31b... First outer peripheral surface portion, 33a... First projecting portion, 33b... Second projecting portion, 34a. First inclined front end surface, 35b second inclined front end surface, 36 mounting hole, 37 cam holder,
39: connecting rod, 40: first outer peripheral surface, 41a,
41b: flat portion, 42: base portion, 43: second
Outer peripheral surface part, 44... First sliding inclined surface, 45.
Sliding inclined surface, 46 projecting portion, 48 opening, 4
9: first guide groove, 51: shaft, 51a: bearing, 51b: lead screw insertion hole, 52
... Cap part, 53 ... Lead screw, 54
... Lock nut, 55a ... Gear, 55b ...
Stroke display counter, 56 ... handle part, 57
... Lead screw connection member, 57a ... partition wall,
57b: detent, 58: rod screw member, 59
..Rotating member, 60a... First groove, 60b.
Groove, 61a: first sloping surface, 61b: second sloping surface,
61c: third sloping surface, 61d: fourth sloping surface, 62
a ... first bottom surface, 62b ... second bottom surface, 63a ...
1st guide plane part, 63b ... 2nd guide plane part, 64a.
..First protrusions, 64b ... second protrusions, 65 ...
Through-hole, 66 ... shaft body.

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) F16H 35/00 F04B 21/00 A F16N 7/16 QZ F Term (Reference) 3H071 AA03 BB01 CC27 CC32 CC33 CC34 DD42 DD89 3H075 AA01 BB03 CC12 CC15 DB22 DB35

Claims (3)

[Claims] 1. A lower end portion rotatably disposed about a central axis in a longitudinal direction, having a through hole penetrating from an upper end to a lower end, and having a lower end portion immersed in lubricating oil stored in an oil storage tank. A crank member, and a female screw hole provided in a lead screw connection portion arranged at an upper end of the crank member so as to be unable to rotate via a bearing with respect to the rotation of the crank member, and A lead screw having a lower end portion that is inserted and is always immersed in the lubricating oil; and a lift movement of the crank member, which transmits a rotation motion of a rotation driving unit to a rotation motion of the crank member, and moves up and down by rotation of the lead screw. A reciprocating motion converting means for converting the rotational motion of the crank member into a reciprocating motion having a different stroke length according to a position. The length adjustment device. 2. The stroke length adjusting device according to claim 1, wherein said through hole has a female screw formed on an inner peripheral surface thereof. 3. The stroke length adjusting device according to claim 2, wherein the female screw formed on the inner peripheral surface of the through hole is a reverse screw.