JPH10318244A - Slider link device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce radius of a crank arm without changing a stroke distance of a head by providing a first link, of which one end can be rotated between a second head and a shaft, a second link, of which one end can be rotated at the first head, and a third link, of which both ends are connected to both the first and the second links and of which intermediate part can be rotated at the second head. SOLUTION: When a crank arm 1 is turned from a position at 180 degree of crank angle toward a side at 0 degree of crank angle, a second head 2 is moved from a bottom dead center to the top dead center, and a third link 5 is turned clockwise around the second head 2, and a first link 6 is turned clockwise around a support shaft 16, and a second link 7 is turned counterclockwise around a first head 4. As a result, a distance L1 between the heads 2, 4 is increased, and achieves the maximum when the crank angle is 0 degree. Length (r) of the crank arm 1 can be shortened by maintaining a constant length of the crank arm 1 and a connecting rod 3 and the constant head-to-head distance L1, and a space for the crank arm 1 can be saved in relation to the stroke distance of the head 4, and a shaft 15 and the whole of an engine can be miniaturized, and weight thereof can be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a slider link device for converting a reciprocating motion / rotational motion into a rotary motion / reciprocating motion, and more particularly to a slider link suitably used as a travel distance extending device for a crosshead type engine or the like. Related to the device.

[0002]

2. Description of the Related Art In general, as an engine for converting a reciprocating motion of a piston into a rotary motion of a shaft, a trunk piston type engine in which a side pressure of a piston is supported by a cylinder,
2. Description of the Related Art There is known a crosshead type engine in which a lateral pressure of a piston is supported by a crosshead. FIG. 2 shows a schematic view of a conventional crosshead type engine.

In FIG. 2, 1 is a crank arm, 2 is a crosshead, 3 is a connecting rod, 11 is a piston, 12 is a stuffing box, 13 is a scavenging chamber, and 14 is a cylinder. The crank arm 1 and the crosshead 2 are connected via a connecting rod 3.
Is moved along the center line of the cylinder 14 along two guide rails 8, 8 disposed in parallel with the center line of the cylinder. It penetrates up and down and is integrally connected to the lower portion of the shaft core of the piston 11 and the shaft portion of the upper surface of the crosshead 2.

The stuffing box 12 is for keeping the airtightness between the cylinder 14 and the crank chamber 18, prevents contaminated sludge in the scavenging chamber 13 from falling into the crank chamber 18, and has a piston rod. This prevents the crankcase oil adhering to 17 from being scooped up by the scavenging chamber 13.

The connecting rod 3 is a member for converting the vertical movement (reciprocating movement) of the piston 11 into a rotary movement. When the distance between the bearing centers of the connecting rod 3 is R and the crank radius is r, the ratio λ = R / r is generally in the range of 2.4 to 3.0, but generally does not interfere with the cylinder liner and piston skirt unlike the above-mentioned trunk piston type engine, so that the overall height and weight can be reduced. It is changed as needed.

[0006]

However, in the slider link device in which the crosshead and the crank arm are connected by a connecting rod, the rotation is restricted by a guide such as a rail or a cylinder, and the moving direction of the crosshead is restricted. The travel distance L of the head (crosshead) is not limited to the head type engine.
Is determined, the length of the crank arm is unambiguously determined to be L / 2 of the stroke distance L. Therefore, for the same stroke distance L, the length of the crank arm cannot be shortened, and the small space on the crank chamber side cannot be reduced. -It has the drawback of not being able to reduce the weight and weight.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a slider link device capable of reducing the radius of an arm even at the same travel distance of a head portion.

[0008]

The above object is achieved by the following constitution. In the present invention, when the arm is rotated from the bottom dead center, that is, the position at the crank angle θ = 180 ° to the crank angle 0 ° side, the second head portion moves from the bottom dead center to the top dead center. Therefore, the first link and the third link rotate clockwise around the second head portion, and the second link 7 rotates counterclockwise around the first head portion. .

For this reason, the head-to-head distance of the first head portion to the second head portion increases as the crank angle θ approaches 0 °, and becomes maximum when the crank angle θ is 0 °.

Next, when the arm is turned from the top dead center, that is, the crank angle θ = 0 ° to the crank angle 180 ° side, the second head section moves from the top dead center to the bottom dead center. Therefore, the first and third links rotate counterclockwise about the second head portion, and the second link rotates clockwise about the first head portion. For this reason,
The head-to-head distance between the first head and the second head is
It decreases as the crank angle θ approaches 180 °, and becomes minimum when the crank angle θ is 180 °. Accordingly, as the lengths of the first link, the second link, and the third link are increased while keeping the length of the arm and the connecting member constant, the head-to-head distance between the first head and the second head is increased. Can be increased,
As a result, space saving, weight reduction, and cost reduction can be achieved.

The present invention is suitably used as a mechanism for extending the stroke distance of a crosshead type engine, but can also be applied as a mechanism for extending the stroke distance of a reciprocating compressor, a press device, and a boring device. .

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will now be described in detail with reference to the drawings. However, dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention unless otherwise specified, and are merely examples. Only.

An embodiment of a slider link device used in a crosshead stroke distance extending mechanism of a crosshead type engine will be described below in detail with reference to FIG.

As shown in FIG. 1, a slider link device 20 includes a first crosshead (corresponding to a crosshead of a conventional crosshead engine) 4 reciprocated by a crank arm 1 and a connecting rod 3. And another second crosshead 2 is provided, and the first and second two crossheads 4 and 2 are connected by a link comprising a first link 6, a second link 7 and a third link 5. The gist is that the stroke distance of the first crosshead 4 is made longer than the stroke distance of the second crosshead 2 by this link mechanism to shorten the length of the crank arm.

In this slider link device 20, the shaft 15
The base end 1b of the arm 1 is fixed or integrally formed to form a crankshaft. A second crosshead (second head portion) 2 is connected to a distal end portion 1a of an arm (hereinafter, referred to as a crank arm) 1 via a connecting rod (connecting member) 3 with a tip portion 1a as a power point portion. Crosshead 2 is axis 1
5 is reciprocated according to the rotation. The first cross is on an extension of the axis a passing through the axis of the second crosshead 2 and the axis of the shaft 15 and on the side opposite to the axis of the shaft 15 with the second crosshead 2 as the center. A head (first head unit) 4 is provided.

The first crosshead 4 and the second crosshead 2 are engaged with a guide, for example, a rail 8 which is disposed in parallel with the axis a and sandwiches the axis a. It is movable only in the direction of the shaft center line a, for example, sliding and rolling. An intermediate portion 5c of the third link 5 is rotatably supported by the first crosshead 2, and one end 7a of the second link 7 is connected to the first crosshead 4 and the other end 7b is connected to the first crosshead 4. One end (open end) 5a of the third link 5 is rotatably supported.

In this case, one end 6a of the first link 6 is rotatably supported by a fixed system, for example, a crankcase, and the other end 6b is rotatably supported by the other end (open end) 5b of the third link 5. The connecting rod 3 has one end 3a at the second crosshead 2
The other end 3b is rotatably supported by a point of force (open end) of the crank arm 1.

For this purpose, the connecting arm 3 and the third link 5 are centered on the second crosshead 2, the first link 6 is centered on the fixed system, and the second link 7 is the first crosshead 2. Swing around 4.

Therefore, in this configuration, the folding angle between the third link 5, the first link 6, and the third link 5 and the second link 7 is minimum when the crank angle θ of the crank arm 1 is 0 °. When the crank angle θ is 180 °, the first crosshead 4 and the second crosshead 2 reach the top dead center when the crank angle is 0 °, and the crank angle 180 °
When it moves to the bottom dead center.

Of course, in this case, the above links 5, 6, 7
Is the length of the crank arm 1 and the connecting rod 3,
At the time of the bottom dead center, a minimum clear rank that does not cause mutual interference between the first crosshead 4 and the second crosshead 2 is formed. Each is set so as to obtain a predetermined stroke distance.

Next, the relationship between the first crosshead 4, the second crosshead 2 and the links 5, 6, 7 with respect to the crank arm 1 and the connecting rod 3 will be described in detail.

In FIG. 1, when the crank arm 1 is now rotated from the bottom dead center, that is, the crank angle θ = 180 ° to the crank angle 0 ° side, the second crosshead 2 is moved upward from the bottom dead center. When moving toward the dead center, the third link 5 rotates clockwise about the second crosshead 2,
The first link 6 rotates clockwise about a fixed support shaft 16 as a center of rotation, and the second link 7 rotates counterclockwise about the first crosshead 4.

As a result, the head-to-head distance L1 between the second crosshead 2 and the first crosshead 4 increases as the crank angle θ approaches 0 °, and when the crank angle θ is 0 °. When the maximum. Therefore, if the lengths of the crank arm 1 and the connecting rod 3 are fixed, the head distance L1 can be increased as the lengths of the first link 6, the second link 7, and the third link 5 are increased. Conversely, if the head-to-head distance L1 is constant, the length r of the crank arm 1 can be reduced.

Next, when the crank arm 1 is turned from the top dead center, that is, the crank angle θ = 0 ° to the crank angle 180 ° side, the second crosshead 2 moves from the top dead center to the bottom dead center. I do. Therefore, the third link 5 rotates counterclockwise about the second crosshead 2, and the first link 6 rotates counterclockwise about the support shaft 16 of the fixed system, and Link 7 rotates clockwise about the first crosshead 4, and the distance between the first crosshead 4 and the second crosshead 2 increases as the crank angle θ approaches 180 °. And the crank angle θ becomes 18
It becomes minimum when it is 0 °.

As described above, according to the conversion device mainly including the link mechanism including the first link 6, the second link 7, the third link 5, and the second crosshead 2,
Crank arm 1 for stroke distance of first crosshead 4
Can be shortened, and as a result, space saving on the crank arm 1 side, downsizing and weight reduction of the shaft 15 and the entire engine can be achieved, and furthermore, downsizing of the shaft 15 which is difficult to machine can be greatly reduced. Cost reduction can be achieved.

[0026]

As described above, in summary, according to the present invention, the radius of the arm can be reduced even at the same travel distance of the head portion, and an excellent effect of achieving compactness, space saving, weight reduction, and cost reduction can be achieved. Demonstrate.

[Brief description of the drawings]

FIG. 1 is a configuration diagram showing an embodiment of the present invention in which a slider link device according to the present invention is used as a mechanism for extending a stroke distance of a crosshead type engine.

FIG. 2 is a configuration diagram of a conventional crosshead type engine.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Crank arm 2 2nd crosshead (2nd head part) 3 Connecting rod (connecting member) 4 1st crosshead (1st head part) 5 3rd link 6 1st link 7 2nd Link

Claims (1)

[Claims] 1. A first head section reciprocating on a straight line, a second head section reciprocating on an extension of a straight line on which the first head section reciprocates, and a first head section reciprocating. An axis installed rotatably on the extension of a moving straight line,
An arm having one end fixed to the shaft and rotating therewith; a connecting member having one end connected to the open end of the arm and the other end connected to the second head; and one end being connected to the first head A first link rotatably supported between the second head portion and the shaft on a linear extension of reciprocating motion, and a second link rotatably supported at one end by the first head portion. And a third link whose both ends are connected to the open ends of the first and second links and whose intermediate portion is rotatably supported by the second head portion. Slider link device.