JPS5985454A - Piston driving mechanism of stirling engine - Google Patents

Abstract

PURPOSE:To obtain the driving mechanism of a Stirling engine with improved mechanical efficiency and easiness for machining, by improving the structure of its crank pin part. CONSTITUTION:A brim part 12 having a side face wider than that of a crank arm 1b is provided in the central area between two first crank pins 1c. A second crank pin 13 is constituted such that it has a side face formed in a circle, whose radius is longer than the radius which includes the first crank pin 1c and drawn under conditions that the origin is the center axis of a crank main shaft 1a and the center axis is located in a position which advances by theta deg. from the center axis of the first crank pin 1c in the turning direction of the crank main shaft 1a. In the second crank pin, a hole is provided in the shape similar to that of the brim part 12, and the second crank pin is secured to the brim part 12 by snapping-in or shrink fit. A power piston is coupled to the first crank pins 1c, and a scavenging piston to the second crank pin 13.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a piston drive mechanism for reciprocating an air supply piston and a power piston within one cylinder with a predetermined phase difference in a Stirling engine.

A schematic diagram of a conventional piston drive mechanism is shown in FIG.

In the figure, (1) surrounded by a dashed line indicates the crankshaft, (la) is the crank main shaft, (lb) is the first crank arm, and (IQ) is the first crankshaft.

(1d) is the second crank arm, (le) is the second crank arm, (2) is the first piston, (3),
(4) is 11. fixed to the first piston (2). The second piston pin (5) is the second piston, (6) is the piston rod of the second piston (5) that can reciprocate using the central shaft of the first piston (2) as a bearing, (7
) is the $8 piston pin provided at the end of the piston rod (6), (8) is the @1 piston pin (3) and @1
a first connecting rod ringing the crank pin (1c) of the
(9) is the second connecting rod that links the @2 piston pin (4) and the first crank pin (IC), and αQ is the @8 piston pin (7) <! : 12 crank pins (1
The eighth connecting rod αυ linking e) is a cylinder in which the first piston (2) and the second piston (5) perform reciprocating motion. As can be seen from FIG. 2 showing the side view, the central axis of the second crank pin (1e) and the central axis of the first crank pin (IC) are aligned with the crank main shaft (1a) as the origin. Since there is a θ degree deviation in the rotation direction of (lB), when the crank main shaft (1a) rotates in the direction of the arrow in the figure.

The second piston (5), for example, the air supply piston, performs a reciprocating motion that is θ degrees ahead of the @1 piston (2), for example, the power piston. FIG. 3 shows a front sectional view and a side view of the actual crankshaft (1).

Since the piston drive mechanism of the conventional Stirling engine is constructed as shown below, the crankshaft (1) has a complicated structure, which reduces workability and furthermore, the overall length of the crank pin of the crankshaft (1) It takes a very long time. For this reason, the first
．． Second. Eighth connecting rod (83, (9).

In order for the QO to operate smoothly over a long period of time, the diameter of the crank shaft (1a) must be increased.

As a result, friction loss increases at the crank bearing.

The disadvantage of the Stirling engine was that the mechanical efficiency increased rapidly.

This invention was made in order to eliminate the drawbacks of the conventional ones such as the above, and between the two first crank pins,
By providing a flange whose side surface is larger than the outer diameter of the side surface of the crank arm, and by fixing the second crank pin to this flange, we have created a Stirling engine piston drive mechanism with high mechanical efficiency and easy machining. is intended to provide.

An embodiment of the present invention will be described below with reference to the drawings. Fourth
In Figure (A), (2) is a flange portion that is provided at the center of the two first crank pins (ICs) and whose side surface has the same outer diameter as, for example, the side surface of the crank arm (1b).

As shown in the side view in Figure 4), the circular shape of the side surface has its origin at the central axis of the crankshaft (1a).

The center axis is a position θ degrees in the rotational direction of the crank main shaft (1a) from the center axis of the first crank pin (IC).

The first crank pin (IC) is configured with a radius of t or less that can include the first crank pin (IC), and a hole in the shape of the flange (A) is bored inside, and the flange (A) is inserted into the flange (A) by press-fitting or shrink-fitting. 2) with the second crank pin stuck in place.

In the piston drive mechanism of the Stirling engine configured in this way, when the crank main shaft (1a) rotates in the direction of the arrow, the air supply piston (5) connected to the second crank pin (to) moves to the first crank pin. In this embodiment, the second crank arm is not provided, so the crank main shaft ( The overall length of the piston pin 1a) can be shortened, the rigidity of the crank main shaft (1a) increases, and as a result, the crank main shaft (1a) can be made thinner, resulting in higher mechanical efficiency. In the manufacturing process, the crank arm (1
b), make the pH piston pin (IQ) and the collar part O4 at the same time, and pass the piston pin (to) of the body 2, which has hollowed out the shape of the collar part (2), through the crank shaft (1a), and attach the collar part ( If it is fixed by press-fitting or shrink-fitting into (a), the piston of a Stirling engine can be easily driven.

It is also possible to construct the second crank pin 0 from aluminum alloy, etc., which makes it lighter than when made from iron.
Furthermore, the unbalanced force caused by the center spacing can be reduced.

In addition, the side shape of the crank arm (1b) and the flange aQ
If the side shapes of the two sides are made to match and the center axis of both cars is made the same,
J: Crank arm (lb.
), when manufacturing the first piston pin (le) and the flange (to), the outer diameters of the flange (2) and crank arm (1b) are finished at the same time, and the outer diameter of the crank arm (lb) is first All you have to do is cut it out, and the machining time for the piston drive mechanism can be significantly reduced.

As described above, according to the present invention, a flange portion whose side surface is larger than the outside diameter of the side surface of the crank arm is provided between the two first crank pins, and the second crank pin is fixed to this flange portion. By configuring the same, it is possible to obtain a piston drive mechanism for a Stirling engine with high mechanical efficiency and improved workability.

[Brief explanation of the drawing]

Figure 1 is a schematic configuration diagram showing the piston drive mechanism of a conventional Stirling engine, Figure 2 is a side view of Figure 1, and Figure 8 is a schematic diagram showing the piston drive mechanism of a conventional Stirling engine.
FIG. 8(A) is a front sectional view showing an actual crankshaft in a piston drive io mechanism of a conventional Stirling engine, and FIG. 8(B) is a side view of FIG. 8(A). Figure 4 GA
) is a front sectional view showing one embodiment of the present invention, and FIG.
B) shows a side view of FIG. 4(A). In the figure, (1) is the crankshaft, (la) is the crank main shaft, (lb) is the first crank arm, (tc
)+, is the first crank pin, (2) is the first piston, (3) is the first piston pin, (4 is the piston pin of Nishiki 2, (5) is the piston of Shoji 2, (7 ) is the 8th piston pin, (8) is the 1st connecting rod, (9) is the 2nd connecting rod, aq is the 8th connecting rod, 0]) is the cylinder, (6) is the part, α indicates the second crank pin. In addition, in FIG. 9, the same reference numerals indicate the same or equivalent parts. Agent Makoto Kuzuno - Figure 1 1d le 1d Figure 2 Figure 3 LA) CB) Figure 4 (A') (B)

Claims (4)

[Claims] (1) @1゜@ configured to be able to reciprocate within the cylinder
a first piston formed on the first piston;
．． A second piston pin, an eighth piston pin formed on the second piston, and a second piston pin formed on the second piston. @1 with one end connected to the 8th piston pin. Second. 8th connecting rod, h description 1, 2nd. The eighth connecting rod is constituted by a crankshaft connected to the other end of each of the connecting rods, and the writing mechanism 1. In the piston drive mechanism of the Stirling engine that operates the pistons of Shima 2 with a predetermined phase difference, the main crank, the crank arm, the first... The total length of the crank pin of the t-marked rank shaft constituted by the second crank pin is at least two widths of the bearing at the end of the first connecting rod and 1. I
: The width of the bearing at the end of the connecting rod shown in @8 is considered to be 14FIA, and it is rearranged between the two first crank fins, and has a side surface that includes the side shape of the crank arm, and The flange is configured with a width t less than the bearing width at the end of the connecting rod,
A piston drive mechanism for a Stirling engine, characterized in that a support part for the end of the eighth connecting rod and a crank pin of the slotted part 2 are fixed to this collar part. (2) A piston drive IJI structure for a Stirling engine according to claim 1, characterized in that the 12 crank pins are made of aluminum alloy. (3) The side surface of the crank arm is circular in shape circumscribing the crank pin and the crank main shaft, and the center of the circular shape on the side of the flange is aligned with the center of the crank arm. Range 1st or 2nd
Piston drive mechanism of Stirling engine described in Section 3 (4) The circular shape of the side surface of the second crank pin, including the flange, has its origin at the center axis of the crank main shaft, and its center axis is at a position θ degrees in the direction of rotation of the crank main shaft from the center axis of the first crank pin. A drive shaft for a Stirling engine according to any one of claims 1 to 8, wherein the drive shaft is configured to have a radius that can encompass the crank arm.