JPS59160086A - Gas compressor - Google Patents

Abstract

PURPOSE:To simplify the mechanism, reduce the leakage of compression and permit to drive the compressor with a small driving power by converting the rotary motion of a driving shaft into the oscillating motion of a piston and compressing the suction gas alternately. CONSTITUTION:When the driving shaft 8 is rotated and an oscillating cam 7 is oscillated, one of operating chambers is expanded and the operating chamber becomes vacuum, therefore, the gas is sucked into the operating chamber through a suction port 12 under opening a reed valve. When the driving shaft 8 is rotated further from a position, whereat the volume of one of the operating chambers become the maximum confining volume, into clockwise direction, the volume of one of the operating chamber is compressed and the compressed gas opens the reed valve and is discharged out of a delivery port 14. At this time, the operation chamber at the other side is expanded in the volume thereof and sucks the gas. Thus, the oscillating piston 7 is oscillated by the rotation of the driving shaft 8 and the suction and delivery motions may be effected sequentially and alternately.

Description

[Detailed description of the invention] The present invention relates to a gas compressor having a novel structure.

Variable displacement gas compressors are mainly divided into reciprocating piston type and rotary type, each having their own disadvantages and advantages.

In other words, the reciprocating piston type requires a complicated mechanism such as a crankshaft and a connecting rod in order to convert rotational motion into reciprocating linear motion, and there is also a lot of mechanical loss due to this, and it is not suitable for its capacity. Becomes large.

In contrast, the rotary type uses the rotational movement 1c as power, so the mechanism is simple and can be made smaller, but compared to the piston type, the leak area of the compression part is larger, so it is particularly difficult to use. During the compression stroke at low speeds, gas leaks into the low pressure chamber, resulting in an increase in driving power due to recompression.

The object of the present invention is to provide a mechanism that is simpler than the reciprocating piston type, has less compression leakage than the rotary type, and can be driven with less driving power.

In order to achieve the above-mentioned object, the present invention includes a piston that is swingable and horizontally mounted in a cylinder chamber, a bearing passing through the cylinder chamber 2, and connected to the piston to cause the rotation of the piston. a piston drive shaft that swings the piston;
A novel rocker comprising an intake boat and a discharge port that communicate with the compression working type formed by the outer periphery of the piston and the inner wall of the cylinder chamber, and check valves for intake and discharge provided at each port. We provide dynamic gas compressors.

Embodiments of the present invention will be described in detail below with reference to the drawings.

1 to 4 show a first embodiment of the invention.

In each figure, the gas compressor includes a cylindrical case 1 with one end open, a compressor main body 2 airtightly loaded into the case 1, and a front head 3 attached to the open surface of the case 1. .

The compressor main body 2 includes a cylinder-shaped cylinder 4 whose inner periphery has a substantially pincushion-shaped cross section, and a front side block 5 and a rear side block 6 mounted on both sides of the cylinder. Be prepared.

Inside a cylinder chamber with a pincushion-shaped cross section formed by the cylinder 4 and both side blocks 5 and 6, a pair of frog-like swinging pistons 7.7 are arranged one above the other. At the center of the cylinder chamber, a piston and a drive shaft 8 are provided which extend through the front head 3 and are rotatably supported at both ends by respective side blocks 5 and 6.

Each swing piston 7 is configured to be able to swing left and right about a support shaft 9 whose both ends are supported by the front side block 5 and rear side block 6, and the swing piston 7 is configured to be able to swing left and right around a support shaft 9 which has both ends supported by the front side block 5 and rear side block 6. A pair of cam floors 10 are rotatably provided in the center.

In contrast, a cam 11 having a circular path is integrated into the center of the piston wl@shaft 8, which slides into contact with each of the cam floors 10 and swings each of the swinging pistons 7 by its rotation.

Therefore, as the drive shaft 80 rotates, the swing piston 7
oscillates, and as a result, it alternately expands and contracts laterally and vertically symmetrically within a generally crescent-shaped compression work chamber surrounded by the back surface of the oscillating piston 7 and the cylinder interior wall.

Correspondingly, the front side block 5 has intake bows (12, 12, . . .) communicating with each of the working chambers.

are formed at four locations, and plate-shaped check valves 1 and 3 are interposed between the end faces of the front side block 5 and the cylinder 4.

As shown in FIG. 3, the check valve 13 is formed by stamping a plate 13α made of a spring material and having the same cross-sectional shape as the cylinder 4.

is formed in contact with the intake boat [2].

Further, on the discharge side with respect to the intake side, there are a plurality of discharge ports 14, 14, which are bored on both sides of the cylinder 4 so as to communicate with each of the compression work chambers. And each port 1
Reed valves 15, 15 for non-returning are attached to both sides of the cylinder 4 in contact with the reed valve 15, and a valve support 16 in contact with the back surface of the reed valve 15 is provided.

Furthermore, the sealing mechanism for the compression chamber in the NFC compressor main body 2 configured as described above is provided at two points at both ends of the compression chamber, that is, at both swing ends of the swing piston 7 and at the pivot point. In this embodiment, a gasket made of a material such as Teflon is placed in a seal groove formed along the axial direction on the inner surface of the cylinder chamber) 17 , 170 . It is loaded with.

Next, the operation of the gas compressor configured as described above will be explained.

When the swing cam 7 swings due to 80 rotations of the drive shaft, one of the working chambers expands, creating negative pressure inside the working chamber, and the NFC intake port 18 provided in the front head 3 flows into the tip of the case l as shown by arrow A. The introduced gas passes through the intake boat 12 of the front side block 5 and reaches the lead pulp 13 b f
As shown in Figures 1 and 4 (c), the cam was displaced approximately 45° from the center shaft at the position where one of the working chambers had the maximum confinement volume. When the drive shaft 8 is further rotated clockwise from this point, the volume of one of the working chambers is reduced and the reed pulp 15 is opened and the discharge boat 14 is opened as shown in FIG. The compressed gas is exhausted. This gas is in cylinder 4
Formed between and case 1! An opening (not shown) in the rear side block 6 is formed at the rear of the case 1 from the bottom gap.
It is discharged to the outside from the discharge port 20 through the entire NFC space 19.

Simultaneously with straining, the volume of the working chamber on the other side expands 2, and the Nato pulp 13 is opened to suck in gas gold in the same manner as described above.

When the drive shaft 8 is further displaced clockwise from this state, the volume of the one working chamber becomes zero, that is, the discharge process is completed, and the volume of the other working chamber becomes zero, as shown in FIG. 4(c). is maximum. When the drive shaft 8 further rotates from this state, the suction and discharge operations of gas are repeated alternately at the opposite position to the above. and discharge operation.

In this embodiment, the shape of the cam 11 is drawn in a seed-like shape to simplify the explanation, but in reality, the rotation locus of this cam and the swing piston are both π (partly on the back side). The shape of the cam lead surface is such that one of the cam floors always comes into sliding contact with the cam lead surface of the cam due to the applied pressure difference, allowing smooth rocking motion.

FIG. 5 shows a second embodiment of the invention. However, the same reference numerals are used for the lock parts as in the previous embodiment, and the explanation thereof will be omitted.

A pair of rocking pistons 30 in the figure have a cam groove 31t formed in their center, and a cam floor 32 in the center of the drive shaft 8 that slides into the cam groove 31. It is provided eccentrically so that the amount of eccentricity corresponds to the swing angle of the swing piston.

In this embodiment as well, suction and discharge operations are performed alternately in the same manner as described above.

Furthermore, in this embodiment, the structure is simplified compared to the first embodiment, and the cam shape is also simplified.

In this embodiment, since each swing piston 30 is connected to one cam floor 3, suction is performed on one side of the cylinder chamber, and discharge is performed on the other side at the same time. However, if a pair of cam floors 32'jk are provided facing each other by 180 degrees and the respective swing pistons 30i are connected to each cam floor 32, suction and discharge can be performed alternately on the upper and lower diagonals as in the first embodiment. It can be carried out.

Further, in each embodiment, a pair of swinging pistons are provided, but it goes without saying that it is also possible to provide one swinging piston, or three to zero or more.

As explained in detail in each of the embodiments above, in the present invention, as described above, the rotational motion of the drive shaft is converted into a swinging motion to alternately compress the sucked NYC gas. Compared to conventional reciprocating piston type gas compressors, the mechanism is simple and does not require a complicated mechanism to convert rotational motion to linear motion. There is no compression leakage compared to the conventional compressor, and since the sealing mechanism for this need only be provided at both ends of the compression work chamber, there are various effects such as low sliding chord resistance and low driving power.

[Brief explanation of the drawing]

Figure 1 is a front cross-sectional view of a gas compressor according to the first embodiment of the present invention, Figure 2 is a cross-sectional view taken along line n--n in Figure 1, and Figure 3 is a reverse view of the m-m helix in Figure 2. Front view showing the upper valve, Figure 4 (
A), (B), (G') are explanatory diagrams showing the operation,
FIG. 5 is a cross-sectional view 20 according to a second embodiment of the present invention.
Compressor body 40. Cylinder 50. Front side block 60. Rear side block 7, glossy. , swinging piston 81. Drive shaft 90. Support shaft 12. Intake port 130. Check valve 13b, reed valve 145. Discharge port 150. Reed valve and above Figure 4 (A) Figure 4 (El) Figure 4 (0)
Figure 5

Claims (1)

[Claims] α) A piston horizontally suspended in a cylinder chamber so as to be able to swing;
A compression work chamber formed by a piston drive shaft ζ that passes through the cylinder chamber and is supported by a bearing, and is connected to the piston and swings the piston by its rotation, the outer periphery of the piston and the inner wall of the cylinder chamber. A gas compressor characterized by consisting of an intake boat and a discharge boat that communicate with each other, and an NFC intake and discharge check valve provided on each boat.