Piston type gas compressor, and piston type gas pressure drive rotation device

Abstract

A piston type gas compressor pressure drive rotation device characterized by comprising a plurality of cylinder members 41, 42 each having a closed bore, first piston members 22, 24 and second piston members 21, 23 slidably fitted into the bore of the cylinder members 41, 42, a connecting mechanism for connecting the first piston members 22, 24 and second piston members 21, 23 to the same crank shaft 15 via a slider crank mechanism, and an intake and exhaust control mechanism for controlling the intake and exhaust of gas into and out of the bore of the cylinder members 41, 42, wherein the first piston members 22, 24 and second piston members 21, 23 perform a reciprocating slide motion in the bores of the cylinder members 41, 42 with the rotation of the crank shaft 15 connected by the connecting mechanism via the slider crank mechanism, while the intake and exhaust control mechanism sends the gas, which is taken into the bores of the plurality of the cylinder members 41, 42, into the bore of one cylinder member 41 or 42 by utilizing the reciprocating slide motion of the first piston members 22, 24 and second piston members 21, 23, and compresses the gas fed to the bore.

Description

TECHNICAL FIELD [0001] The present invention relates to a device (hereinafter, referred to as “gas compressor”) having a structure for compressing air or other gases (hereinafter, referred to as “gas compressing structure”); and more particularly which is characterized in that, by means of the compression strokes sharing both cylinders, the cylinders can be downsized with almost the same compression volume as is usual. Further, an object of this invention is to provide a piston type gas compressor and a piston type gas pressure drive rotation device capable of producing high velocity rotation and high pressure, characterized in that good balance of rotation and hence high velocity rotation are achieved, wherein the crank radius in the case of high pressure compression via two-step compression mechanism equals the difference between a pair of crank radii and hence is reduced. BACKGROUND ART [0002] As gas compressor there has heretofore been suggested various ones, among which there a...

AI Technical Summary

Benefits of technology

[0045] According to a piston type gas compressor described in claim 1, there can be achieved an effect of being able to compress gas in two steps, namely, to obtain high-compressed gas with the help of a small amount of energy, because the reciprocating slider motion of the first and second piston members each fitted into the bore of each corresponding cylinder member causes the intake and exhaust control mechanism to feed the gas that has been taken into the bores of the plurality of cylinder members into the bore of one cylinder member, and at the same time to further compress the gas that has been fed into this bore.

[0046] Further, there can be attained an effect of being able to further reduce a required amount of energy for gas compression, and at the same time to downsize the entire structure as compared with the case of the rotation of each piston member via two different crank shafts, because there is configured such that the rotation of one crank shaft is made to perform the reciprocating slide motion of both of the first and second piston members each fitted into the bore of each corresponding cylinder member.

[0048] According to a piston type gas compressor described in claim 2, in addition to the effects achieved by a piston type gas compressor described in claim 1, there can be further achieved an effect of being able to construct a connecting mechanism constituted by a simple and highly efficient mechanism in terms of connecting operations, because first piston shaft members whose one end portions are firmly fixed to first piston members and second piston shaft members whose one end portions are firmly fixed to second piston allow first and second piston members to be connected to the same crank shaft disposed on the side of first piston members.

[0050] According to a piston type gas compressor described in claim 3, in addition to the effects achieved by a piston type gas compressor described in claim 2, it is envisaged that the radius of rotation of first crank arms which constitutes a connecting mechanism is made larger than that of second crank arms which likewise constitutes a connecting mechanism, thereby making it possible to make the slide length of the reciprocating slide motion of the first piston members larger than that of the second piston members, and also to make the size of a pair of gaps which are formed between the end wall portion of the bore of each cylinder member and a pair of piston members fitted into this bore, respectively, smaller than the size of the gap formed between the pair of piston members. This affords an effect of being able to further enhance or increase the intake volume into the bore of cylinder members and the compressibility within the bore of each cylinder.

[0052] According to a piston type gas compressor described in claim 4, in addition to the effects achieved by a piston type gas compressor described in claim 3, there can be further achieved an effect of being able to form a gap between the outer circumference diameter of first or second piston members and a side circumferential wall of the bore without impairing sealing properties, because the outer circumference diameter of each head portion of first and second piston members is made smaller than that of the corresponding bottom portion thereof. This makes it possible to make the slide length of the reciprocating slide motion of first piston members larger than that of second piston members.

[0054] According to a piston type gas compressor described in claim 5, in addition to the effects achieved by a piston type gas compressor according to claim 3 or 4, it is envisaged that the first and the second crank arms are made to differ in crank angle, thereby making it possible to provide a phase difference between a phase of the reciprocating slide motion of first piston members and that of second piton members. This affords an effect of being able to further increase the intake volume into the bore of each cylinder member and the compressibility within the bore of each cylinder member.

Problems solved by technology

A screw type can produce a large compression time at one time and hence produce high pressure, but has poor rotational balance and hence cannot produce high velocity rotation.

On the other hand, a screw type has good rotational balance and hence can produce high velocity rotation, but can produce only a small compression volume at one time and hence has difficulty in producing high pressure.

However, as described above, a piston type has a problem of having poor rotational balance, thus hampering high velocity rotation.

However, there is one problem that this air compression structure causes the reciprocating motion of the piston to be distributed to a pair of crank shafts provided on both sides of the cylinder member through which this piston is fitted, hampering the further increase or enhancement of the rotational torque and rotational velocity of each crank shaft as well as the downsizing of the entire air compression structure.

Further, as described above, another problem is that the reciprocating motion of the piston is transmitted to distinct crankshafts respectively disposed on either side of the cylinder member, hampering the realization of the higher velocity rotation and the further downsizing.

However, for the same reason as with the case described above, there has been a problem that the realization with a piston type which can produce a large compression volume at one time is desirable, while a piston type has poor rotational balance and hens cannot produce high velocity rotation.

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