US20050042112A1 - Piston type gas compressor, and piston type gas pressure drive rotation device - Google Patents

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

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Publication number
US20050042112A1
US20050042112A1 US10/492,672 US49267204A US2005042112A1 US 20050042112 A1 US20050042112 A1 US 20050042112A1 US 49267204 A US49267204 A US 49267204A US 2005042112 A1 US2005042112 A1 US 2005042112A1
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United States
Prior art keywords
piston
members
bore
gap
cylinder
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US10/492,672
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English (en)
Inventor
Kowhei Nokubi
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CHUOGIKEN KOGYOU Co Ltd
CHUOGIKEN KOGYO CO Ltd
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CHUOGIKEN KOGYO CO Ltd
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Assigned to CHUOGIKEN KOGYOU CO., LTD. reassignment CHUOGIKEN KOGYOU CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NOKUBI, KOWHEI
Publication of US20050042112A1 publication Critical patent/US20050042112A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/025—Driving of pistons coacting within one cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/005—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders with two cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for

Definitions

  • 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.
  • 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.
  • 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.
  • 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.
  • a piston type could perform high velocity rotation, then a piston type would be extremely preferable as gas compression structure, as compared with a screw type, which can produce only a small compression volume at one time.
  • a piston type has a problem of having poor rotational balance, thus hampering high velocity rotation.
  • a gas compression structure for solving the above problems, the applicant has devised (invented) a air compression structure comprising a input shaft and a auxiliary shaft, which are arranged side-by-side, wherein there is provided slider of each of a slider crank mechanism on the input shaft side and at least one slider crank mechanism on the auxiliary shaft which slider crank mechanism constitutes a pair with the slider crank mechanism on the input shaft side in a state, where piston members repulsed by a pressure mutually are provided to the slider and reciprocated in the same direction while facing mutually in the same cylinder to compress air; and the outer diameter of the front end of the piston members is smaller than the inner diameter of the cylinder so that there can be formed a gap portion between the inner diameter of the cylinder and the outer diameter of the front end of the piston members.
  • the air compression structure described above makes it possible to produce compressed air with a minimum of energy.
  • 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.
  • the present invention is one which is achieved to solve the above problems, and has for its object to provide a compact piston type gas compressor which can produce high pressure with the help of a small amount of energy and is capable of high torque and high velocity rotation, and a piston type gas pressure drive rotation device which can rotate by clean energy and is further capable of high torque and high velocity rotation.
  • a piston type gas compressor comprises: a plurality of cylinder members each of which has a closed bore; first piston members and second piston members slidably fitted into the bore of the each cylinder member; a connecting mechanism for connecting the first piston members and second piston members to the same crank shaft respectively, 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 each cylinder member, wherein said first piston members and second piston members perform a reciprocating slide motion in the bores of said respective cylinder members in accordance with the rotation of the crank shaft connected by the connecting mechanism via slider crank mechanism; while the intake and exhaust control mechanism feeds the gas, which has been taken into the bores of the plurality of cylinder members, into the bore of one cylinder member by utilizing the reciprocating slide motion of said first piston members and second piston members, and compresses the gas fed to said bore.
  • the rotation of the crank shaft causes the first piston members and second piston members, which are connected to the crank shaft via slider crank mechanism owing to connecting mechanism, to reciprocate within the bore of each corresponding cylinder.
  • the intake and exhaust of gas into and out of the bore of each cylinder member is controlled through the intake and exhaust control mechanism.
  • the gas that has been taken into the bores of a plurality of cylinder members is fed into the bore of one cylinder member. Further at the same time, the gas that has been fed into this bore is further compressed.
  • a piston type gas compressor according to claim 2 in a piston type gas compressor according to claim 1 , in which the connecting mechanism comprises first piston shaft members whose one ends are firmly fixed to the respective first piton members and second piston shaft members whose one ends are firmly fixed to the respective second piston members and which are arranged side-by-side with the first piston members; and a through-hole penetrated through said first piston members, through which the second piston shaft members, arranged side-by-side with the first piston members, are capable of being slidably fitted, in which the first piston members and second piston members are connected to the same crank shaft arranged on the side of the first piston members via the first piston shaft members and second piston shaft members.
  • the connecting mechanism comprises first crank arms for connecting the first piston shaft members to the crank shaft and second crank arms for connecting the second piston shaft members to the crank shaft in a state, where the radius of rotation of the first crank arms is larger than that of the second crank arms.
  • piston type gas compressor according to claim 4 in the piston type gas compressor according to claim 3 , in which the outer circumference diameter of each head of the first piston members and second piston members is made smaller than that of the corresponding bottom portion thereof.
  • piston type gas compressor according to claim 5 in the piston type gas compressor according to claim 3 or 4 , in which the first crank arms and the second crank arms are made to differ in each crank angle.
  • a piston type gas compressor is in accordance with a piston type gas compressor described in any one of claims 1 to 5 , in which the intake and exhaust control mechanism comprises an intake mechanism for causing a first intake gap and a second intake gap to take in gas alternately in a state, where the first intake gap is composed of a first gap formed between the end wall portion of the bore of one cylinder member and the bottom portion of either of the first piston member or the second piston member fitted into said bore, and a second gap formed between the end wall portion of the bore of the other cylinder member and the bottom portion of either of a first piston member or second piston member fitted into the bore, and where the second intake gap is composed of a third gap formed between the end wall portion of the bore of the one cylinder member and the other of the first piston member or second piston member, and a forth gap formed between the end wall portion of the bore of the other cylinder member and the bottom portion of the other of the first piston member or second piston member fitted into said bore; a gas feed mechanism for feeding the gas, which has been
  • a piston type gas compressor according to claim 7 in the piston type gas compressor according to claim 6 in which the first gap is formed between the end wall portion of the bore of one cylinder member and the bottom portion of the first piston member fitted into the bore; the second gap is formed between the end wall portion of the bore of the other cylinder member and the bottom portion of the second piston member fitted into the bore; the third gap is formed between the wall face of the bore of the one cylinder member and the bottom portion of the second piston member fitted into said bore; and the fourth gap is formed between the end wall portion of the bore of the other cylinder member and the bottom portion of the first piston member fitted into the bore.
  • piston type gas compressor according to claim 8 in the piston type gas compressor described in any one of claims 1 to 7 , in which there is provided a phase difference of 180 degrees or 120 degrees between a reciprocating slide motion of the first piston members and second piston members fitted into the bore of one cylinder member and that of the first and second piston members fitted into the bore of the other cylinder member.
  • a piston compressor according to claim 9 is capable of high velocity rotation, which has first piston members and second piston members faced mutually on a line within the same cylinder so as to compress gas by reciprocating the first and second pistons in the same direction, in which there is provided a mechanism in which a piston shaft for reciprocating the first piston members causes the second piston member to be penetrated, so that both piston shafts are put together on one side to reciprocate; and a structure in which each of piston shafts with a machinery body having dual cylinders arranged side-by-side and piping and pressure valve integrated together, the machinery body constituting one set, is connected via crank connecting rod with crank mechanisms, the crank mechanisms differing in crank angle and crank radius, so as to be able to perform crank rotational motion and piston reciprocating motion well balanced, wherein building of both a single machinery and a multiple machinery is possible.
  • a piston type gas pressure drive rotation device comprises a plurality of cylinder members each of which has a closed bore; first piston members and second piston members slidably fitted into the bore of the each cylinder member; an intake and exhaust control mechanism for controlling the intake and exhaust of gas into and out of the bore of said each cylinder member so as to make the first piston members and second piston members slidably reciprocating motion; and a connecting mechanism for connecting the first piston members and second piston members to the same crank shaft having a slider crank mechanism so as to convert the reciprocating slide motion of both the first piston members and second piston members in accordance with the control of the intake and exhaust control mechanism into one rotational motion; wherein the intake and exhaust control mechanism feeds compressed gas into the bore of one cylinder member while feeding the gas that has expanded in the bore into the bores of the plurality of cylinder members.
  • a piston type gas pressure drive rotation device in a piston type gas pressure drive rotation device according to claim 10 , in which the connecting mechanism comprises first piston shaft members whose one ends are firmly fixed to the first piston members, and second piston shaft members whose one ends are firmly fixed to the second piston members, and the second piston shaft members are arranged side-by-side with the first piston members, and a through-hole penetrated through the first piston members, through which the second piston shaft members, arranged side-by-side with the first piston members, are capable of being slidably fitted, in which the first piston members and second piston members are connected to the same crank shaft disposed on the side of the first piston members via the first piston shaft members and second piston shaft members.
  • the connecting mechanism comprises first crank arms for connecting the first piston shaft members to the crank shaft and second crank arms for connecting the second piston shaft members to the crank shaft in a state, where the radius of rotation of the first crank arms is made larger than that of the second crank arms.
  • piston type gas pressure drive rotation device in the piston type gas pressure drive rotation device according to claim 12 , in which the outer circumference diameter of each head portion of the first piston members and second piston members is made smaller than that of the corresponding bottom portion thereof.
  • piston type gas pressure drive rotation device in the piston type gas pressure drive rotation device according to claim 12 or 13 , in which said first crank arms and said second crank arms are made to differ in each crank angle.
  • the intake and exhaust control mechanism comprises an intake mechanism for causing a fifth gap and sixth gap to take in gas alternately in a state, where the fifth gap is formed between head portion of the first piston members and second piston members fitted into the bore of one cylinder member constituting the cylinder members, and where the sixth gap is formed between head portion of the first piston members and second piston members fitted into the bore of the other cylinder member constituting said cylinder members; a gas feed mechanism for feeding the gas, which has been taken into the fifth gap via the intake mechanism, by distributing the gas between both gaps, into a first gap formed between the end wall portion of the bore of the one cylinder member and the bottom portion of either of the first members or the second piston members fitted into said bore, and a second gap formed between the head portion of the bore of the other cylinder member and the bottom portion of either of the first piton members or the second piston members fitted into the bore, while feeding the
  • a piston type gas pressure drive rotation device in the piston type gas pressure drive rotation device according to claim 15 , in which the first gap is formed between the end wall portion of the bore of one cylinder member and the bottom portion of the first piston member fitted into the bore; the second gap is formed between the end wall portion of the bore of the other cylinder member and the bottom portion of the second piston member fitted into the bore; the third gap is formed between the wall face of one cylinder member and the bottom portion of the second piston member fitted into the bore; and said fourth gap is formed between the end wall portion of the bore of the other cylinder member and the bottom portion of the first piston member fitted into said bore.
  • a piston type gas pressure drive rotation device in the piston type gas pressure drive rotation device described in any one of claims 10 to 16 , wherein there is provided a phase difference of 180 degrees or 120 degrees between the reciprocating slide motion of the first piston members and second piston members fitted into the bore of one cylinder member, and that of the first piston members and second piston members fitted into the bore of the other cylinder member.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • a piston type gas compressor described in claim 6 in addition to the effects achieved by a piston type gas compressor described in any one of claims 1 to 5 , it is further possible to perform the intake of gas into the bore of both of one and the other cylinders, respectively, and at the same time to compress and feed into either of one or the other cylinder the gas that has been taken into the bores of both the cylinder members, utilizing the reciprocating slide motion of both of first and second cylinder members. This affords an effect of being able to efficiently compress gas, utilizing the reciprocating slide motion of both the cylinder members.
  • a first gap is formed between the end wall portion of the bore of one cylinder member and the bottom portion of a first piston member fitted into the bore; a second gap is formed between the end wall portion of the bore on the other cylinder member and the bottom portion of a second piston member fitted into the bore; a third gap is formed between the end wall portion of the bore of the one cylinder member and the bottom portion of the second piston member; and a fourth gap formed between the end wall portion of the bore of the other cylinder member and the bottom portion of the first piston member fitted into the bore, so that there can be provide a phase difference between the reciprocating slide motion of the first piston member fitted into the one piston member and that of the first piston member fitted into the other piston member.
  • a piston type gas compressor described in claim 8 in addition to the effects achieved by a piston type gas compressor described in any one of claims 1 to 7 , there can be achieved an effect of being able to prevent the rotational balance of the crank shaft from deteriorating, because there is provided a phase difference of 180 degrees or 120 degrees between the reciprocating slide motion of each piston member fitted into the bore of one cylinder member and that of each piston member fitted into the bore of the other cylinder member and corresponding to the respective piston member within the one cylinder member.
  • a piston type gas compressor described in claim 9 there is achieved a structure in which reciprocating mechanisms of the piston shafts are put together on one side, and the high pressure compression load of the cylinder of each volume is compressed through the difference of the length of crank shaft radii, so that a slight amount of a difference in rotational angle is provided between the cranks so as to effectively reduce the high pressure compression load to the last.
  • the residual pressure air after exhaust of the residual high pressure compressed air will act as equivalent to the repellent force of a magnet, and hence will aid in the rotation, because repellent force will act on the larger radius according the difference in crank radii.
  • high velocity rotation similar to that of a conventional gasoline engine can be realized with a compact mechanism.
  • a piston type gas pressure drive rotation device because the intake and exhaust control mechanism causes compressed gas to be fed into the bore of one cylinder member, and at the same time causes the gas that has expanded within said bore to be distributed into the bores of a plurality of cylinder members, the expansion force of this compressed gas causes the first and second piston members to perform reciprocating slide motion. That is, it becomes possible to push the first and second piston members utilizing the expansion force of the compressed gas in two steps. Therefore, there can be achieved an effect of being able to reduce the required amount of energy for the rotation of the crankshaft.
  • the connecting mechanism allows a pair of pistons each fitted into each corresponding cylinder to be connected both to one same crank shaft, the energy of each piston member required for the rotation of the crank shaft can be divided into a plurality of cylinder members. This makes it possible to achieve an effect of being able to further reduce the energy required for the rotation of the crankshaft and to downsize the entire structure.
  • a piston type gas pressure drive rotation device described in claim 11 in addition to the effects achieved by a piston type gas pressure drive rotation device described in claim 10 , 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 the first piston shaft members whose one ends are firmly fixed to the first piston members and the second piston shaft members whose one ends are firmly fixed to the second piston members allows the first and second piston members to be connected to the same crank shaft disposed on the side of the first piston members.
  • the rotational radius of the first crank arms which constitute a connecting mechanism is made larger than that of the second crank arms which constitute likewise 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 to enlarge the size of a pair of pistons each formed between the end wall portion of the bore of each cylinder portion and a pair of piston members fitted into this bore and at the same time to enlarge the amount of displacement of a gap formed between the pair of these piston members.
  • This makes it possible to achieve an effect of being able to enhance the coefficient of expansion of compressed gas, that is, of being able to enhance the rate of exploitation of expansion force of this compressed gas.
  • a piston type gas pressure drive rotation device described in claim 13 in addition to the effects achieved by a piston type gas pressure drive rotation device described in claim 12 , there can be further achieved an effect of being able to form a gap between the outer circumferential diameter of the first or second piston members and the side circumferential wall of the bore without impairing sealing properties, because the outer circumferential diameter of each head of the first and second piston members is made smaller than that of the corresponding bottom portion thereof. That allows the slide motion length of the reciprocating slide motion of the first piston members to be made larger than that of the second piston members, allowing the coefficient of expansion of compressed gas to be further enhanced.
  • a piston type gas pressure drive rotation device described in claim 14 in addition to the effects achieved by a piston type gas pressure drive rotation device described in claim 12 or 13 , there can be further achieved an effect of being able to provide a phase difference between the phase of the reciprocating slide motion of the first piston members and that of the second piston members. This allows the coefficient of expansion to be further enhanced.
  • a piston type gas pressure drive rotation device described in claim 15 in addition to the effects achieved by a piston type gas pressure drive rotation device described in any one of clams 10 to 14 , it is envisaged that compressed gas is fed into the fifth and sixth gaps, thereby making it possible to cause the first and the second piston members each fitted into each corresponding cylinder to slide upon utilizing the expansion force of this compressed gas, and at the same time to distribute the gas, which has expanded within the fifth gap, into the first and second gaps, while further distributing the gas, which has expanded within the sixth gap, into the third and the fourth gaps, thereby making it possible to achieve an effect of being able to further cause respectively the first or the second piston members fitted into each corresponding cylinder member to slide utilizing the expansion force of the gas. Further, there can be achieved an effect of being able to enhance the rotational balance and rotational speed of the crankshaft, because gas feeding into the fifth and the sixth gaps is performed alternately.
  • a first gap is formed between the end wall portion of the bore of one cylinder member and the bottom portion of the first piston member fitted into the bore; a second gap is former between the end wall portion of the bore of the other cylinder member and the bottom portion of the second piston member fitted into the bore; a third gap is formed between the end wall portion of the one cylinder member and the bottom portion of the second piston member fitted into the bore; a fourth gap is formed between the end wall portion of the bore of the other cylinder member and the bottom portion of the first piston member fitted into the bore, thereby making it possible to achieve an effect of being able to provide a phase difference between the reciprocating slide motion of both the piston members fitted into the one piston member and that of both the piston members fitted into the other piston member. With that, there can be achieved an effect of being able to realize the further enhancement of the rotational balance and rotational speed of the crankshaft.
  • a piston type gas pressure drive rotation device described in claim 17 in addition to the effects achieved by a piston type gas pressure drive rotation device described in any one of claims 10 to 16 , it is envisaged that there is provided a phase difference of 180 degrees or 120 degrees between the reciprocating slide motion of each piston member fitted into the bore of one cylinder and that of each piston member fitted into the bore of the other cylinder member and corresponding to the respective piston members within the other, thereby making it possible to achieve an effect of being able to realize the further enhancement of the rotational balance and rotational speed of the crank shaft.
  • the present invention relates to a piston type gas compressor and to a piston type gas pressure drive rotation device, but these can be realized with the same structure (of course, it is needless to say that there can be provided appropriate differences between both for enhancing the performance). Namely, despite one mechanism (structure), this can become a device for compressing gas utilizing rotational force, or a device for producing rotation utilizing compressed air. Therefore, the piston type air compression structure described in the application (basic application) upon which the priority claim of the present application is based, includes the both, and in the present application the description will be made distinguishing between a piston type gas compressor and a piston type gas pressure drive rotation device for the ease of understanding of the invention.
  • the air of the air compressor represents merely an example of compressed gas, and it will be explicitly indicated that the gas is not limited to air but includes, for example, nitrogen, oxygen, argon, etc.
  • FIG. 4 is a perspective view of cylinder member 40 , which is component of a piston type gas compressor 100 to be of an example of the invention.
  • cylinder member 40 is constituted by both of a first cylinder member 41 and a second cylinder member 42 , and the first cylinder member 41 is connected to the second cylinder member 42 via air feed pipe 50 .
  • FIGS. 6 to 8 are detailed plan views of the piston type gas compressor 100 as described above, but in FIGS. 1 and 2 , cylinder member 40 is shown partially in cross section for the ease of understanding of the invention.
  • Crank mechanism 10 as shown in FIGS. 6 to 8 is assumed to have a maximum forward position of 180 degrees and a maximum backward position of 360 degrees on a horizontal line, measured counterclockwise with respect to a center of crank rotation.
  • First crank mechanism 10 a has 7.1 mm radius/180 degrees, second 10 b 4.9 mm radius/165 degrees, third 10 c 4.9 mm radius/345 degrees, and fourth 10 d 7.1 mm radius/360 degrees. This has crank mechanism well balanced.
  • phase difference 180 degrees between first crank mechanism 10 a and fourth crank mechanism 10 d and between second crank mechanism 10 b and third crank mechanism 10 c
  • phase difference between first crank mechanism 10 a and second crank mechanism 10 b (namely, between the piston members arranged within the same cylinder member).
  • crankshaft 15 It is possible to transform rotational motion of the crankshaft 15 smoothly into the reciprocating slide motion of piston members. This makes it possible to enhance the rotational balance and rotational speed of crankshaft 15 . These all contribute to the enhancement of the efficiency of gas compression.
  • crank mechanism 10 a is connected to crank connecting rod 11 , piston shaft member 15 and second piston member 21 ; crank mechanism 10 b is connected to crank connecting rod 12 , piston shaft member 16 and first piston member 22 ; crank mechanism 10 c is connected to crank connecting rod 13 , piston shaft member 17 and second piston member 23 ; and crank mechanism 10 d is connected to crank connecting rod 14 , piston shaft member 18 and first piston member 24 . This causes the reciprocating motion to be well balanced against the rotational motion.
  • Piston shaft members 15 , 17 respectively connected to second piston members 21 , 23 are put together on one side via transparent hole provided within and penetrating through first piston members 22 , 24 , respectively. Therefore, with only one rotational system, it can cause the two piston members arranged in each cylinder member to perform reciprocating slide motion. This contributes to the simplification of the structure.
  • Machinery body 20 having dual cylinders arranged side-by-side and air passage and pressure valve integrated together is constituted by first cylinder member 41 having provided therein second piston member 21 and first piston member 22 , and second piston member 42 having provided therein second piston member 23 and first piston member 24 .
  • Crankshaft 10 's counterclockwise rotation causes second piston member 21 , first and second piston members 22 and 23 , and first piston member 24 to reciprocate within cylinders according to each crank radius.
  • volumetric cylinders (spaces) 31 , 33 , and 35 sandwiched between second piston member 21 and first piston member 22 are created within one cylinder volume, and perform air compression motion.
  • volumetric cylinders 30 , 32 , and 34 sandwiched between second piston member 23 and first piston member 24 are created, which then perform air compression motion. Compression strokes are produced effectively utilizing volumetric cylinders 30 , 31 , 32 , 33 , and 34 created within dual cylinders.
  • Crank mechanism 10 a 's counterclockwise rotation of 0 to 180 degrees causes air from the intake and exhaust opening 26 to be taken into volumetric cylinders 33 , 34 depending on accompanied crank mechanisms' rotations.
  • crank mechanism 10 a 's rotation of 180 to 360 degrees causes air from volumetric cylinders 33 , 34 to be compressed and enclosed into volumetric cylinder 35 depending on accompanied crank mechanisms' rotations.
  • crank mechanism 10 a 's second rotation of 0 to 180 degrees causes compressed air within volumetric cylinder 35 to be once again compressed and then exhausted from intake and exhaust opening 27 depending on accompanied crank mechanisms' rotations.
  • This stroke shares both cylinders and is performed alternately. Namely, in the other cylinder, air from intake and exhaust opening 25 is taken into volumetric cylinders 30 , 31 . The air is then compressed and enclosed into volumetric cylinder 32 , and subsequently once again compressed and exhausted from intake and exhaust opening 28 .
  • FIG. 3 shows gas flow.
  • the gas taken into cylinder 31 and the gas taken into cylinder 30 are displaced into cylinder 32 , because cylinder 31 and cylinder 30 (gaps between the bottom portion of piston members 22 23 and the corresponding cylinder members 41 , 42 ) are reduced in volume due to the slide motion of piston members 22 , 23 toward the end wall portion of respective cylinder members 22 , 23 .
  • first crank mechanism 10 a and second crank mechanism 10 b are made to differ in length (namely, length of crank arm), there can be provided a phase difference between first piston member 22 and second piston member 21 , both performing slide motion in the same direction. That is, there can be provided a difference between the distance between the head portion of first piston member 22 and second piston member 21 when these heads have been displaced away from each other on one hand and that when they have approached each other on the other. This allows the gas that has been fed into cylinder 32 via air feed pipe to be compressed accompanied with the slide motion of first piston member 22 and second piston member 21 .
  • first cylinder member 41 corresponds to one cylinder member as recited in claims
  • second cylinder member 42 corresponds to the other cylinder.
  • Volumetric cylinder 31 corresponds to first gap as recited in claims
  • volumetric cylinder 30 corresponds to second gap
  • volumetric cylinder 33 corresponds to third gap
  • volumetric cylinder 34 corresponds to fourth gap
  • volumetric cylinder 35 corresponds to fifth gap
  • volumetric cylinder 32 corresponds to sixth gap.
  • a pair of volumetric cylinders 30 , 31 corresponds to first intake gap as recited in claims
  • volumetric cylinders 33 , 34 correspond to second intake gap.
  • Intake and exhaust openings 25 , 26 correspond to intake mechanism
  • intake and exhaust openings 27 , 28 correspond to exhaust mechanism
  • intake and exhaust openings 25 , 26 and intake and exhaust openings 27 , 28 correspond to intake and exhaust mechanism
  • air feed pipe 50 corresponds to intake mechanism and gas feed mechanism.
  • FIG. 5 is a view showing a piston type gas compressor 100 attached with power tool.
  • the force at the level of power tool 500 would be enough to obtain sufficient compressed air.
  • this piston type gas compressor 100 is not limited to dual cylinder type but could be of multi-cylinder type.
  • triple-cylinder type or quadruple-cylinder type could be implemented, and a multiple of two or 4 is preferable.
  • FIGS. 1, 2 , and 9 to 12 there will be described a piston type gas pressure drive rotation device 200 to be of the present invention.
  • a piston type gas pressure drive rotation device 200 is constituted by almost as same the structure as that of the piston type gas compressor.
  • piston shaft members 15 , 17 connected to second piston members 21 , 23 are disposed on either side of the piston shaft members 16 , 18 connected to first piston shaft members 22 , 24 in such a way as to put the shaft members 16 , 18 between piston shaft members 15 , 17 . Therefore, reciprocating slide motion in this case can be made smooth, as compared with the case of piston shaft members each consisting of one peace.
  • intake and the exhaust of gas into and out of each cylinder 41 , 42 are reversed.
  • intake and exhaust openings 25 , 26 constitute an intake opening respectively in a piston type gas compressor 100 , but constituting an exhaust opening in a piston type gas pressure drive rotation device, while, intake and exhaust openings 27 , 28 likewise constitute respectively an exhaust opening.
  • volumetric cylinders 30 , 31 , 32 , 33 , 34 , and 35 the intake and the exhaust of gas are reversed with respect to piston type gas compressor 100 . Therefore, feeding compressed gas into cylinders 32 and 35 can cause crankshaft 15 to rotate.
  • first cylinder member 41 corresponds to one cylinder member as recited in claims
  • second cylinder member 42 corresponds to the other cylinder member.
  • Volumetric cylinder 31 corresponds to a first gap as recited in claims
  • volumetric cylinder 30 corresponds to a second gap
  • volumetric cylinder 33 corresponds to a third gap
  • volumetric cylinder 34 corresponds to a fourth gap
  • volumetric cylinder 35 corresponds to a fifth gap
  • volumetric cylinder 36 corresponds to a sixth gap.
  • Intake and exhaust openings 25 , 26 correspond to an exhaust mechanism
  • intake and exhaust openings 27 , 28 correspond to an intake mechanism
  • intake and exhaust openings 25 , 26 and intake and exhaust openings 27 , 28 correspond to an intake and exhaust control mechanism
  • gas feed pipe 50 corresponds to a gas feed mechanism
  • FIG. 10 is a view of a tool to which the present invention is applied. As shown in the drawing, a simple tank would be enough to obtain sufficient rotational force.
  • FIG. 1 is a detailed plan view of a piston type gas pressure drive rotation device according to the present invention
  • FIG. 2 is a detailed plan view of a piston type gas pressure drive rotation device according to the present invention.
  • FIG. 3 is a view showing a gas flow of the piston type gas compressor
  • FIG. 4 is a perspective view of cylinder members constituting the piston type gas compressor
  • FIG. 5 is a photographic picture of a test model illustrative of an air compression structure according to the present invention (embodiment);
  • FIG. 6 is a detailed plan view showing a piston type gas compressor according to the present invention.
  • FIG. 7 is a detailed plan view showing a piston type gas compressor according to the present invention.
  • FIG. 8 is a detailed plan view showing a piston type gas compressor according to the present invention.
  • FIG. 9 is a view showing the gas flow of said piston type gas pressure drive rotation device
  • FIG. 10 is a view showing the state where the piston type gas pressure drive rotation device is applied to a tool
  • FIG. 11 is a view showing the state where the piston type gas pressure drive rotation device is applied to a vehicle.
  • FIG. 12 is a view showing the state where the piston type gas pressure drive rotation device is applied to a vehicle.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
US10/492,672 2001-10-17 2002-09-24 Piston type gas compressor, and piston type gas pressure drive rotation device Abandoned US20050042112A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2001-319036 2001-10-17
JP2001319036 2001-10-17
PCT/JP2002/009777 WO2003033909A1 (fr) 2001-10-17 2002-09-24 Compresseur a gaz du type a pistons et dispositif de rotation du type a pistons, entraine par la pression de gaz

Publications (1)

Publication Number Publication Date
US20050042112A1 true US20050042112A1 (en) 2005-02-24

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Application Number Title Priority Date Filing Date
US10/492,672 Abandoned US20050042112A1 (en) 2001-10-17 2002-09-24 Piston type gas compressor, and piston type gas pressure drive rotation device

Country Status (5)

Country Link
US (1) US20050042112A1 (zh)
EP (1) EP1437506A4 (zh)
JP (1) JP4129684B2 (zh)
CN (1) CN100344871C (zh)
WO (1) WO2003033909A1 (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009061443A1 (en) * 2007-11-08 2009-05-14 Us Airflow Compression apparatus
JP2013129831A (ja) * 2011-12-21 2013-07-04 Merck Patent Gmbh 効果顔料

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US593099A (en) * 1897-11-02 holst
US3704080A (en) * 1970-07-22 1972-11-28 Grosvenor M Cross Fluid engine
US5341725A (en) * 1993-06-14 1994-08-30 Dick James B Twin piston power cylinder
US6228153B1 (en) * 1998-07-21 2001-05-08 Micro Electronics Inc. Solvent delivery pump assembly

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62261602A (ja) * 1986-05-09 1987-11-13 Sanden Corp 圧力−機械変換装置
JPH0417827Y2 (zh) * 1986-11-28 1992-04-21
JPH03112583U (zh) * 1990-03-06 1991-11-18
JP3455763B2 (ja) * 1999-04-13 2003-10-14 株式会社中央技研工業 空気圧縮構造
JP2001207801A (ja) * 2000-01-26 2001-08-03 Akira Miyata ピストンポンプ式エンジン

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US593099A (en) * 1897-11-02 holst
US3704080A (en) * 1970-07-22 1972-11-28 Grosvenor M Cross Fluid engine
US5341725A (en) * 1993-06-14 1994-08-30 Dick James B Twin piston power cylinder
US6228153B1 (en) * 1998-07-21 2001-05-08 Micro Electronics Inc. Solvent delivery pump assembly

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009061443A1 (en) * 2007-11-08 2009-05-14 Us Airflow Compression apparatus
JP2013129831A (ja) * 2011-12-21 2013-07-04 Merck Patent Gmbh 効果顔料

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Publication number Publication date
JP4129684B2 (ja) 2008-08-06
EP1437506A4 (en) 2005-03-09
WO2003033909A1 (fr) 2003-04-24
JPWO2003033909A1 (ja) 2005-02-03
EP1437506A1 (en) 2004-07-14
CN1571885A (zh) 2005-01-26
CN100344871C (zh) 2007-10-24

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