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WO2018143233A1 - Compresseur de gaz du type à piston alternatif - Google Patents

Compresseur de gaz du type à piston alternatif Download PDF

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Publication number
WO2018143233A1
WO2018143233A1 PCT/JP2018/003095 JP2018003095W WO2018143233A1 WO 2018143233 A1 WO2018143233 A1 WO 2018143233A1 JP 2018003095 W JP2018003095 W JP 2018003095W WO 2018143233 A1 WO2018143233 A1 WO 2018143233A1
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WO
WIPO (PCT)
Prior art keywords
compression
compression chamber
cylinder
introduction holes
type gas
Prior art date
Application number
PCT/JP2018/003095
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English (en)
Japanese (ja)
Inventor
陽介 小川
藤岡　完
Original Assignee
アネスト岩田株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by アネスト岩田株式会社 filed Critical アネスト岩田株式会社
Publication of WO2018143233A1 publication Critical patent/WO2018143233A1/fr

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Classifications

    • 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
    • F04B35/01—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 the means being mechanical
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections

Definitions

  • the present disclosure relates to a reciprocating piston type gas compressor that compresses gas by reciprocating a piston inserted in a cylinder.
  • a so-called reciprocating piston type gas compressor in which gas is compressed in a compression chamber formed by a cylinder and a piston by reciprocating a piston inserted in the cylinder.
  • the piston descends to generate a negative pressure in the compression chamber, and the negative pressure introduces a gas to be compressed from the intake port into the compression chamber.
  • the compression step of compressing the gas by raising the piston is repeated periodically.
  • Patent Document 1 discloses an example of a reciprocating piston type gas compressor.
  • an intake port for introducing gas into the compression chamber and a discharge port for discharging compressed gas from the compression chamber are provided adjacent to the cylinder above the cylinder.
  • a layout is disclosed.
  • the intake port is provided with an introduction hole communicating with the intake introduction side and the pressure chamber in parallel to the cylinder axis.
  • One of the basic performance requirements for compressors is to improve volumetric efficiency.
  • it is effective to improve the cylinder pressure at the end of the intake process.
  • the pressure in the cylinder at the end of the intake process depends on the magnitude of the negative pressure generated in the cylinder at the time of intake. was there.
  • Patent Document 1 when the inlet hole of the intake port is provided in parallel to the cylinder axis, the gas introduced into the compressor from the inlet hole collides with the inner wall of the cylinder or piston constituting the compression chamber. There is also a situation in which the kinetic energy of gas is easily wasted due to friction and friction, and a certain amount of energy loss cannot be avoided.
  • the conventional reciprocating piston type gas compressor has a limit in improving the volume efficiency, and has a limit in reducing the energy consumption per unit gas amount.
  • At least one embodiment of the present invention has been made in view of the above circumstances, and provides a reciprocating piston type gas compressor capable of reducing energy consumption per unit gas amount by having a superior volume efficiency. With the goal.
  • a reciprocating piston type gas compressor includes a cylinder and a piston that is inserted in the cylinder so as to be reciprocable and forms a compression chamber together with the cylinder.
  • An intake port having a plurality of introduction holes for introducing gas into the compression chamber, and a discharge port having a discharge hole for discharging the gas compressed in the compression chamber. The hole is opened toward a compression region set in the compression chamber.
  • the gas to be compressed is introduced into the compression chamber through the plurality of introduction holes.
  • the gas introduced from each introduction hole collides with each other in the compression region as a jet.
  • the kinetic energy of the jet is converted into pressure energy, and the gas is compressed.
  • Collision compression by such a jet improves the cylinder internal pressure at the end of the intake process.
  • compression exceeding the conventional mechanical limit becomes possible, and more excellent volumetric efficiency can be obtained.
  • a reciprocating piston type gas compressor capable of reducing energy consumption per unit gas amount can be realized. .
  • the plurality of introduction holes are concentrically arranged around the compression region.
  • the jets from the plurality of introduction holes collide locally in the compression region in the intake process. be able to. Thereby, in the compression region, more advanced collision compression is performed, and more excellent volume efficiency is obtained.
  • the plurality of introduction holes are provided in the compression chamber from the top surface of the piston when the piston is at top dead center.
  • the side surface of the cylinder is opened so as to be exposed to the compression chamber.
  • the plurality of introduction holes are provided on the side surface of the cylinder.
  • these introduction holes are not exposed to the compression chamber, and then are only exposed to the compression chamber when the piston is lowered to some extent. Yes. Therefore, immediately after the start of the intake process, gas is not introduced from the plurality of introduction holes, and the formation of negative pressure is promoted in the sealed compression chamber.
  • gas is introduced from the plurality of introduction holes into the compression chamber by the negative pressure formed so far. Since such gas introduction is performed by the large negative pressure accumulated so far, a strong jet is formed. In this way, since a jet having a larger kinetic energy can be formed, collision compression is promoted, and a reciprocating piston type gas compressor having more excellent volume efficiency can be realized.
  • the compression region is configured such that the discharge hole is formed from the top surface of the piston when the piston is at bottom dead center. It is set close.
  • the compression region is set so as to include the discharge holes, and the discharge holes have a concave shape when viewed from the plurality of introduction holes. .
  • the discharge hole included in the compression region has a concave shape (dent shape) when viewed from the introduction hole, the jets ejected from the plurality of introduction holes are within the concave shape of the discharge hole. Collide with each other. Therefore, the jet flow does not escape to the surroundings at the time of collision, and collision compression is performed efficiently.
  • the plurality of introduction holes are formed obliquely with respect to a side surface of the cylinder so as to go to the compression region. ing.
  • the compression hole can be flexibly set at various positions in the compression chamber by forming the introduction hole obliquely on the side surface of the cylinder.
  • the compression region is set so as to be biased from a central portion of the compression chamber.
  • a swirl flow is formed in the compression chamber by the gas introduced from the plurality of introduction holes.
  • the gas impingingly compressed in the compression region is dispersed toward the entire compression region by such a swirling flow, and contributes to an increase in pressure in the entire compression chamber.
  • new gas is continuously supplied from the plurality of introduction holes to the compression region.
  • the gas whose pressure has been increased by the collision compression is dispersed by the swirl flow, so that the compression is compressed. Gas does not stay in the area. Therefore, the collision compression of new gas can be continuously performed in the compression region, and more excellent volume efficiency can be obtained.
  • a reciprocating piston type gas compressor capable of reducing energy consumption per unit gas amount by having a superior volume efficiency.
  • FIG. 1 is a cross-sectional view showing an overall configuration of a reciprocating piston-type gas compressor 1 according to at least one embodiment of the present invention
  • FIG. 2 is an enlarged cross-sectional view in the vicinity of a compression chamber 6 in FIG.
  • the reciprocating piston type gas compressor 1 includes a cylinder 2 and a piston 4 inserted into the cylinder 2 so as to be able to reciprocate.
  • the cylinder 2 has a substantially cylindrical side surface 2a and a top surface 2b provided on one end side.
  • the side surface 2 a and the top surface 2 b of the cylinder 2 form a compression chamber 6 together with the top surface 4 a of the piston 4 inserted inside the cylinder 2.
  • the crankcase 8 is connected to the lower side of the cylinder 2.
  • a crankshaft 14 is rotatably supported in the crankcase 8 via a bearing 15.
  • the crankshaft 14 is connected to a drive shaft 12 of an electric motor 10 installed outside the crankcase 8 and is configured to be rotatable by the electric motor 10.
  • the crankshaft 14 is connected to the piston 4 via a piston rod 16.
  • the reciprocating piston gas compressor 1 includes an intake port 18 for introducing gas into the compression chamber 6.
  • the intake port 18 communicates with an intake passage 20 (generally referred to as a first intake passage 20a and a second intake passage 20b described later) that communicates with the outside to which a gas to be compressed is taken in, and the intake passage 20.
  • the intake passage 20 of the present embodiment includes a first intake passage 20a that communicates with the outside, and a plurality of second intake passages 20b that branch from the first intake passage 20a to the plurality of introduction holes 22, respectively. , Including.
  • Each of the second intake passages 20b is provided with a check intake valve 24 for suppressing the backflow of the gas flowing through the intake passage 20.
  • the check suction valve 24 can be opened and closed based on an internal / external differential pressure, and is configured to open when the negative pressure in the compression chamber 6 exceeds a predetermined value in the intake process.
  • a reed valve, a rotary valve, a solenoid valve, or the like may be used.
  • the plurality of introduction holes 22 are open toward the compression region 30 set in the compression chamber 6.
  • the introduction hole 22 opens along a horizontal direction perpendicular to the cylinder axis C (FIG. 2).
  • gas is introduced into the compression chamber 6 through the introduction holes 22 due to the negative pressure generated when the piston 4 descends in the cylinder 2. Since each introduction hole 22 opens toward the compression region 30, the gas introduced from the introduction hole 22 is ejected toward the compression region 30.
  • the plurality of introduction holes 22 are arranged concentrically around the compression region 30. Therefore, the gas ejected from each introduction hole 22 locally collides with each other in the compression region 30 as a jet as shown in FIG. Then, the kinetic energy which a jet has is converted into pressure energy, and gas compression is performed. Since the collision compression by the jet flow contributes to the improvement of the cylinder internal pressure at the end of the intake process, it is effective for improving the volumetric efficiency of the reciprocating piston type gas compressor 1, and is therefore effective for reducing energy consumption. .
  • the compression region 30 is set on the cylinder axis C, and the distance from each introduction hole 22 to the compression region 30 is set to be equal to each other. Therefore, the jets ejected from the plurality of introduction holes 22 are configured to collide evenly in the compression region 30 so that the above-described collision compression is effectively performed.
  • the gas compressed in the compression chamber 6 is discharged to the outside through the discharge port 32.
  • the discharge port 32 includes a discharge chamber 36 that communicates with the compression chamber 6 via a discharge hole 34, and a discharge passage 38 that communicates from the discharge chamber 36 to the outside.
  • a check discharge valve 40 for suppressing the backflow of gas from the compression chamber 6 is provided on the discharge chamber 36 side of the discharge hole 34.
  • the check discharge valve 40 can be opened and closed based on the internal and external differential pressures, and is configured to open when the pressure in the compression chamber 6 exceeds a predetermined value in the compression process.
  • a reed valve, a rotary valve, a solenoid valve, or the like may be used.
  • the discharge hole 34 is provided in the top surface 2b of the cylinder 2.
  • the compression region 30 is set closer to the discharge hole 34 in the cylinder 2 (more specifically, as shown in FIG. 3, the compression region 30 is formed when the piston 4 is at the bottom dead center. , It is set closer to the discharge hole 34 than the top surface 4a of the piston 4).
  • FIG. 3 is a sectional view showing the operation in the intake process of the reciprocating piston type gas compressor 1 of FIG. 1 for each process.
  • a part of the configuration shown in FIGS. 1 and 2 is omitted for easy understanding.
  • FIG. 3A shows an initial state at the start of the intake process.
  • the piston 4 In the initial state, the piston 4 is at the top dead center, and then starts to descend toward the bottom dead center in the cylinder 2.
  • the pressure in the compression chamber 6 decreases as the volume of the compression chamber 6 increases, and negative pressure is generated.
  • the plurality of introduction holes 22 are positioned below the upper surface 4 a of the piston 4, and thus the plurality of introduction holes 22 are formed in the compression chamber 6. Not exposed to. Therefore, at this time, no gas is introduced into the compression chamber 6 from the plurality of introduction holes 22, and the formation of negative pressure is promoted in the compression chamber 6 in a sealed state as the piston 6 descends.
  • FIG. 3 (c) shows the area
  • FIG. 3C the high pressure region extending from the compression region 30 is indicated by reference numeral 35 in order to easily show how such a region having a high pressure expands.
  • the pressure Pex2 in the high pressure region 35 is lower than the pressure Pex1 in the compression region 6 in FIG. 3B, but is higher than the pressure Pcy0 in the peripheral region (that is, Pcy0 ⁇ Pex2 ⁇ Pex1).
  • FIG. 4 is a cross-sectional view showing the operation in the intake process of the reciprocating piston type gas compressor 1 ′ according to the prior art for each process.
  • symbol corresponding to the above-mentioned reciprocating piston type gas compressor 1 shall be attached
  • the reciprocating piston type gas compressor 1 ′ is provided with one introduction hole 22 ′ constituting the intake port 18 on the top surface 2 b of the cylinder 2.
  • the introduction hole 22 ′ is provided in parallel to the cylinder axis C.
  • the check suction valve 24 ′ provided outside the introduction hole 22 ′ (on the compression chamber 6 side) opens, and the gas to be compressed enters the compression chamber 6 from the introduction hole 22 ′. be introduced.
  • the gas flows along the inner wall of the cylinder 2 from the introduction hole 22 ′ and then winds upward near the approximate center of the top surface 4 a of the piston 4.
  • the inside of the compression chamber 6 is filled.
  • the compression chamber 6 when negative pressure is generated in the compression chamber 6 due to the piston 4 descending in the cylinder 2 in the intake process, the compression chamber 6 is connected to the object to be compressed via the plurality of introduction holes 22. A gas is introduced. Since the plurality of introduction holes 22 are opened toward the compression region 30 set in the compression chamber 6, the gas introduced from each introduction hole 22 collides with each other in the compression region 30 as a jet. Then, the kinetic energy of the jet is converted into pressure energy, and the gas is compressed. Collision compression by such a jet improves the cylinder internal pressure at the end of the intake process. As a result, the compression exceeding the conventional mechanical limit becomes possible, and the reciprocating piston type gas compressor 1 capable of reducing the energy consumption per unit gas amount can be realized by having a more excellent volumetric efficiency.
  • FIG. 5 is a cross-sectional view showing the operation of the reciprocating piston gas compressor 1 ′ according to the first modification in the intake process for each process.
  • the components corresponding to the above-described reciprocating piston type gas compressor 1 will be denoted by the same reference numerals, and overlapping description will be omitted as appropriate.
  • a plurality of introduction holes 22 provided in the side surface 2 a of the cylinder 2 are formed obliquely.
  • the inclination angles of the plurality of introduction holes 22 are set so that the jets ejected from the introduction holes 22 are directed to the compression region 30 set so as to include the discharge holes 34.
  • the compression region 30 is set so as to include the discharge holes 34, so that further compression can be promoted. That is, as shown in FIG. 5, since the check discharge valve 40 is disposed in the discharge hole 34 on the downstream side (discharge chamber 36 side), a concave shape (that is, a hollow shape) is formed when viewed from the introduction hole 22. Have. Therefore, the jets ejected from the plurality of introduction holes 22 collide with each other within the concave shape of the ejection hole 40. Therefore, the jet flow at the time of the collision does not escape to the surroundings, and the gas can be efficiently compressed by the collision of the jet flow.
  • a plurality of introduction holes 22 are provided on the lower side of the cylinder 2 as compared with the above-described embodiment, so that the initial stage of the intake process (the plurality of introduction holes 22 are exposed to the compression chamber 6).
  • a larger negative pressure can be formed. More specifically, as shown in FIG. 5A, when the piston 4 is at the top dead center at the start of the intake process, the plurality of introduction holes 22 are located below the top surface 4a of the piston 4. Therefore, the plurality of introduction holes 22 are not exposed to the compression chamber 6. Therefore, at this time, no gas is introduced into the compression chamber 6 from the plurality of introduction holes 22, and the formation of negative pressure is promoted in the compression chamber 6 in a sealed state as the piston 6 descends.
  • the plurality of introduction holes 22 are caused by the negative pressure formed so far. From this, gas is introduced into the compression chamber 6.
  • the negative pressure formed in the compression chamber 6 by the time the gas introduction by the introduction holes 22 is started is larger (that is, the introduction holes).
  • the negative pressure increases by the amount of time required until 22 is exposed). Therefore, the gas introduced into the compression chamber 6 from the plurality of introduction holes 22 is blown toward the compression region 30 more vigorously based on a large internal / external differential pressure. In this way, since a jet having a larger kinetic energy is formed, collision compression in the compression region 30 is promoted.
  • the check discharge valve 40 opens and the compressed gas is discharged.
  • the inside of the compression chamber 6 finally becomes the pressure Pcy1 ′′.
  • the pressure Pcy1 ′′ of the compression chamber 6 in FIG. 5C is higher than the pressure Pcy1 of the compression chamber 6 in FIG. 3D (that is, Pcy1 ′′> Pcy1). This is because in the first modified example, since the magnitude of the negative pressure formed in the compression chamber 6 is increased before the gas is ejected from the plurality of introduction holes 22, collision compression is performed more effectively. .
  • FIG. 6 is a cross-sectional view schematically showing the internal structure of a reciprocating piston-type gas compressor 1 ′′ according to a second modification.
  • the components corresponding to the above-described reciprocating piston type gas compressor 1 will be denoted by the same reference numerals, and overlapping description will be omitted as appropriate.
  • the compression region 30 is set on the cylinder axis C (the central portion of the compression chamber 6) as described above.
  • the compression region 30 is set. May be set so as to deviate from the center of the compression chamber 6.
  • the center of the compression region 30 is set so as to be deviated in the radial direction with respect to the cylinder axis C.
  • a swirl flow R is formed in the compression chamber 6 by the gas introduced from the plurality of introduction holes 22.
  • the high pressure gas impingingly compressed in the compression region 30 is dispersed toward the entire compression region 30 by such a swirl flow R.
  • the case where the plurality of introduction holes 22 are opened in the side surface 2a of the cylinder 2 is illustrated, but is formed so as to be opened in the top surface 2b of the cylinder 2 or the top surface 4a of the piston 4. May be.
  • the cylinder internal pressure can be improved by causing the jets ejected from the plurality of introduction holes 22 to collide with each other in the compression region 30.
  • the intake passage 20 has an asymmetric shape with respect to the cylinder axis C is illustrated, but these may have a symmetrical shape with respect to the cylinder axis C.
  • collision compression can be more effectively performed by suppressing variations in jet flow from the plurality of introduction holes 22 and causing the jet flows to collide evenly in the compression region 30.
  • the second intake passage 20b is directly branched from the first intake passage 20a.
  • An intake chamber for temporarily storing the introduced gas may be provided between the first intake passage 20a and the second intake passage 20b.
  • static pressure in the intake chamber, variation in jets from the plurality of introduction holes 22 is suppressed, and jets collide evenly in the compression region 30, thereby improving the cylinder internal pressure more effectively. Can be expected.
  • the plurality of introduction holes 22 may be configured to be exposed to the compression chamber 6 when the piston 4 is at the top dead center (that is, at the start of the intake process). In this case, when the piston 4 starts to descend in the cylinder 2 in the intake process, gas introduction into the compression chamber 6 from the plurality of introduction holes 22 is immediately started by the negative pressure generated in the compression chamber 6. Thereby, a large total amount introduced into the compression chamber 6 in the intake process can be ensured, and more excellent volume efficiency can be obtained.
  • the present disclosure can be used for a reciprocating piston type gas compressor that compresses gas by reciprocating a piston inserted in a cylinder.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

La présente invention concerne un compresseur de gaz du type à piston alternatif, le compresseur comprenant : un cylindre ; un piston introduit dans le cylindre afin de pouvoir effectuer un mouvement alternatif à l'intérieur du cylindre et formant une chambre de compression conjointement avec le cylindre ; un orifice d'admission comportant une pluralité de trous d'introduction servant à introduire un gaz dans la chambre de compression ; et un orifice d'évacuation comportant un trou d'évacuation servant à évacuer le gaz comprimé dans la chambre de compression. Les trous d'introduction sont ouverts vers une région de compression établie à l'intérieur de la chambre de compression.
PCT/JP2018/003095 2017-02-01 2018-01-31 Compresseur de gaz du type à piston alternatif WO2018143233A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017017083A JP2018123773A (ja) 2017-02-01 2017-02-01 往復ピストン式気体圧縮機
JP2017-017083 2017-08-08

Publications (1)

Publication Number Publication Date
WO2018143233A1 true WO2018143233A1 (fr) 2018-08-09

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Application Number Title Priority Date Filing Date
PCT/JP2018/003095 WO2018143233A1 (fr) 2017-02-01 2018-01-31 Compresseur de gaz du type à piston alternatif

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JP (1) JP2018123773A (fr)
WO (1) WO2018143233A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4829405U (fr) * 1971-08-13 1973-04-11
JPS5779276A (en) * 1980-10-31 1982-05-18 Hitachi Koki Co Ltd High-speed reciprocating compressor
JPS5816818A (ja) * 1981-07-08 1983-01-31 Bando Chem Ind Ltd 化粧材の製造方法
JPH0335900Y2 (fr) * 1986-06-23 1991-07-30
US20130327212A1 (en) * 2010-12-10 2013-12-12 Reinhold Ficht Cylinder of a reciprocating piston machine and reciprocating piston machine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4829405U (fr) * 1971-08-13 1973-04-11
JPS5779276A (en) * 1980-10-31 1982-05-18 Hitachi Koki Co Ltd High-speed reciprocating compressor
JPS5816818A (ja) * 1981-07-08 1983-01-31 Bando Chem Ind Ltd 化粧材の製造方法
JPH0335900Y2 (fr) * 1986-06-23 1991-07-30
US20130327212A1 (en) * 2010-12-10 2013-12-12 Reinhold Ficht Cylinder of a reciprocating piston machine and reciprocating piston machine

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