EP1394413B1 - Compresseur à piston de taille réduite - Google Patents

Compresseur à piston de taille réduite Download PDF

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Publication number
EP1394413B1
EP1394413B1 EP02019521.0A EP02019521A EP1394413B1 EP 1394413 B1 EP1394413 B1 EP 1394413B1 EP 02019521 A EP02019521 A EP 02019521A EP 1394413 B1 EP1394413 B1 EP 1394413B1
Authority
EP
European Patent Office
Prior art keywords
piston
longitudinal axis
cylinder barrel
axis
cylinder
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Lifetime
Application number
EP02019521.0A
Other languages
German (de)
English (en)
Other versions
EP1394413A1 (fr
Inventor
Uwe Dr. Folchert
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Teves AG and Co OHG
Original Assignee
Continental Teves AG and Co OHG
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 Continental Teves AG and Co OHG filed Critical Continental Teves AG and Co OHG
Priority to EP02019521.0A priority Critical patent/EP1394413B1/fr
Priority to JP2003179945A priority patent/JP2004092638A/ja
Priority to KR1020030060173A priority patent/KR100935749B1/ko
Priority to US10/652,473 priority patent/US7179064B2/en
Publication of EP1394413A1 publication Critical patent/EP1394413A1/fr
Application granted granted Critical
Publication of EP1394413B1 publication Critical patent/EP1394413B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • 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
    • F04B39/0005—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 adaptations of pistons
    • F04B39/0022—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 adaptations of pistons piston rods
    • 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
    • F04B39/0094—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 crankshaft

Definitions

  • the present invention relates to a reciprocating compressor for gaseous media, in particular for a level control system in motor vehicles according to the preamble of claim 1.
  • Such a reciprocating compressor is known from the German patent DE19903025C2 known.
  • the reciprocating compressor for gaseous media described in this document has a movable piston within a cylinder. An outboard end of the piston is connected via a crankshaft to a drive shaft of an electric motor.
  • the reciprocating compressor and the drive device are each disposed in a compressor housing and a drive device housing. On the compressor housing a tubular, integrally formed with the compressor housing end piece is arranged in the region of the piston, wherein the compressor housing and the drive device housing are integrally formed.
  • the known from this document and designed in conventional design reciprocating compressor has the disadvantage of a large design and high friction of the piston ring on the cylinder bore, in particular in the intake stroke.
  • a reciprocating compressor which drives a piston engine via a drive motor.
  • a working space of a cylinder has a volume that pulsates between a minimum value and a maximum value.
  • inlet and outlet ports provided inlet and outlet ports, a medium is pushed in through the inlet and pushed out through the outlet.
  • the working space of the cylinder is preceded by a crankshaft housing enveloped by a crankshaft housing.
  • the crankshaft space is connected to the environment, wherein the air inlet valve is a rotary valve and is controllable in synchronism with the rotational movement of the crankshaft.
  • the rotary valve is preceded by a suction filter integrated into the intake manifold.
  • the intake manifold, the intake filter and the rotary valve form a single unit.
  • Also known from this document and designed in a conventional design reciprocating compressor has the disadvantage of a large design and high friction of the piston ring on the cylinder bore, in particular in the intake stroke.
  • the U.S. 4,848,213 discloses a piston compressor without oil lubrication, wherein the axis of the compression cylinder with respect to the axis of the crank mechanism with an "offset", so an offset is arranged so that minimizes the inclination of the piston and thus the friction between the piston seal and cylinder walls during the compression stroke becomes.
  • the offset consists essentially in a parallel displacement of the axes.
  • US 5,378,123 discloses such parallel displacement of the axles in a piston compressor for a coolant to further reduce the friction between piston seal and cylinder walls, in addition to self-lubricating properties of the piston seal.
  • the US 2,023,466 discloses a piston pump in which the piston rod or the piston surface are inclined to the axis of the compression cylinder, or in which the cylinder bottom is formed inclined.
  • the construction essentially serves to avoid air losses and the piston seal.
  • the FR 2 752 269 also discloses a compressor with such a parallel displacement of the axes of the crank mechanism relative to the axis of the compression cylinder, wherein further the piston surface is inclined to the axis of the piston rod. This should reduce both the dead volume in the compression stroke and the friction.
  • US 5 531 574 discloses a refrigerant compressor with a parallel displacement of the axes of the crank mechanism relative to the axis of the compression cylinder and a special material combination between the piston seal and cylinder material to reduce friction.
  • the DE 100 05 929 A1 discloses a compressor for an automotive air spring system in which the filling and compression processes in the compression are improved by a special valve formation in the crankcase.
  • the object of the invention is to provide a reciprocating compressor of improved design with low height and a reduced friction of the piston ring on the cylinder bore.
  • the surface of the end piece of the cylinder head, which is oriented toward the crankcase has a rounding formed in the direction of the piston.
  • the surface of the end piece of the cylinder head, so the cylinder base, which is oriented towards the crankcase thus with such a curve or curvature on a spherical or barrel-shaped contour, in which the outer surface of the curvature of the spherical or barrel-shaped contour oriented towards the crankcase is, so that the dead space (dead volume) is reduced and thus the performance and efficiency of the reciprocating compressor is increased
  • the longitudinal axis of the cylinder bore is pivoted relative to the first spatial axis.
  • One advantage is that thereby the pivot angle of the piston ring with respect to the cylinder bore can be best adapted in particular in the compression stroke and the maximum reduction of the height of the reciprocating compressor is achieved.
  • Another advantage is that the pivot angle of the piston ring relative to the cylinder bore, in particular in the compression stroke over the largest possible distance of the compression and / or intake stroke within a for the tightness of the piston ring to the cylinder bore, the piston ring wear and / or the piston ring life optimal range moves.
  • the maximum pivot angle of the piston ring longitudinal axis with respect to the longitudinal axis of the cylinder bore is smaller during the upward movement of the piston (compression stroke) than during the downward movement of the piston (suction stroke), wherein the longitudinal axis of the cylinder bore is offset with respect to the first spatial axis.
  • the pivot angle of the piston ring relative to the cylinder bore and thus the piston ring longitudinal axis relative to the longitudinal axis of the cylinder bore is limited in terms of deformation, pressure load and thus tightness of the piston ring to a maximum allowable value. This is especially true in the upward movement of the piston (the compression stroke), since then increased demands on deformation, pressure load and thus tightness of the contact point piston ring and cylinder bore are made.
  • the advantage of the invention is to be seen in particular in the fact that as a result the height of the reciprocating compressor can be reduced by reducing the length of the rod and correspondingly reduced length of the cylinder bore without unduly high stress on the piston ring and exceed the maximum allowable pivot angle in the compression stroke.
  • the reduced height of the reciprocating compressor can be achieved by reducing the connecting rod length and correspondingly reduced length of the cylinder bore, wherein the longitudinal axis of the cylinder bore is arranged offset from the first axis, so that the maximum swing angle of the piston ring relative to the cylinder bore in the compression stroke the maximum allowable value exceeds.
  • a further advantage of the invention is in particular to be seen in the fact that the maximum pivot angle in the intake stroke, where no increased requirement for the piston ring with respect to deformation, pressure load and tightness, is greater than the maximum permissible pivot angle, resulting in a reduction of friction and a Improvement of the suction process in the intake stroke leads.
  • the longitudinal axis of the cylinder bore is pivoted relative to the first spatial axis by an angle between 0.5 ° and 7 °.
  • the intersection of the longitudinal axis of the cylinder bore with the first spatial axis in the middle of the range of the up and down movement of the piston is within the cylinder bore.
  • the intersection of the longitudinal axis of the cylinder bore with the first axis of space in the upper reversal point of the piston is within the cylinder bore.
  • outlet opening with the material surrounding the outlet opening dips into the cylinder bore on one side and the plane of the end piece, which is oriented towards the crankcase, runs perpendicular to the first spatial axis.
  • the FIG. 1 describes a reciprocating compressor 10 in conventional construction.
  • the cylinder head 20 is integrally formed in this embodiment with a cylindrical member 56 and has an exhaust passage 22.
  • the outlet channel 22 is closed to the dryer housing 28 by an outlet valve 24 which consists of an elastomeric body, a leaf valve or the like.
  • One in the cylinder head 20 fastened valve spring 26 presses the outlet valve 24 at no or only a slight pressure drop on the sealing seat of the outlet channel 22 and closes it to the dryer housing 28 out.
  • the function of a dryer, in particular for air is well known and will not be described in detail here.
  • the cylindrical component 56 has a cylinder surface 58 with a high surface quality and is connected at one end to a crankcase 42.
  • the cylinder head 20 and the cylindrical member 56 may also be made of separate components.
  • the cylindrical member 56 may be manufactured inexpensively from a standard component such as a pipe. By means of a press connection or the like, the cylinder head 20 is connected to the cylindrical member 56.
  • crankshaft 38 In the crankcase 42, a crankshaft 38 is arranged, which is pressed with a pin in the inner ring of a bearing 36.
  • the outer ring of the bearing 36 is mounted in the Kurbelgekorsue.
  • the crankshaft 38 has a crankshaft journal 44, which serves to receive a bearing 40 and thus a connecting rod 50.
  • the bearing 40 is fixedly connected to the connecting rod 50 and is fixed to the crankshaft journal 44 by means of a screw 46 and a washer 48 or the like.
  • the connecting rod 50 has a longitudinal axis 64, which in this embodiment coincides with the longitudinal axis of a piston 60 fixedly connected to the connecting rod 50 and the longitudinal axis of a piston ring 54 fixed in the piston 60.
  • the piston 60 and / or the piston ring 54 may also have a different longitudinal axis of the longitudinal axis 60 of the connecting rod 50.
  • the piston 60 is designed together with the connecting rod 50 as a so-called oscillating piston, i. the piston 60 is rigidly connected to the connecting rod 50.
  • an inlet channel 62 is arranged, which connects the compression chamber with the space to the crankcase 42 out.
  • the intake passage 62 is closed at the time of upward movement of the piston 60 (compression stroke) from an intake valve 66 so that air can not flow from the compression space to the interior of the crankcase 42, and becomes in the downward movement of the piston 60th (Suction stroke) open, so that air can flow from the interior of the crankcase 42 to the compression chamber.
  • the inlet channel 62 and thus also the inlet valve 66 are arranged in the cylinder head 20.
  • the inlet valve 66 may, as shown in this embodiment, be designed as a leaf valve or in a known manner as an elastomeric valve body with or without valve spring.
  • the axis of symmetry of the bearing 36 coincides with a drive shaft 31 of a fixedly connected to the crankshaft 38 drive shaft 34 of the drive unit.
  • the drive unit is formed in this embodiment of an electric motor whose function is known and will not be described in detail. It is the use of any other known drive technology, such as a pneumatic or hydraulic drive, possible.
  • the drive shaft 34 of the electric motor is mounted on one side in the bearing 36 and on the other side in a bearing 32.
  • the bearing 32 is fixed in a motor housing 30 which is fixedly connected to the crankcase 42.
  • FIG. 2 schematically shows the kinematics of a reciprocating compressor.
  • a schematically represented piston 228 and a schematically illustrated connecting rod 230 are shown at top dead center of the piston 228.
  • a first spatial axis 222 intersects the upper reversal point 231 of the crankshaft journal 44 (see FIG. Fig.1 ) and a pivot 232 of the drive shaft 31 (see FIG. Fig.1 ).
  • a longitudinal axis 220 of the cylindrical member 56 and the cylinder barrel 58 intersects the pivot point 232 of the drive shaft 31 (s. Fig.1 ), but is pivoted relative to the first spatial axis 222 by an angle 238.
  • the pivot angle 238 is in a range between 0.5 ° and 7 °.
  • the pivot point of the crankshaft journal 44 (s. Fig.1 ) describes at a rotation through 360 ° about the pivot 232 of the drive shaft 31 (s. Fig.1 ) has a radius 234 which has a radius corresponding to the eccentricity of the crankshaft 38 (see Fig. 1).
  • the direction of movement 239 of the pivot point of the crankshaft journal 44 (S. Fig.1 ) runs counterclockwise.
  • Between the top of the piston 228 and the surface of the cylinder head 224 is the smallest possible gap, which represents the dead volume of the reciprocating compressor.
  • the surface of the cylinder head 224 is perpendicular to the first spatial axis 222. Also, a misalignment of this to first spatial axis 222 is possible, for example, the surface of the cylinder head 224 perpendicular to the longitudinal axis of the cylinder bore, so that the dead volume is minimized.
  • FIG. 2a also shows schematically the kinematics of a reciprocating compressor.
  • the piston 228 is shown in its bottom dead center.
  • the crankshaft journal 44 (s. Fig.1 ) is at its lower reversal point 235.
  • the range of movement 226 of the piston 228 extends from the bottom of the piston 228 at bottom dead center to the top of the piston 228 at top dead center.
  • the point of intersection 221 of the longitudinal axis 220 of the cylinder bore 58 with the first spatial axis 222 is within the cylinder bore and within a range of movement 226 of the piston 228th
  • FIG. 3 shows the piston 228 and the connecting rod 230 in the maximum pivotal position in the compression stroke.
  • the crankshaft (connection of the pivot point of the drive shaft 232 to the pivot point of the crankshaft journal) is perpendicular to the longitudinal axis 64 of the connecting rod 230.
  • the longitudinal axis 64 of the piston ring not shown, which is identical in this embodiment with the longitudinal axis of the piston 228 and the connecting rod 230 points relative to the longitudinal axis 220 of the cylinder bore 58 has a pivot angle 236.
  • the pivot angle 236 corresponds to the maximum pivot angle of the piston ring to the cylinder bore 58 in the compression stroke.
  • FIG. 4 shows the piston 228 and the connecting rod 230 in the maximum pivotal position in the intake stroke.
  • the crankshaft (connection of pivot point of the drive shaft 232 to the pivot point of the crankshaft journal) is perpendicular to the longitudinal axis 64 of the connecting rod 230.
  • the longitudinal axis 64 of the piston ring not shown, which in this embodiment is identical to the longitudinal axis 64 of the piston 228 and the connecting rod 230, has with respect to the longitudinal axis 220 of the cylinder bore 58 a pivot angle 240 on.
  • the swivel angle 240 corresponds to the maximum swivel angle of the piston ring to the cylinder bore 58 in the intake stroke.
  • the maximum pivot angle 236 in the compression stroke is smaller than the maximum pivot angle 240 in the intake stroke.
  • FIG. 5 shows the piston 228 and the connecting rod 230 in a position during the compression stroke just before top dead center.
  • the longitudinal axis 64 of the piston ring, the piston 228 and / or the connecting rod 230 is to the in Figure 5 in this embodiment, the piston 228 facing surface of the cylinder head 224 is round or cylindrical.
  • the outer contour of the rounding of the surface 224 points in each case in the direction of the piston, so that the dead volume is as small as possible.
  • the center of the curve or the longitudinal axis of the cylinder of the surface 224 lies on or preferably intersects the longitudinal axis 220 of the cylinder bore 58.
  • the first spatial axis 222 or a further axis the center of the rounding or the longitudinal axis of the cylinder the surface 224 intersects.
  • FIG. 6 schematically shows the kinematics of a reciprocating compressor.
  • the longitudinal axis 220 of the cylinder bore 58 is offset parallel to the first spatial axis 222 and does not intersect the pivot point 232 of the drive shaft 31 (s. Fig.1 ).
  • the cylindrical component 56 is offset parallel to the first spatial axis.
  • the parallel displacement of the longitudinal axis 220 to the first spatial axis 222 can be performed either so that the longitudinal axis 242 of the connecting rod 230 at two points during the suction stroke (as shown) or in two points during the compression stroke with the longitudinal axis 220 of the cylinder bore 58 match.
  • the longitudinal axis 242 of the connecting rod 230 and the longitudinal axis 244 of the piston 228 and / or the piston ring are not identical.
  • the axis 244 of the piston 228 and / or the piston ring have a different pivoting angle relative to the longitudinal axis 220 of the Cylinder runway 58, as the longitudinal axis 242 of the connecting rod 230.
  • the longitudinal axis 220 of the cylinder bore 58 coincides at top dead center with the longitudinal axis 244 of the piston or the piston ring, so that a very small dead volume.
  • the pivot angle and thus the pivoting of the longitudinal axis 244 of the piston ring with respect to the longitudinal axis 220 of the cylinder bore 58 may be oriented, for example, to a low maximum or a low amplitude, in particular during the compression stroke.

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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)

Claims (4)

  1. Compresseur à piston (10) pour milieux gazeux, en particulier pour une installation de régulation de niveau dans des véhicules automobiles, contenant :
    - une source d'entraînement et un carter de vilebrequin (42) qui sont connectés l'un à l'autre, un arbre d'entraînement (34) entraînant un vilebrequin (38) fixé sur celui-ci avec un tourillon de vilebrequin (44),
    - une culasse (20) qui est fixée au carter de vilebrequin (42),
    - au moins une ouverture de sortie (22) avec au moins une soupape de sortie (24) et au moins une ouverture d'entrée (62) avec au moins une soupape d'entrée (66),
    - un composant cylindrique (56) qui est fixé au carter de vilebrequin (42) et qui présente une surface de glissement de cylindre (58) située à l'intérieur, avec un axe longitudinal (220),
    - une bielle (50, 230) avec un piston (60, 228) connecté sur celle-ci avec un segment de piston (54), la bielle (50, 230) étant déplacée suivant un mouvement de va-et-vient par le vilebrequin (38) et donc le piston (60, 228) dans la surface de glissement de cylindre (58),
    - un premier axe spatial (222) qui coupe le centre (232) de l'arbre d'entraînement (34) et le centre du tourillon de vilebrequin (44) dans un point d'inversion supérieur (231) du tourillon de vilebrequin (44),
    l'angle de pivotement maximal (238, 240) de l'axe longitudinal du segment de piston (64, 244) par rapport à l'axe longitudinal (220) de la surface de glissement de cylindre (58) lors du mouvement vers le haut du piston étant inférieur à celui lors du mouvement vers le bas du piston (60, 228) et l'axe longitudinal (220) de la surface de glissement de cylindre (58) étant décalé par rapport au premier axe spatial (222), l'axe longitudinal (220) de la surface de glissement de cylindre (58) étant pivoté par rapport au premier axe spatial (222), caractérisé en ce que la surface (224) du bout de la culasse (20) qui est orientée vers le carter de vilebrequin (42) présente un arrondissement réalisé dans la direction du piston, et en ce que l'axe longitudinal (220) de la surface de glissement de cylindre (58) est pivoté par rapport au premier axe spatial (222) d'un angle compris entre 0,5° et 7°.
  2. Compresseur à piston (10) selon l'une quelconque ou plusieurs des revendications précédentes, caractérisé en ce que le point d'intersection de l'axe longitudinal (220) de la surface de glissement de cylindre avec le premier axe spatial (222) est situé dans la région du mouvement vers le haut et vers le bas (226) du piston (60, 228) à l'intérieur de la surface de glissement de cylindre (58).
  3. Compresseur à piston (10) selon l'une quelconque ou plusieurs des revendications précédentes, caractérisé en ce que le point d'intersection de l'axe longitudinal (220) de la surface de glissement de cylindre (58) avec le premier axe spatial (222) est situé au milieu de la région du mouvement vers le haut et vers le bas (226) du piston (60, 228) à l'intérieur de la surface de glissement de cylindre (58).
  4. Compresseur à piston (10) selon l'une quelconque ou plusieurs des revendications précédentes, caractérisé en ce que le point d'intersection de l'axe longitudinal (220) de la surface de glissement de cylindre (58) avec le premier axe spatial (222) est situé au point d'inversion supérieur du piston (60, 228) à l'intérieur de la surface de glissement de cylindre (58).
EP02019521.0A 2002-08-31 2002-08-31 Compresseur à piston de taille réduite Expired - Lifetime EP1394413B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP02019521.0A EP1394413B1 (fr) 2002-08-31 2002-08-31 Compresseur à piston de taille réduite
JP2003179945A JP2004092638A (ja) 2002-08-31 2003-06-24 低減された全高を有するガス状媒体のための往復ピストン圧縮機
KR1020030060173A KR100935749B1 (ko) 2002-08-31 2003-08-29 기체용 왕복 피스톤 압축기
US10/652,473 US7179064B2 (en) 2002-08-31 2003-09-02 Reciprocating piston compressor for a gaseous medium

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP02019521.0A EP1394413B1 (fr) 2002-08-31 2002-08-31 Compresseur à piston de taille réduite

Publications (2)

Publication Number Publication Date
EP1394413A1 EP1394413A1 (fr) 2004-03-03
EP1394413B1 true EP1394413B1 (fr) 2016-10-12

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EP02019521.0A Expired - Lifetime EP1394413B1 (fr) 2002-08-31 2002-08-31 Compresseur à piston de taille réduite

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Country Link
US (1) US7179064B2 (fr)
EP (1) EP1394413B1 (fr)
JP (1) JP2004092638A (fr)
KR (1) KR100935749B1 (fr)

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JP4752241B2 (ja) * 2004-11-01 2011-08-17 パナソニック株式会社 往復動式圧縮機
DE102005009947A1 (de) * 2005-03-04 2006-09-07 Wabco Gmbh & Co.Ohg Hubkolbenmaschine
DE102005061482A1 (de) * 2005-12-22 2007-07-05 Wabco Gmbh Hubkolbenmaschine
KR100718567B1 (ko) * 2006-11-27 2007-05-15 성주환 공기압축기용 바로크랭크축
WO2008096874A1 (fr) * 2007-02-09 2008-08-14 Daikin Industries, Ltd. Compresseur à piston
JP5094349B2 (ja) * 2007-11-30 2012-12-12 株式会社日立産機システム シリンダ装置、圧縮機およびシリンダ装置の製造方法
JP4872938B2 (ja) * 2008-02-08 2012-02-08 ダイキン工業株式会社 往復動圧縮機及び酸素濃縮装置
US20100158715A1 (en) * 2008-12-24 2010-06-24 Min-Hsieng Wang Mute compressor
US20110076164A1 (en) * 2009-09-25 2011-03-31 Wen San Chou Air compressor having tilted piston
CN102042191B (zh) * 2009-10-15 2013-06-12 周文三 空气压缩机
JP5380353B2 (ja) * 2010-04-14 2014-01-08 株式会社日立産機システム 往復動圧縮機
BR112012029261A2 (pt) 2010-05-19 2017-12-12 Graco Minnesota Inc conjunto de bomba.
DE102010054709A1 (de) 2010-12-16 2012-06-21 Wabco Gmbh Lufttrockner-System, Druckluftversorgungsanlage, pneumatisches System und Verfahren zum Betreiben einer Pneumatikanlage
TWI531721B (zh) * 2011-01-25 2016-05-01 周文三 空氣壓縮機
JP5374524B2 (ja) * 2011-01-26 2013-12-25 住友ゴム工業株式会社 コンプレッサ装置
DE102012005345B4 (de) 2011-12-23 2024-02-08 Zf Cv Systems Hannover Gmbh Druckluftversorgungsanlage, Druckluftversorgungssystem, Fahrzeug und Verwendung der Druckluftversorgungsanlage
DE102012024757A1 (de) 2012-12-19 2014-06-26 Wabco Gmbh Ringförmiges Dichtungselement, Ventil, Druckluftversorgungsanlage, Druckluftversorgungssystem und Fahrzeug
JP5565490B1 (ja) * 2013-03-26 2014-08-06 東亜ディーケーケー株式会社 送液ポンプ
DE102014116805A1 (de) * 2014-11-17 2016-05-19 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Kompressor mit anpassbarer Übersetzung zur Antriebsquelle
CN107476952A (zh) * 2016-06-08 2017-12-15 谈宇 新传动结构节能压缩机
CN107476950B (zh) * 2016-06-08 2024-02-27 谈宇 活塞力作功节能压缩机
DE102016013036A1 (de) 2016-11-02 2018-05-03 Wabco Gmbh Hubkolbenmaschine, insbesondere ein-, zwei- oder mehrstufiger Kolbenkompressor, Druckluftversorgungsanlage, Druckluftversorgungssystem und Fahrzeug, insbesondere PKW mit einer Druckluftversorungsanlage, Verfahren zur Montage einer Hubkolbenmaschine und Verfahren zum Betrieb einer Hubkolbenmaschine, insbesondere an einer Druckluftversorgungsanlage.
JP7449061B2 (ja) 2019-10-01 2024-03-13 株式会社日立産機システム 圧縮機
JP2022019099A (ja) * 2020-07-17 2022-01-27 株式会社日立産機システム レシプロ機構及びレシプロ機構を備えた機器
JP2022021164A (ja) * 2020-07-21 2022-02-02 株式会社日立産機システム 圧縮機
US11767840B2 (en) 2021-01-25 2023-09-26 Ingersoll-Rand Industrial U.S. Diaphragm pump

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JP2004092638A (ja) 2004-03-25
US20040042919A1 (en) 2004-03-04
US7179064B2 (en) 2007-02-20
EP1394413A1 (fr) 2004-03-03
KR100935749B1 (ko) 2010-01-06
KR20040020037A (ko) 2004-03-06

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