EP2191133A1 - Machine à pistons alternatifs - Google Patents

Machine à pistons alternatifs

Info

Publication number
EP2191133A1
EP2191133A1 EP08785113A EP08785113A EP2191133A1 EP 2191133 A1 EP2191133 A1 EP 2191133A1 EP 08785113 A EP08785113 A EP 08785113A EP 08785113 A EP08785113 A EP 08785113A EP 2191133 A1 EP2191133 A1 EP 2191133A1
Authority
EP
European Patent Office
Prior art keywords
guide body
pin
guide
engine according
reciprocating piston
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.)
Granted
Application number
EP08785113A
Other languages
German (de)
English (en)
Other versions
EP2191133B1 (fr
Inventor
Jan Hinrichs
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.)
ixetic Bad Homburg GmbH
Original Assignee
Ixetic Mac GmbH
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 Ixetic Mac GmbH filed Critical Ixetic Mac GmbH
Publication of EP2191133A1 publication Critical patent/EP2191133A1/fr
Application granted granted Critical
Publication of EP2191133B1 publication Critical patent/EP2191133B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1063—Actuating-element bearing means or driving-axis bearing means
    • 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
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1072—Pivot mechanisms

Definitions

  • the invention relates to a reciprocating engine according to the preamble of claim 1.
  • Reciprocating engines of the type discussed here are known. They are used in particular in connection with coolant compressors for regulating the passenger compartment temperature in motor vehicles. They have a preferably designed as a pivot ring pivot element, which is connected via at least one pin with a preferably designed as a guide sleevesammlungsammlungsungskör- per.
  • the guide body is arranged coaxially to a shaft and guided against this displaceable.
  • the pivoting element can thus perform a pivoting movement relative to the shaft and cause a movement of at least one piston which is slidably mounted in a cylinder bore of the reciprocating engine.
  • the first end of the at least one pin, via which the guide body is in communication with the pivot element, is mounted with play in a guide bore in the guide body.
  • Object of the present invention is therefore to provide a reciprocating engine, in which malfunction caused by forces acting on the pivot member can be avoided.
  • a reciprocating engine which has the features mentioned in claim 1. It is characterized by the fact that acting on the pivot member forces are introduced into the jacket of the guide body.
  • the advantageous embodiment of the present invention causes a reduction in the friction of the guide body on the shaft and thereby wear and malfunction of the reciprocating engine.
  • caused by friction between the pin and the guide body wear and deformation is avoided, which can lead to tilting of the pin in the guide bore.
  • By the introduction of forces directly into the shell of the guide body acting on the pivot element operating forces are introduced as pure compressive forces and not as moments in the shell of the guide body, as is the case with known reciprocating engines. Overuse of the module addressed here is thus avoided.
  • a reciprocating engine which is characterized in that the at least one pin is pressed with its second end in the pivot member. This embodiment makes it possible to guide the pin with its first end with play in a guide bore of the guide body.
  • a reciprocating engine which is characterized in that the at least one pin has a two-plane at its second end. This embodiment prevents expansion by existing in the operating room operating forces acting on the pivot member.
  • a reciprocating engine which is characterized in that at least one bearing sleeve is provided between the pivot member and the guide body, which is arranged around the at least one pin around.
  • the bearing sleeve essentially serves to support the pivoting element in a pivoting movement about the guide body around this and to dampen vibrations caused by the pivoting movement of the pivoting element.
  • the at least one bearing sleeve has a larger diameter than the guide bore, in which the at least one pin is mounted in the guide body. This embodiment causes the introduction of forces directly into the shell of the guide body.
  • Another preferred reciprocating engine is characterized in that the at least one bearing sleeve is formed integrally with the guide body or the pivot member. It can also be provided to weld the bearing sleeve with the guide body or the pivot member.
  • a reciprocating engine which is characterized in that an end face of the first end of the at least one pin which is mounted in the guide bore of the guide body, between an outer circumferential surface and an inner circumferential surface of the guide body is arranged.
  • a reciprocating engine which is characterized in that the end face of the first end of the at least one pin, which is mounted in the guide bore of the guide body, between the shaft and the inner circumferential surface of the guide body is arranged.
  • the end face of the first end of the at least one pin is therefore outside the guide bore in this embodiment, so that forces are introduced even more effectively directly into the shell, whereby jamming of the guide body and wear and tear are avoided.
  • FIG. 1 shows a section through an assembly of a reciprocating engine.
  • the single FIGURE shows an assembly 1, which is arranged in the operating room of a reciprocating engine.
  • the assembly 1 comprises a shaft 3, on which a guide body 5 is arranged coaxially and is guided displaceably on the shaft 3.
  • the guide body 5 is exemplified here as a guide sleeve.
  • a driver element 9 is pressed into a bore 7, which is perpendicular to the image plane of the figure.
  • the driver element 9 engages through a non-illustrated elongated recess in the guide body 5 in a pivot member 11, which is exemplified in the figure as a pivot ring. Rotation of the shaft 3 thus also causes, via the driver element 9, rotation of the pivoting element 11 and of the guide body 5.
  • the oblong recess (not shown) in the guide body 5 enables the coaxial displaceability of the guide body 5 on the shaft 3, if this is about one Rotary axis D rotates.
  • the figure makes it clear that at least one, here two pins 13 are provided which connect the pivot member 11 with the guide body 5.
  • the pin 13 is mounted to a first end 15 with a game 17 in a guide bore 19 of the guide body 5 and pressed with a second end 21 in the pivot member 11.
  • the second end 21 of the pin 13 has, as can not be seen here, a two-fold, which is aligned parallel to sliding surfaces 23 and 25 of the pivot member 11 in order to prevent expansion of the pivot member.
  • a bearing sleeve 27 is arranged, which preferably surrounds the pin 13 completely.
  • the bearing sleeve 27 may be formed integrally with the guide body 5 or with the pivot member 11, but it is also conceivable to weld the bearing sleeve 27 with the guide body 5 or the pivot member 11.
  • the bearing sleeve 27 preferably has a larger inner diameter than the guide bore 19, in which the first end 15 of the pin 13 is arranged.
  • an end face 29 of the first end 15 of the pin 13 is arranged outside the guide bore 19, so that the end face 29 is arranged between the shaft 3 or between the outer peripheral surface 31 and an inner circumferential surface 33 of the guide body 5.
  • Both embodiments cause the direct introduction of forces in the shell 37 of the guide body 5, ie in the region of the guide body between the inner lateral surface 33 and the outer lateral surface 35. This ensures that only a compressive force and no moment exerted on the guide body 5 is, so that a deformation of the guide body 5 and thus wear and jamming of the guide body 5 on the shaft 3 are substantially reduced.
  • these resulting forces Fi 'and F 2 ' are introduced directly into the shell 37 of the guide body 5, so that they act as pure compressive forces, so that a deformation of the guide body 5 is avoided.
  • the end face 29 of the first end 15 of the pin 13 between the inner circumferential surface 33 and the outer lateral surface 35 or between the peripheral surface 31 of the shaft 3 and the inner circumferential surface 33 is arranged and the bearing sleeve 27 has a larger inner diameter than the guide bore 19 , the resulting forces FT and F 2 'are introduced directly into the jacket 37 of the guide body 5.

Landscapes

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

Abstract

L'invention concerne une machine à pistons alternatifs, notamment pour des véhicules automobiles, comprenant un élément pivotant (11) qui est réalisé de préférence sous forme de bague pivotante et qui est relié par l'intermédiaire d'au moins une tige (13) à un corps de guidage (5) disposé coaxialement à un arbre (3) et mobile en translation par rapport à ce dernier. Une première extrémité (15) de la tige au moins unique (13) est montée avec jeu (17) dans un alésage de guidage (19) dans le corps de guidage (5).
EP08785113A 2007-08-22 2008-07-25 Machine à pistons alternatifs Not-in-force EP2191133B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007039724 2007-08-22
PCT/EP2008/006161 WO2009024248A1 (fr) 2007-08-22 2008-07-25 Machine à pistons alternatifs

Publications (2)

Publication Number Publication Date
EP2191133A1 true EP2191133A1 (fr) 2010-06-02
EP2191133B1 EP2191133B1 (fr) 2013-04-03

Family

ID=39735386

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08785113A Not-in-force EP2191133B1 (fr) 2007-08-22 2008-07-25 Machine à pistons alternatifs

Country Status (3)

Country Link
EP (1) EP2191133B1 (fr)
DE (1) DE112008002028A5 (fr)
WO (1) WO2009024248A1 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19749727C2 (de) * 1997-11-11 2001-03-08 Obrist Engineering Gmbh Lusten Hubkolbenmaschine mit Schwenkscheibengetriebe
DE10335159A1 (de) * 2003-07-31 2005-02-17 Zexel Valeo Compressor Europe Gmbh Axialkolbenverdichter, insbesondere CO2-Verdichter für Kraftfahrzeug-Klimaanlagen
DE112005002570A5 (de) * 2004-11-05 2007-07-12 Ixetic Mac Gmbh Hubkolbenmaschine
DE102005004840A1 (de) * 2005-02-02 2006-08-10 Valeo Compressor Europe Gmbh Axialkolbenverdichter
DE102005018102A1 (de) * 2005-04-19 2005-11-03 Zexel Valeo Compressor Europe Gmbh Axialkolbenverdichter

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009024248A1 *

Also Published As

Publication number Publication date
WO2009024248A1 (fr) 2009-02-26
EP2191133B1 (fr) 2013-04-03
DE112008002028A5 (de) 2010-07-22

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