EP2505838B1 - Compresseur à piston - Google Patents

Compresseur à piston Download PDF

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Publication number
EP2505838B1
EP2505838B1 EP11002717.4A EP11002717A EP2505838B1 EP 2505838 B1 EP2505838 B1 EP 2505838B1 EP 11002717 A EP11002717 A EP 11002717A EP 2505838 B1 EP2505838 B1 EP 2505838B1
Authority
EP
European Patent Office
Prior art keywords
crank
crankshaft
pin
crank pin
screw
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.)
Active
Application number
EP11002717.4A
Other languages
German (de)
English (en)
Other versions
EP2505838A1 (fr
Inventor
Peter Mißfeldt
Peter Dahms
Wolfgang Wiegers
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.)
JP Sauer and Sohn Machinenbau GmbH
Original Assignee
JP Sauer and Sohn Machinenbau 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 JP Sauer and Sohn Machinenbau GmbH filed Critical JP Sauer and Sohn Machinenbau GmbH
Priority to EP11002717.4A priority Critical patent/EP2505838B1/fr
Priority to ES11002717.4T priority patent/ES2449700T3/es
Priority to IN965DE2012 priority patent/IN2012DE00965A/en
Priority to US13/435,566 priority patent/US8939047B2/en
Priority to CN2012101018060A priority patent/CN102734128A/zh
Publication of EP2505838A1 publication Critical patent/EP2505838A1/fr
Application granted granted Critical
Publication of EP2505838B1 publication Critical patent/EP2505838B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B39/0094—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
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/006—Crankshafts
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2173—Cranks and wrist pins
    • Y10T74/2174—Multiple throw
    • Y10T74/2175—Sectional

Definitions

  • the invention relates to a reciprocating compressor.
  • crank mechanism It is common practice to drive reciprocating compressors via a crank mechanism.
  • the movement coupling of a piston of the reciprocating compressor with a crankshaft takes place via a connecting rod mounted on a crankpin of the crankshaft.
  • the connecting rod bearing is usually designed as an oil-lubricated slide bearing.
  • crankshaft In dry-running reciprocating compressors, the use of such oil-lubricated plain bearings is not possible. Here instead rolling bearings must be used as a rod bearing.
  • the crankshaft can be made in several parts, i. be designed as a so-called built crankshaft. After mounting the bearings, the individual parts of the crankshaft are assembled into the complete crankshaft.
  • crankshaft is connected to a crank pin with a crank arm characterized in that a tapered in the direction of the crank arm portion of the pin engages in a formed on an end portion of the crank arm recess which tapers corresponding to the taper of the end portion of the crank pin, wherein the crank pin is clamped by means of a screw connection between crank pin and crank arm.
  • the end section of the crank pin and the recess on the crank arm have a non-circular cross-section.
  • FR 610 596 A is a built-crankshaft described, are connected to the crank pin and a crank arm by means of a conical connection.
  • a pin lock is provided, wherein a locking pin engages in a bore formed on the crankshaft, which is arranged such that it has a recess for receiving an end portion of the crank pin and in the recess located tangent tangent end portion of the crank pin.
  • the invention has for its object to provide a reciprocating compressor with a multi-part crankshaft whose parts can be releasably connected to each other in a simple and cost-effective manner.
  • the reciprocating compressor according to the invention has at least one piston that is moved by a crankshaft.
  • the crankshaft is formed at least in two parts.
  • crankshaft such a division of the crankshaft is expediently provided, wherein at least a first part of the crankshaft in the unassembled state of the crankshaft forms a free end of a crank pin of the crankshaft, while on the second part of the crankshaft an angrerizende crank pin crank web is formed.
  • All parts of the crankshaft may be formed, for example, as cast or forged parts.
  • the free end of the first part of the crankshaft makes it possible to arrange a rolling bearing on the crankpin before assembling the crankshaft.
  • the at least two parts of the crankshaft are connected to each other by means of a conical connection. Accordingly, manufacturing technology simply the end of one of the parts to be joined together conical or frustoconical design and the other part correspondingly provided with a hollow cone-shaped recess. To connect the two parts, the first part is simply inserted with the conical end in the hollow cone-shaped recess of the second part and the two parts then clamped together, with the two parts center in the axial direction itself and only one component to the other component in terms the required angular orientation of the two adjoining the Hupzapfen crank webs must be aligned.
  • the inventive design of the crankshaft not only allows a quick and easy initial assembly of the crankshaft but also later disassembly for maintenance or repair purposes.
  • a crank pin and a crank arm of the crankshaft are connected by means of the conical connection.
  • one end of a first part of the crankshaft is formed by a crank pin, while a crank arm forms one end of a second part of the crankshaft.
  • the free end of the crank pin preferably tapers conically, while on the crank arm, which forms an end of the second part of the crankshaft, a conical outside Recess is formed, which extends transversely to the longitudinal extent of the crank arm.
  • the first and the second part of the crankshaft can be screwed together.
  • the conical connection forming areas of crank pin and crank arm are braced by means of a screw.
  • This screw is expediently arranged and aligned in such a way that it pulls the conical end of the crank pin into the design formed on the crank cheek during a screwing movement for bracing the conical connection.
  • crank pin In a tensioned by screw conical connection between crank pin and crank arm an embodiment is preferred in which the screw engages through the crank arm in the axial direction of the crank pin and engages in an end portion of the crank pin. That is, in the crank pin, a threaded blind hole is preferably formed, while in the crank arm, a through hole is formed, which extends completely through the crank arm in the axial direction of the crank pin and transverse to the longitudinal extent of the crank arm.
  • the through hole formed on the crank web and the threaded blind hole formed on the crank pin are in alignment, so that a screw guided through the through bore of the crank web can now be screwed into the threaded blind hole of the crank pin , Where a head of the screw coming to rest on the crank arm presses the crank arm against the crank pin and braces the crank arm with the crank pin.
  • the through-hole preferably has a larger diameter than the screw, so that it has play in the through hole and centering takes place via the conical connection.
  • the screw preferably engages centrally in the crank pin. Accordingly, a center axis of the crank pin and a center axis of the threaded bolt hole formed on the crankpin coincide.
  • the screw forms an axis of rotation about which the second part of the crankshaft with the crank arm can be rotated relative to the first part of the crankshaft with the crank pin and vice versa for the exact alignment of the first part relative to the second part with not yet completely screwed screw.
  • crank arm and crank pin are secured by means of an additional rotation.
  • the rotation lock is expediently formed by positive locking elements, which engage at the same time in the crank arm and the crank pin substantially, transversely to a possible direction of rotation of the second part of the crankshaft relative to the first part.
  • the invention provides that at least one locking pin penetrating the crank arm and engaging in the crank pin forms the security against rotation.
  • a bore is formed on the crank web and formed on the crank pin a blind hole, wherein the blind hole on the crank pin with proper alignment of the first part of the crankshaft relative to the second part in direct extension to the bore on the crank arm, i. Is arranged coaxially with the bore of the crank arm.
  • the at least one locking pin radially spaced from the screw axially parallel to the crank pin engages through the crank arm and engages in the crank pin. Accordingly, the locking pin is guided in a bore extending from the side facing away from the crankpin side of the crank arm laterally next to the screw for bracing the two parts of the crankshaft and parallel to a longitudinal axis of this screw and extending parallel to the central axis of the crank pin through the crank arm and into the crank pin adjacent thereto.
  • the locking pin is arranged axially parallel to the crank pin, it is also arranged axially parallel to a rotational axis of the crankshaft. This is advantageous in that the locking pin is aligned transversely to the moments to be transmitted.
  • two locking pins are preferably provided. These two locking pins are advantageously aligned axially parallel to the crank pin and preferably arranged such that they engage in the crank pin diametrically opposite one another.
  • the leading through the crank arm in the crank pin holes for receiving the locking pins both extend in a plane in which the central axis of the crank pin lies, wherein the two locking pins are arranged on two opposite sides of the central axis of the crank pin and preferably each one same Distance from the central axis of the journal.
  • the bore for receiving the at least one securing pin is preferably made after the assembly of the conical connection, i. formed after the alignment of the two parts of the crankshaft and their tension with each other.
  • the bore in the crank arm and the blind hole in the crank pin can be formed simultaneously aligned with each other.
  • the bore or holes for receiving the locking pin or the locking pins are thus prepared when the two parts of the crankshaft have their final position to each other.
  • they can then each be made quickly and easily in one drilling operation.
  • adjusting surfaces are to each of the parts to be interconnected with the crankshaft relative alignment of these parts formed to each other.
  • These adjusting surfaces are each flat surfaces on an outer side of these parts of the crankshaft, which are arranged so that the parts of the crankshaft to be joined together, when the Justier vom rest on a flat reference surface, exactly the required orientation to each other.
  • the reciprocating compressor is a two-stage, dry-running reciprocating compressor with two cylinders 3 and 5. To drive the piston arranged in these cylinders 3 and 5, the latter are each connected via an unillustrated connecting rod with the In Fig. 2 shown crankshaft motion coupled.
  • crankshaft journals 2 and 4 which define an axis of rotation A of the crankshaft.
  • crankshaft has two cranks 6 and 8.
  • the first crank 6 of the crankshaft directly adjoining the shaft journal 2 is formed by two crank webs 10 and 12 projecting radially outwards with respect to the shaft journals 2 and 4, which are connected via a crank pin 14 whose central axis B radially from the common center axis A of the shaft journal 2 and 4 is spaced apart, are interconnected.
  • the second crank 8 is from the crank arm 12, a further parallel to the crank arm 12 aligned crank arm 16 and a crank webs 12 and 16 connecting crank pin 18 is formed.
  • a central axis C of the crank pin 18 is radially spaced in the opposite direction to the central axis B of the crank pin 14 from the central axis A of the shaft journals 2 and 4.
  • the crankshaft is formed in three parts.
  • the shaft journal 2 and the crank arm 10 form a first part of the crankshaft
  • the crank pin 14 with the crank arm 12 and the crank pin 18 a second part of the crankshaft
  • the crank arm 16 and the shaft journal 4 a third part of the crankshaft.
  • the three parts of the crankshaft are each connected by means of conical connections.
  • the three-part design of the crankshaft makes it possible to mount roller bearings on the crank pins 14 and 18.
  • an end portion 20 of the crank pin 14 tapers conically.
  • a recess 22 is formed on the crank arm 10 on the side remote from the shaft journal 2, which also tapers conically.
  • the crank pin 14 engages with its end portion 20 in the formed on the crank arm 10 recess 22 a. In this position, the crank pin 14 is clamped to the crank arm 10 with a screw 24.
  • this screw 24 extends through the crank web 10 and engages in the crank pin 14 at the front side.
  • a bore 26 is formed on the crank web 10, which extends transversely to the longitudinal extent of the crank arm 10 through the crank web 10 therethrough.
  • a shaft 2 facing the end portion 29 of the bore 26 is formed radially widened and serves to receive a screw head of the screw 24 designed as a hexagon socket screw.
  • alignment surfaces 30 and 32 are formed on the crank webs 10 and 12, respectively, on an outer side aligned substantially transversely to the central axis B of the crank pin 14. With proper alignment of the first and second parts of the crankshaft, the alignment surfaces 30 and 32 lie flat on a flat, not shown, reference surface.
  • the connection of the crank pin 14 with the crank arm 10 is secured by means of a rotation.
  • the anti-rotation is formed by two locking pins 34 and 36, which is arranged in each case in a crank arm 10 by breaking and engaging in the crank pin 14 bore.
  • the locking pin 34 is disposed in a bore 38 and the locking pin 36 in a bore 40.
  • the central axes of the holes 38 and 40 are in a common plane with the central axis B of the crank pin 14, wherein the holes 38 and 40 on opposite sides of the screw 24 and radially spaced from the screw 24 are arranged diametrically opposite one another.
  • the bores 38 and 40 are formed for receiving the locking pins 34 and 36 in the assembled, shown in the drawing state of the crankshaft, ie when the second part of the crankshaft with the crank pin 14 with the first part of the crankshaft with the Crankshaft 10 are clamped together by means of the screw 24 and the first and the second part of the crankshaft have the required relative orientation to each other.
  • the portions of the bores 38 and 40 provided in the crank web 10 and in the crank pin 14 can each be formed jointly in one drilling operation.
  • the conical connection between the second and the third part of the crankshaft substantially corresponds to the conical connection between the first and the second part of the crankshaft.
  • a side facing away from the crank arm 12 end portion 42 of the crank pin 18 tapers conically.
  • a hollow cone-shaped recess 44 is formed on the crank arm 16 on the side remote from the shaft journal 4, in which engages the conical end portion 42 of the crank pin 18.
  • a screw 46 which, like the screw 24, is designed as a hexagon socket screw
  • the second part of the crankshaft is clamped to the third part of the crankshaft.
  • a bore 48 is formed on the crank web 16 and a threaded blind hole 50 is formed on the crank pin 18 on the face side.
  • a common center axis of bore 48 and threaded blind hole 50 coincides with the central axis C of the crank pin 18.
  • an end portion 52 of the bore 48 facing away from the crank pin 18 is radially widened.
  • the connection of the crank pin 18 with the crank arm 16 is secured by means of a rotation in the form of locking pins 54 and 56 against unwanted rotational movement of the two parts relative to each other.
  • the locking pin 54 is in a bore 58 and the locking pin 56 is disposed in a bore 60.
  • the holes 58 and 60 are arranged at a radial distance on opposite sides of the screw 46 diametrically opposite one another.
  • the center axes of the holes 58 and 60 lie in a common plane with the central axis C of the crank pin 18.
  • the holes 58 and 60 are suitably formed in the assembled state of the crankshaft, namely, when the third part of the crankshaft is connected to the second part ,

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Claims (5)

  1. Compresseur à piston comprenant au moins un piston couplé en mouvement à un vilebrequin, lequel est réalisé en au moins deux parties et présente un maneton (14, 18) et un flasque de vilebrequin (10, 16) qui sont reliés au moyen d'un raccord conique, les régions du maneton (14, 18) et du flasque de vilebrequin (10, 16) formant le raccord conique étant serrées à l'aide d'une vis (24, 46) qui traverse le flasque de vilebrequin (10, 16) dans la direction axiale du maneton (14, 18) et s'engage dans une partie d'extrémité (20, 42) du maneton (14, 18), et la liaison du flasque de vilebrequin (10, 16) et du maneton (14, 18) étant dotée d'une sécurité anti-rotation formée d'au moins une goupille de sécurité (34, 36, 54, 56) traversant le flasque de vilebrequin (10, 16) et s'engageant dans le maneton (14, 18), caractérisé en ce que la goupille de sécurité (34, 36, 54, 56) traverse le flasque de vilebrequin (10, 16) et s'engage dans le maneton (14, 18) d'une manière parallèle à l'axe du maneton (14, 18) et radialement espacée de la vis (24, 46).
  2. Compresseur à piston selon la revendication 1, caractérisé en ce que la vis (24, 46) s'engage de manière centrée dans le maneton (14, 18).
  3. Compresseur à piston selon l'une des revendications précédentes, caractérisé en ce que sont prévues deux goupilles de sécurité (34, 36, 54, 56) qui sont disposées de façon à s'engager dans le maneton (14, 18) de manière diamétralement opposée.
  4. Compresseur à piston selon l'une des revendications précédentes, caractérisé en ce qu'est prévu dans le maneton (14, 18) et le flasque de vilebrequin (10, 16) un alésage (38, 40, 58, 60) destiné à recevoir la goupille de sécurité (34, 36, 54, 56), au moins au nombre de une, lequel alésage a été réalisé après le montage du raccord conique.
  5. Compresseur à piston selon l'une des revendications précédentes, caractérisé en ce que des surfaces de réglage (30, 32) sont formées sur chacune des parties du vilebrequin à relier entre elles pour l'alignement relatif de ces parties l'une par rapport à l'autre.
EP11002717.4A 2011-04-01 2011-04-01 Compresseur à piston Active EP2505838B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP11002717.4A EP2505838B1 (fr) 2011-04-01 2011-04-01 Compresseur à piston
ES11002717.4T ES2449700T3 (es) 2011-04-01 2011-04-01 Compresor de pistón
IN965DE2012 IN2012DE00965A (fr) 2011-04-01 2012-03-30
US13/435,566 US8939047B2 (en) 2011-04-01 2012-03-30 Piston compressor
CN2012101018060A CN102734128A (zh) 2011-04-01 2012-04-01 活塞式压缩机

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11002717.4A EP2505838B1 (fr) 2011-04-01 2011-04-01 Compresseur à piston

Publications (2)

Publication Number Publication Date
EP2505838A1 EP2505838A1 (fr) 2012-10-03
EP2505838B1 true EP2505838B1 (fr) 2013-11-27

Family

ID=43920321

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11002717.4A Active EP2505838B1 (fr) 2011-04-01 2011-04-01 Compresseur à piston

Country Status (5)

Country Link
US (1) US8939047B2 (fr)
EP (1) EP2505838B1 (fr)
CN (1) CN102734128A (fr)
ES (1) ES2449700T3 (fr)
IN (1) IN2012DE00965A (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104421131B (zh) * 2013-08-22 2016-08-24 珠海格力节能环保制冷技术研究中心有限公司 压缩机、空调及热泵热水器系统
CN104653590B (zh) * 2013-11-22 2017-07-21 刘运武 一种组合式偏心轴

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US852447A (en) * 1906-12-05 1907-05-07 Carl J Mellin Return-crank for valve-gears.
CH93365A (de) * 1920-01-16 1922-03-16 Skf Svenska Kullagerfab Ab Zusammengesetzte Kurbelwelle.
US1690296A (en) * 1920-12-22 1928-11-06 Hirth Albert Crank shaft
FR610596A (fr) * 1925-02-06 1926-09-08 Manivelles et organes analogues avec paliers à rouleaux à chaîne
US2190411A (en) * 1939-03-14 1940-02-13 Berman G Kielmeyer Sectional crankshaft
DE717230C (de) * 1939-08-03 1942-02-09 Maschf Augsburg Nuernberg Ag Mehrteilige Kurbelwelle
US2566785A (en) * 1946-08-16 1951-09-04 Ben W Wheelis Crankshaft construction
US2471982A (en) * 1946-11-04 1949-05-31 Shulda Melvin Splice for crankshaft bearings
US3309941A (en) * 1965-07-15 1967-03-21 James C Kappel Sectional crankshaft
US4913033A (en) * 1986-10-07 1990-04-03 Martin Bernas Steam engine
DE10337247B4 (de) * 2003-08-13 2005-07-14 Man B & W Diesel A/S Kurbelwelle

Also Published As

Publication number Publication date
EP2505838A1 (fr) 2012-10-03
CN102734128A (zh) 2012-10-17
US8939047B2 (en) 2015-01-27
US20120251364A1 (en) 2012-10-04
IN2012DE00965A (fr) 2015-09-11
ES2449700T3 (es) 2014-03-20

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