EP3221584B1 - Compresseur avec rapport de transmission ajustable enevrs les moyens d'entraînement - Google Patents

Compresseur avec rapport de transmission ajustable enevrs les moyens d'entraînement Download PDF

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Publication number
EP3221584B1
EP3221584B1 EP15794204.6A EP15794204A EP3221584B1 EP 3221584 B1 EP3221584 B1 EP 3221584B1 EP 15794204 A EP15794204 A EP 15794204A EP 3221584 B1 EP3221584 B1 EP 3221584B1
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EP
European Patent Office
Prior art keywords
crankshaft
compressor
gear
driving means
connecting rod
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
EP15794204.6A
Other languages
German (de)
English (en)
Other versions
EP3221584A1 (fr
Inventor
Gilles Hebrard
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.)
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
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Publication of EP3221584A1 publication Critical patent/EP3221584A1/fr
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Publication of EP3221584B1 publication Critical patent/EP3221584B1/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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
    • F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
    • 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
    • F04B39/0094—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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/0002—Cylinder arrangements
    • F02F7/0019—Cylinders and crankshaft not in one plane (deaxation)

Definitions

  • the invention relates to a compressor which is connected to a drive source by a gear transmission.
  • Air compressors for commercial vehicles generally convert a rotary movement provided by the drive source (engine) of at least one piston, which moves up and down in a cylinder and compresses the air during this movement. This conversion takes place by means of a connecting rod which is rotatably mounted on the piston with a connecting rod eye and which is rotatably mounted eccentrically on a crankshaft with another connecting rod eye.
  • the crankshaft is rotated by the drive source through a gear ratio.
  • the gear ratio is constant so that the working speed of the compressor changes with the engine speed.
  • the compressor is generally designed so that it can still supply the required compressed air requirement of the vehicle at its system pressure even when the vehicle engine is idling.
  • the compressor must fit into an installation volume specified by the vehicle design, and the crankshaft must have a gearwheel for the power transmission that fits into a gearwheel present on the drive source.
  • the operating parameters of the compressor are more or less fixed and must be accepted by the user, even if they are not optimal in terms of noise or energy consumption.
  • a compressor In the context of the invention, a compressor was developed. This has a crankcase in which a crankshaft is rotatably mounted in a crankcase.
  • the crankcase contains at least one cylinder space in which a piston, which is mounted eccentrically on the crankshaft by a connecting rod, can be excited to reciprocate.
  • the crankshaft is connected to a drive source by a gear transmission that has a modulus m, in that the gearwheel arranged on the crankshaft engages in the gearwheel on the drive source.
  • the axis of rotation of the crankshaft is offset from the central axis of the cylinder space by an amount d1, which is an integral multiple of m / 2.
  • the central axis of the cylinder space is understood to mean the axis extending from the center of the base area of the cylinder space perpendicular to this base area, along which the piston moves.
  • the transmission ratio of the transmission can be changed to an advantageous range without having to make changes to the external dimensions of the compressor or to the drive source.
  • the gear of the drive source does not have to be changed. If the gear of the drive source has a number Z 1 of teeth and the meshing gear of the crankshaft has a number Z 2 of teeth, then the distance between the axes of rotation of the gears is given by m ⁇ (Z 1 + Z 2 ) / 2, where m is the modulus of the transmission. This modulus is a measure of the size of the teeth.
  • the claimed offset between the axis of rotation of the crankshaft and the central axis of the cylinder space is introduced, the number of teeth Z 2 of the gear on the crankshaft and thus also the transmission ratio of the transmission can be changed without having to make changes to the drive source.
  • the number of teeth remains an integral number, particularly in the case of the claimed offset, so that complex adaptation measures on the gear wheels are not required.
  • the claimed feature of the integer multiple of m / 2 is not to be interpreted purely mathematically, but expressly also includes distances dl that deviate from an integer multiple of m / 2 only to such an extent that the gearwheel of the crankshaft within the mechanical tolerances can still mesh with the gear of the drive source without changes in the size of the teeth for the purpose of power transmission.
  • the transmission advantageously has a transmission ratio between 1 to 0.9 and 1 to 1.1 from the drive source to the crankshaft.
  • the typical motors for heavy commercial vehicles provide a gearwheel with a modulus value between 1.5 and 3.5 mm for driving a compressor.
  • the gear ratio by which the number of teeth Z 2 of the gear on the crankshaft is changed can thus be changed by 2 to 3%.
  • the transmission ratio is therefore advantageously greater than 1, ie Z 2 is less than Z 1 .
  • the piston of the compressor moves faster. Given the specifications for the air output per unit of time (for example 200 liters per minute at 12 bar system pressure and 700 revolutions per minute of the engine), less piston stroke in the cylinder is then required to achieve this output.
  • the compressor can be made more compact. Because of the limited space in the engine compartment, the piston displacement is a constant bottleneck. Typically only 360 to 400 cm 3 are available per cylinder.
  • the connecting rod eye of the connecting rod which is rotatably mounted against the crankshaft, is advantageously freely movable in a circle around the axis of the crankshaft. Wear caused by bearing forces is particularly low. Furthermore, this configuration takes up particularly little space in the crankcase of the crankcase.
  • the axis of rotation of the crankshaft is advantageously offset from the central axis of the cylinder space by an amount dl between 1 and 5 mm, preferably between 2 and 3 mm. Then the effect can additionally be exploited that the deflection of the connecting rod from the central axis of the cylinder is reduced when the crankshaft rotates about its axis. This deflection applies a force component to the piston, which presses against the wall of the cylinder and thus increases the wear due to friction between the cylinder and the piston.
  • the invention offers the advantage that compressors of a limited range of performance classes with a high proportion of identical parts can be manufactured inexpensively.
  • To adjust the power only the offset dl between the axis of rotation of the crankshaft and the central axis of the cylinder has to be adjusted.
  • FIG 1 shows a schematic diagram of a compressor according to the invention.
  • a cylinder bore 1a in the crankcase 1.5 Their central axis is labeled X.
  • a piston 2 moves in the cylinder bore. It is connected to the crankshaft 4 via a connecting rod 3.
  • the connecting rod has two connecting rod eyes 3a and 3b.
  • the upper connecting rod eye 3a is rotatably supported against the piston 2.
  • the lower connecting rod eye 3b is rotatably supported against a crank pin 4a which rotates with the crankshaft 4 about its central axis Y. If the crankshaft 4 rotates, the lower connecting rod eye 3b of the connecting rod 3 describes a circle around the central axis Y of the crankshaft 4.
  • the axes X and Y run perpendicular to one another; the X axis runs in the drawing plane, the Y axis perpendicular to the drawing plane. However, both axes are shifted parallel to each other by an amount dl.
  • the crankshaft 4 is rotatably supported against the part 5 of the crankcase 1.5.
  • the effect of the parallel displacement dl is shown in the integration of the compressor into an engine compartment Figure 2 ,
  • the motor block 9 with fixed dimensions is located at a predetermined location and provides a predetermined gear wheel 8 for driving the compressor.
  • the gearwheel rotates about an axis Z which is perpendicular to the plane of the drawing and is at a distance A from the central axis X of the cylinder space which runs in the plane of the drawing.
  • the crankshaft 4 is from driven a gear 7 that engages in the gear 8 on the engine block 9. This gear 7 rotates about the axis Y, which is the axis of symmetry of the crankshaft 4 and is perpendicular to the plane of the drawing.
  • the axes Y and Z are at a distance B from one another which is smaller than the distance A.
  • the gear 7 therefore has a number Z 2 of teeth which is smaller than the number Z 1 of the gear 8 on the engine block 9.
  • the gear 7 thus rotates faster than the gear 8.
  • the flange 6, with which it is mounted in the engine compartment, is also located at the same location as in a compressor according to the prior art, the gear 7 of which was the same size as the gear 8.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Claims (5)

  1. Compresseur ayant un carter (1, 5) de manivelle, dans lequel un arbre (4) de manivelle est monté tournant dans un espace de manivelle, le carter (1, 5) de manivelle comportant au moins un espace (1a) cylindrique, dans lequel un piston (2), monté de manière excentrée sur l'arbre (4) de manivelle par une bielle (3), peut être excité en un mouvement de va-et-vient et dans lequel l'arbre (4) de manivelle est relié par une transmission (7, 8) à engrenage, qui a un module m, à une source (9) d'entraînement, par le fait que la roue (7) dentée, disposée sur l'arbre (4) de manivelle, engrène dans la roue (8) dentée de la source (9) d'entraînement, l'axe (Y) de rotation de l'arbre (4) de manivelle étant, par rapport à l'axe (X) médian de l'espace (1a) cylindrique, décalé d'un montant dl,
    caractérisé en ce que le montant dl est un multiple en nombre entier de m/2 et dl est compris entre 1 et 5 mm.
  2. Compresseur suivant la revendication 1,
    caractérisé en ce que la transmission (7, 8) a un rapport de multiplication compris entre 1:09 et 1:1,1 de la source (9) d'entraînement à l'arbre (4) de manivelle.
  3. Compresseur suivant l'une des revendications 1 à 2,
    caractérisé en ce que le rapport de multiplication est plus grand que 1.
  4. Compresseur suivant l'une des revendications 1 à 3,
    caractérisé en ce que le pied (3b), monté tournant de la bielle (3), est mobile librement suivant un cercle autour de l'axe (Y) de l'arbre (4) de manivelle.
  5. Compresseur suivant l'une des revendications 1 à 4,
    caractérisé en ce que l'axe (Y) de rotation de l'arbre (4) de manivelle est, par rapport à l'axe (X) médian de l'espace (1a) cylindrique, décalé d'un montant dl compris entre 2 et 3 mm.
EP15794204.6A 2014-11-17 2015-11-16 Compresseur avec rapport de transmission ajustable enevrs les moyens d'entraînement Active EP3221584B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014116805.4A DE102014116805A1 (de) 2014-11-17 2014-11-17 Kompressor mit anpassbarer Übersetzung zur Antriebsquelle
PCT/EP2015/076636 WO2016079031A1 (fr) 2014-11-17 2015-11-16 Compresseur à transmission réglable à la source d'entraînement

Publications (2)

Publication Number Publication Date
EP3221584A1 EP3221584A1 (fr) 2017-09-27
EP3221584B1 true EP3221584B1 (fr) 2020-01-15

Family

ID=54541092

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15794204.6A Active EP3221584B1 (fr) 2014-11-17 2015-11-16 Compresseur avec rapport de transmission ajustable enevrs les moyens d'entraînement

Country Status (7)

Country Link
US (1) US10753349B2 (fr)
EP (1) EP3221584B1 (fr)
JP (1) JP2017534802A (fr)
CN (1) CN107110139B (fr)
BR (1) BR112017009922A2 (fr)
DE (1) DE102014116805A1 (fr)
WO (1) WO2016079031A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1025648B1 (nl) * 2017-10-19 2019-05-20 Paul Uyttersprot Schuine opstelling van de cilinder tegenover de krukas
DE102017011615A1 (de) 2017-12-15 2019-06-19 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Antriebsanordnung für einen Kompressor eines Nutzfahrzeugs
CN112324634B (zh) * 2020-10-28 2021-07-13 西安交通大学 一种侧向力自动平衡的往复式压缩机

Family Cites Families (22)

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Publication number Priority date Publication date Assignee Title
DE2302800C2 (de) 1973-01-20 1982-12-16 Klöckner-Humboldt-Deutz AG, 5000 Köln Hubkolbenbrennkraftmaschine mit Luftpresser
US3985475A (en) * 1974-02-20 1976-10-12 Tecumseh Products Company Expansible chamber device
JPS51109305U (fr) * 1975-02-27 1976-09-03
JPS56120377U (fr) 1980-02-18 1981-09-12
WO1988007620A1 (fr) 1987-03-30 1988-10-06 Mueller Lothar Moteur a pistons alternatifs
US4848213A (en) * 1988-01-11 1989-07-18 The Devilbiss Company Reciprocating piston compressor with offset cylinder
DE3804574A1 (de) 1988-02-13 1989-08-24 Man Nutzfahrzeuge Gmbh Nebenantrieb einer brennkraftmaschine fuer einen luftpresser
DE3815741C1 (fr) 1988-05-07 1989-12-28 Man Nutzfahrzeuge Ag, 8000 Muenchen, De
US5378123A (en) * 1990-02-02 1995-01-03 Carmelo J. Scuderi Apparatus for recovering refrigerant with offset cam
US5215447A (en) * 1992-06-26 1993-06-01 Wen San Jou Mini-type air compressor
US20040129244A1 (en) * 2001-03-15 2004-07-08 Normand Beaudoin Poly inductive machines and differential turbines
EP1394413B1 (fr) * 2002-08-31 2016-10-12 Continental Teves AG & Co. oHG Compresseur à piston de taille réduite
JP4309326B2 (ja) * 2004-10-06 2009-08-05 本田技研工業株式会社 プラントの制御装置
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
US20070264139A1 (en) * 2006-05-09 2007-11-15 Chou Wen S Air compressor having stabilized structure
DE102006026220B4 (de) * 2006-06-06 2008-05-08 Siemens Ag Fluidpumpe mit Kurbeltrieb
DE202007017339U1 (de) * 2007-12-12 2008-03-27 Neander Motors Ag Kolbenmaschine
US8522833B2 (en) * 2008-11-04 2013-09-03 Wen San Chou Device for sealing and inflating inflatable object
DE102011015720A1 (de) 2011-03-31 2012-10-04 Neander Motors Ag Hubkolbenmaschine, vorzugsweise als Kompressor, Pumpe, Kompressionsmaschine oder dgl. wirkend
WO2014065208A1 (fr) * 2012-10-26 2014-05-01 住友ゴム工業株式会社 Compresseur et trousse de réparation de pneu à plat l'utilisant
WO2015090340A1 (fr) * 2013-12-19 2015-06-25 Volvo Truck Corporation Moteur à combustion interne
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Also Published As

Publication number Publication date
CN107110139A (zh) 2017-08-29
CN107110139B (zh) 2019-10-11
BR112017009922A2 (pt) 2018-01-02
DE102014116805A1 (de) 2016-05-19
US20180291883A1 (en) 2018-10-11
WO2016079031A1 (fr) 2016-05-26
JP2017534802A (ja) 2017-11-24
US10753349B2 (en) 2020-08-25
EP3221584A1 (fr) 2017-09-27

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