EP1718867B1 - Compresseur a pistons axiaux, en particulier compresseur pour la climatisation d'un vehicule automobile - Google Patents

Compresseur a pistons axiaux, en particulier compresseur pour la climatisation d'un vehicule automobile Download PDF

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Publication number
EP1718867B1
EP1718867B1 EP05700686A EP05700686A EP1718867B1 EP 1718867 B1 EP1718867 B1 EP 1718867B1 EP 05700686 A EP05700686 A EP 05700686A EP 05700686 A EP05700686 A EP 05700686A EP 1718867 B1 EP1718867 B1 EP 1718867B1
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EP
European Patent Office
Prior art keywords
supplementary
captive
washer
mass
ring
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 - Fee Related
Application number
EP05700686A
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German (de)
English (en)
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EP1718867A1 (fr
Inventor
Otfried Schwarzkopf
Matthias Mauritz
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.)
Valeo Compressor Europe GmbH
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Valeo Compressor Europe GmbH
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Filing date
Publication date
Application filed by Valeo Compressor Europe GmbH filed Critical Valeo Compressor Europe GmbH
Publication of EP1718867A1 publication Critical patent/EP1718867A1/fr
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Expired - Fee Related 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
    • 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
    • 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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1206—Rotational speed of a rotating inclined plate

Definitions

  • the invention relates to an axial piston compressor, in particular compressor for the air conditioning of a motor vehicle, comprising a housing and a housing arranged in the housing, driven by a drive shaft compressor unit for sucking and compressing a refrigerant, wherein the compressor unit in a cylinder block axially reciprocating piston and a the piston driving, rotating with the drive shaft swash plate, eg in the form of a swivel ring, a wobble plate or swash plate.
  • Such axial piston compressor is for example from the DE 197 49 727 A1 known.
  • This comprises a housing in which a plurality of axial pistons are arranged around a rotating drive shaft in a circular arrangement.
  • the driving force is transmitted from the drive shaft via a driver on an annular pivot plate and from this in turn to the parallel to the drive shaft translationally displaceable piston.
  • the annular swash plate is pivotally mounted on a sleeve mounted axially displaceably on the drive shaft.
  • a slot is provided through which engages the mentioned driver.
  • Drive shaft, driver, sliding sleeve and swivel disk are arranged in a so-called.
  • Engine room in which a gaseous working fluid of the compressor with a certain pressure is present.
  • the delivery volume and thus the delivery rate of the compressor are dependent on the pressure ratio between the suction side and pressure side of the piston or correspondingly dependent on the pressures in the cylinders on the one hand and in the engine room on the other.
  • the swash plate is designed as a swash plate, wherein between the swash plate and the piston mounted opposite the swash plate, rotatable receiving disc is arranged.
  • the compressors described in these publications are u.a. to take measures to prevent or reduce the imbalance of the engine during operation.
  • the known constructions in common that the rotating components relative to the translationally moving parts, namely piston, piston rod, etc. are relatively large and therefore heavy built.
  • the known constructions have in common that acts on the actual swash plate device an additional disc by a suitable coupling mechanism.
  • the plurality of rotating components are intended to establish an establishment of the moment of the swash plate device in the direction of minimal stroke of the piston, whereby influence on the control behavior is taken.
  • the series compressor 6SEU 12 C from DENSO has an engine with the following masses that are relevant for control behavior: component number Mass component [g] Total mass [g] piston 6 41 246 slide 12 5 60 translationally moving masses 306 g swash plate 1 391 391 guide pins 2 20 40 rotationally moving masses 431 g
  • the compressor according to the EP 0 809 027 A1 directed. It is about a particular embodiment of the coupling mechanism between the drive shaft and swivel disk device.
  • the coupling mechanism is designed for high pressure, for example, when used as a refrigerant R744.
  • the last-mentioned prior art also deals with a so-called constant regulation of the flow rate. It is proposed to design the kinematics of the compressor in such a way that the decelerating tilting moments acting on the swashplate clearly dominate the overturning overturning moments.
  • the term "flow rate" is relatively blurred.
  • the delivery rate could be regarded as constant, if, for example, when doubling the speed halves the tilt angle of the swash plate. This would geometrically the flow rate constant.
  • other parameters affect the flow rate when the tilt angle of the swash plate changes, eg. Degree of delivery, oil throw od. Like ..
  • the restoring torque of the swash plate is utilized because the swash plate counteracts their inclination due to the dynamic forces on the co-rotating disc part. This behavior can be supported by the force of a spring, so that the increasing with increasing rotational speed or speed flow rate is at least partially compensated by resetting the oblique or pivotal position of the swash plate.
  • compressors are known, in particular series compressors for R134a, in which the stroke volume increases on the sole side due to the acting moments of up-regulating and regulating mass forces.
  • Fig. 1 Based on the diagram according to Fig. 1 can be easily seen that arise gradients that cause an adjustment of the swashplate to larger tilt angles, as the speed increases. It should be mentioned that Fig. 1 only to be considered as an example with simple geometry. However, the trend shown also applies to more complex geometries. The calculation was based on a pivot ring with a predetermined inner and outer diameter and a predetermined height.
  • piston mass is relevant, the pitch diameter on which the pistons are located, and the number of pistons.
  • the pivot ring preferably has a moment of inertia of m 2 ( r a 2 + r i 2 ) . which is greater than 200,000 gmm 2 , preferably about 400,000 - 500,000 2 gmm 2 .
  • Deviation moment is given below, which is relevant for the tilting of the swash plate or a swivel ring, and in the case illustrated is solely responsible for the tilting of the swash plate or the swivel ring under the condition that the center of gravity of the Swivel disk or the swivel ring is located both in the tipping point and in the geometric center of the swash plate or the swivel ring. This is a desirable ideal case of construction.
  • Fig. 2 is a diagram for a nearly identical engine specified, this diagram is based on the following calculation scheme, where also ⁇ was varied from 0 ° to 16 °:
  • Fig. 1 reflects the state of the art.
  • the aufzinde behavior is appropriate Fig. 1 Frequently detectable in current R134a series compressors.
  • Fig. 2 In more recent developments, one tries rather to convert this trend into the opposite, namely accordingly Fig. 2 ,
  • a construction is selected in which an additional mass, in particular additional disc or ring is coupled to the swashplate mechanism, whose or its erecting tilting moment due to his or her Deviationsmoments cooperating with the erecting tilting moment due to the Deviationsmoments the swash plate.
  • the moments add up.
  • the deviation moment defined by the additional mass is superimposed on the moment of deviation of the swashplate, specifically the deviation moment J yz effective around the tilting axis of the swashplate .
  • the additional mass transmits no moment to the swash plate, but a power transmission takes place such that a reaction force is formed on the swash plate, which triggers a corresponding additional Deviationsmoment.
  • the additional mass preferably in the form of an additional disk or an additional ring is advantageously optimized such that the ratio "mass moment of inertia / component mass" is as large as possible.
  • the component mass should therefore be as low as possible with maximum mass moment of inertia.
  • the outer circumference of the additional ring is designed to be spherical in cross-section in order to avoid a collision between the auxiliary ring and the engine housing when pivoting the additional ring about its tilt axis.
  • the distance between the auxiliary ring and the housing inner wall should be substantially constant regardless of the tilted position of the additional ring.
  • the center of gravity of the additional mass e.g. an additional ring preferably lie on the drive shaft center axis. It is also advantageous if the tilt center of the additional mass coincides with its center of mass.
  • drive shaft 11 extends into the housing interior or in the engine room into it. The storage of the drive shaft takes place, on the one hand, in the region of the bottom of the cup-shaped housing 10 and, on the other hand, within the cylinder block 12.
  • the engine compartment bounded by the housing 10 is identified by the reference numeral 22.
  • a swash plate mechanism is effective, by which the rotational movement of the drive shaft 11 is converted into axial movement of the piston 13.
  • a swash plate 14 engages with its peripheral edge via a hinge assembly in C-shaped recesses on the back of the piston 13 a.
  • the joint arrangement is defined by two spherical segment-like joint stones 16, 17, between which the swash plate 14 slidably engages.
  • the spherical bearing surfaces of the hinge blocks 16, 17 are associated with corresponding spherical recesses on the mutually facing end faces of the C-shaped recesses of the piston 13.
  • the swash plate 14 is supported on a rotatably connected to the drive shaft 11 driver 20, preferably via roller ball, barrel or needle roller bearings, both axially and radially.
  • the tilt angle of the swash plate 14 is between the positions according to Fig. 5 and according to Fig. 6 changeable, with in Fig. 5 the tilt angle of the swash plate 14 maximum and in Fig. 6 is minimal. Accordingly, the stroke of the piston 13 is maximum or minimum.
  • the swash plate 14 is assigned an additional mass in the form of an additional ring 15 such that swash plate 14 and additional ring 15 tilt in the same way.
  • M SW ⁇ 2 * I yz .
  • the swash plate 14 which provides an insufficient moment of inertia or Deviationsmoment for a desired control behavior, supported by a further component, namely the auxiliary ring 16, which also provides a Deviationsmoment.
  • Deviationmomentes of swash plate 14 and auxiliary ring 15 are largely rectified. Both components cause a negative moment (see above for definitions), ie M SW / M SW1 / M SW2 have a negative effect. It should be noted that at very small tilt angles quite a "Hommeregeln” may arise (but not necessarily). This depends on the concrete construction.
  • the Deviationsmomente of swash plate 14 and auxiliary ring 15 are preferably dimensioned so that the sum M SW of the overturning moments M SW1 + M SW2 due to the aforementioned Deviationsmomente greater than or equal to the moment M k, ges due to all translationally moving masses, namely piston 13 and sliding blocks 16, 17 is.
  • the additional ring 15 is dimensioned so that it has a greater Deviationsmoment than the Deviationsmoment the swash plate 14th
  • the additional ring 15 is slidably supported or stored in the direction parallel to the swivel plate plane relative to the swash plate. In this respect, additional ring 15 and swash plate 14 are mechanically decoupled.
  • cylinder head 23 In the Fig. 5 and 6 is designated by the reference numeral 23 nor a cylinder head. Between cylinder head 23 and cylinder block 12 intake and exhaust valves are arranged in a conventional manner.
  • Fig. 7 shows the engine according to the Fig. 5 and 6 in exploded view.
  • the swash plate 14 is tiltable about a spherical segment ring 24 which is mounted longitudinally displaceably on the drive shaft 11 and is held by a helical compression spring in the operating position.
  • the additional ring 15 is, in particular Fig. 7 can recognize, on the driver 20, in particular hinged to a yoke 26.
  • the corresponding hinge pin is identified by the reference numeral 27. This ensures that the association between additional ring 15 and swash plate 14 is maintained.
  • the Fig. 8a and 8b show the control behavior of a compressor with additional mass ( Fig. 8a ) or without additional mass ( Fig. 8b ). It can be seen that with the help of the additional mass, the characteristics are close to each other, as in Fig. 8a is shown.
  • the control behavior is such that almost a certain independence of the Tilt angle of the speed results (M SW ⁇ M k, ges ).
  • the behavior according to Fig. 8a (with additional mass) is slightly alsregelnd compared to the behavior without additional mass accordingly Fig. 8b ,
  • the characteristics are in Fig. 8a, 8b as well as in the Fig. 9a, 9b .
  • the Fig. 12a, 12b include an invoice based on the last used additional mass for operating conditions with about 20 bar suction pressure and 60 and 90 bar high pressure (heat pump mode HP-mode).
  • the set control characteristic is also suitable for this application, since in HP operation there is generally the problem that the engine does not reach the maximum stroke. It can be seen that in the configuration calculated here, at least 70% of the maximum stroke volume is achieved. Better values would be achieved by using a lower spring stiffness for the return spring 25. A lower spring rate would remove the characteristics slightly more from the X-axis.
  • a spring constant in the range 30... 200 N / mm is claimed in connection with the additional mass, in particular 30... 90 N / mm and preferably about 60 N / mm.
  • Fig. 13 shows, by way of example, how according to the invention the deviation moment Y yz2 of the additional mass and the deviation moment J yz1 of the swashplate are substantially rectified over the tilting angle thereof.
  • the Fig. 13 also shows that for larger tilt angles, here> 16 °, J yz2 > J yz1 .
  • Fig. 13 still recognize that up to a tilt angle of about 4 ° to 5 °, the Deviationsmomente of swashplate and additional mass approximately linearly increase linearly.
  • Fig. 13 an example, which qualitatively reflects the basic idea of the described doctrine.

Claims (8)

  1. Compresseur à pistons axiaux, en particulier compresseur pour le système de climatisation d'un véhicule automobile, avec un boîtier (10) et, disposé dans le boîtier (10), un groupe compresseur entraîné par un arbre moteur (11) pour aspirer et comprimer un fluide frigorigène, le groupe compresseur comprenant des pistons (13) qui décrivent un mouvement alternatif axial dans un bloc-cylindres (12) et un plateau orientable (bague oscillante, plateau oscillant ou disque en nutation) (14) qui tourne avec l'arbre moteur (11) et entraîne les pistons,
    dans lequel
    le plateau orientable (14) est associé à une masse additionnelle, en particulier sous la forme d'un plateau additionnel ou d'une bague additionnelle (15), qui permet de maintenir un moment de déviation (Jyz2) sensiblement de même sens que le moment de déviation (Jyz1) du plateau orientable (14) de façon que la somme (MSW) des moments de renversement (MSW1 + MSW2) résultant de ces moments de déviation soit supérieure ou égale au moment (Mk,tot) résultant de l'ensemble des masses déplacées en translation, en particulier des pistons (13), le cas échéant y compris les coulisseaux (16, 17), tiges de pistons ou similaires,
    caractérisé en ce que
    le centre de gravité de la masse additionnelle (15) se trouve sur l'axe de l'arbre moteur (18), et en ce que
    lorsque la masse additionnelle est réalisée sous la forme d'une bague additionnelle (15) pivotant avec le plateau orientable (14), son centre de gravité se situe dans la zone de son articulation de renversement.
  2. Compresseur à pistons axiaux selon la revendication 1, caractérisé en ce que la masse additionnelle (15) peut se déplacer selon un mouvement alternatif parallèle à l'axe longitudinal de l'arbre moteur (11), en particulier conjointement avec le plateau orientable (14).
  3. Compresseur à pistons axiaux selon l'une des revendications 1 ou 2,
    caractérisé en ce que, sur une bonne partie de la plage d'angle de basculement du plateau orientable (14), le moment de, déviation (Jyz2) de la masse additionnelle (15) est plus grand que celui (Jyz1) du plateau orientable (14), le moment de déviation (Jyz1) du plateau orientable, à des angles de basculement plus grands, en particulier à un angle de basculement de 12° à 18° environ, en particulier de 15° environ, étant de préférence plus petit que le moment de déviation (Jyz2) de la masse additionnelle.
  4. Compresseur à pistons axiaux selon l'une des revendications 1 à 3, caractérisé en ce que, lorsqu'elle est réalisée sous la forme d'une bague additionnelle (15), la masse additionnelle présente un diamètre extérieur qui est à peine plus petit que le diamètre intérieur du boîtier de mécanisme moteur (10).
  5. Compresseur à pistons axiaux selon la revendication 4, caractérisé en ce que le bord périphérique extérieur de la bague additionnelle (15) présente une section de forme convexe telle que, lors du pivotement en maintenant une distance minimale par rapport à la paroi intérieure du boîtier de mécanisme moteur, une collision avec cette dernière est exclue.
  6. Compresseur à pistons axiaux selon l'une des revendications 1 à 5, caractérisé en ce que la masse additionnelle, en particulier la bague additionnelle (15), est supportée de manière à pouvoir se déplacer dans une direction parallèle au plan du plateau orientable par rapport au plateau orientable (14).
  7. Compresseur à pistons axiaux selon la revendication 6, caractérisé en ce que la masse additionnelle ou la bague additionnelle (15) est retenue par un pion de guidage (19) qui s'étend parallèlement à l'axe du plateau orientable de manière à pouvoir se déplacer sur un taquet d'entraînement (20) solidaire en rotation de l'arbre moteur (11).
  8. Compresseur à pistons axiaux selon l'une des revendications 1 à 7, caractérisé en ce que la masse additionnelle s'étend au moins en partie autour du disque en nutation (14), en particulier concentriquement à l'axe de ce dernier.
EP05700686A 2004-02-26 2005-01-04 Compresseur a pistons axiaux, en particulier compresseur pour la climatisation d'un vehicule automobile Expired - Fee Related EP1718867B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200410009270 DE102004009270A1 (de) 2004-02-26 2004-02-26 Axialkolbenverdicher, insbesondere Verdichter für die Klimaanlage eines Kraftfahrzeuges
PCT/EP2005/000021 WO2005085638A1 (fr) 2004-02-26 2005-01-04 Compresseur a pistons axiaux, en particulier compresseur pour la climatisation d'un vehicule automobile

Publications (2)

Publication Number Publication Date
EP1718867A1 EP1718867A1 (fr) 2006-11-08
EP1718867B1 true EP1718867B1 (fr) 2008-03-12

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EP05700686A Expired - Fee Related EP1718867B1 (fr) 2004-02-26 2005-01-04 Compresseur a pistons axiaux, en particulier compresseur pour la climatisation d'un vehicule automobile

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EP (1) EP1718867B1 (fr)
DE (2) DE102004009270A1 (fr)
WO (1) WO2005085638A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1661523B1 (fr) * 2004-11-30 2008-04-09 Stryker Trauma SA Insert pour élément de serrage, élément de serrage avec un tel insert et articulation formée avec ceux-ci.
DE102008038436B4 (de) * 2008-08-20 2019-03-21 Robert Bosch Gmbh Verfahren zur Ermittlung einer Einstellgröße einer hydrostatischen Verdrängereinheit und entsprechendes System
DE102012006907A1 (de) * 2012-04-05 2013-10-10 Gea Bock Gmbh Verdichter
CN114811741B (zh) * 2022-05-13 2024-01-19 宁波奥克斯电气股份有限公司 空调重心高度与支撑面半径的设计方法、结构及空调器

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
CS172656B1 (fr) * 1974-06-24 1977-01-28
US4077269A (en) * 1976-02-26 1978-03-07 Lang Research Corporation Variable displacement and/or variable compression ratio piston engine
US4815358A (en) * 1988-01-27 1989-03-28 General Motors Corporation Balanced variable stroke axial piston machine
US4836090A (en) * 1988-01-27 1989-06-06 General Motors Corporation Balanced variable stroke axial piston machine
JP2892718B2 (ja) * 1989-11-17 1999-05-17 株式会社日立製作所 可変容量形圧縮機
DE19616961C2 (de) * 1996-04-27 2002-11-07 Daimler Chrysler Ag Hubkolbenmaschine mit Taumelscheibengetriebe
JPH10246181A (ja) * 1997-02-28 1998-09-14 Toyota Autom Loom Works Ltd 可変容量型圧縮機
DE19749727C2 (de) * 1997-11-11 2001-03-08 Obrist Engineering Gmbh Lusten Hubkolbenmaschine mit Schwenkscheibengetriebe
DE19839914A1 (de) * 1998-09-02 2000-03-09 Luk Fahrzeug Hydraulik Axialkolbenmaschine

Also Published As

Publication number Publication date
EP1718867A1 (fr) 2006-11-08
DE102004009270A1 (de) 2005-09-15
WO2005085638A1 (fr) 2005-09-15
DE502005003194D1 (de) 2008-04-24

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