EP1692396B1 - Compresseur a pistons axiaux, en particulier compresseur pour installation de climatisation d'un vehicule automobile - Google Patents

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

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Publication number
EP1692396B1
EP1692396B1 EP04765823A EP04765823A EP1692396B1 EP 1692396 B1 EP1692396 B1 EP 1692396B1 EP 04765823 A EP04765823 A EP 04765823A EP 04765823 A EP04765823 A EP 04765823A EP 1692396 B1 EP1692396 B1 EP 1692396B1
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EP
European Patent Office
Prior art keywords
moment
tilt angle
tilt
plate
pistons
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.)
Not-in-force
Application number
EP04765823A
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German (de)
English (en)
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EP1692396A1 (fr
Inventor
Otfried Schwarzkopf
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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Publication date
Application filed by Valeo Compressor Europe GmbH filed Critical Valeo Compressor Europe GmbH
Publication of EP1692396A1 publication Critical patent/EP1692396A1/fr
Application granted granted Critical
Publication of EP1692396B1 publication Critical patent/EP1692396B1/fr
Not-in-force 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
    • F04B27/14—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
    • F04B27/1804—Controlled by crankcase pressure
    • 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

Definitions

  • the invention relates to an axial piston compressor, in particular compressor for the air conditioning of a motor vehicle, in the form of a swash or swash plate compressor with an adjustable in its inclination and driven by the machine shaft swash plate device.
  • Such a compressor according to the preamble of claim 1 is for example from the US 4,801,248 A known.
  • EP 1 172 557 A2 is a two-part support device, which simultaneously transmits the torque between the shaft and swash plate as a driver.
  • the attached to the machine shaft first driver part which is designed as a bearing in the form of a receiving bore is disposed at a considerable distance next to the swash plate, and a second, in the first articulated engaging driver part is formed as a lateral extension of the swash plate.
  • the first as well as the second driver part are in pairs.
  • the bearing clearance of a driver and its bearing part is slightly larger in order to guide defined and thereby avoid overdetermination or a double fit. This has the consequence that such a compressor can not be operated independently of rotation, that has a defined preferred direction of rotation.
  • the center of gravity removed from the tilt axis causes imbalance since the engine can only be balanced for a (preferably) average swash plate tilt angle.
  • the swashplate having a thickened hub part has a relatively large moment of inertia with its "lateral extension" with a center of gravity substantially away from the tilt axis, so that a sudden change in the rotational speed with corresponding inertia leads to a tilt adjustment of the swashplate. Furthermore, the center of gravity substantially determines the control behavior, in such a way that the compressor greatly upregulates, i. the mass inertia forces of the swashplate and their center of gravity position cause a moment of deviation, which causally dominates the translatory mass forces (for example, by the pistons and sliding blocks).
  • the compressor should be able to control.
  • gas is passed from the high pressure side of the compressor into the crankcase.
  • the pressure increase causes the swashplate tilt angle to increase.
  • a minimum tilt angle of approx. 0.5 ° must exist (can scatter, depending on the constructive implementation of various parameters).
  • the minimum tilt angle ensures a minimum piston stroke, which is sufficient to maintain the pressure on the high pressure side. Leaks e.g. on the low pressure side of the system via the expansion device counteract this.
  • the focus of consideration is on the magnitude of the moment due to the rotating masses (-) (including the moment due to the center of gravity, can be (+ or (-)), based on the moment due to the translationally moving masses (+).
  • flow rate is relatively blurred.
  • the flow rate should be considered constant, if, for example, when doubling the speed of the tilt angle of the swash plate device halved. This would geometrically the flow rate constant.
  • other parameters on the flow rate for example, if the tilt angle changes, for example, slightly varying degree of delivery or oil throw or the like.
  • compressors are known in the prior art in which the stroke volume is increased on the sole side due to the acting moments of regulating and regulating mass forces.
  • control intervention of the control valves used that must be compensated if necessary.
  • New developments especially known for CO 2 ) are aimed at reversing this behavior. The necessary control intervention can then be reduced or unnecessary.
  • Fig. 1 shows the dependence engine room pressure difference, based on the suction pressure on the tilt angle of the swash plate.
  • An example was calculated for the pressures: high pressure 120 bar and suction pressure 35 bar.
  • the speeds were also calculated: 600 rpm, 1200 rpm, 2500 rpm, 5000 rpm, 8000 rpm and 11,000 rpm. However, only 5 of the 6 calculated courses can be seen. This is because the gradients for the calculated speeds of 600 rpm and 1200 rpm are almost identical to each other.
  • Deviationsomomentes specified which is relevant for the tilting of the swash plate or a swivel ring, and in the case shown solely for the tilting of the swash plate or the swivel ring is responsible under the condition that the center of gravity of the swash plate or of the pivot ring is located both in the tilting point and in the geometric center of the swash plate or the swivel ring. This is a desirable ideal case of construction.
  • J Y Z - J 2 ⁇ cos ⁇ sin ⁇ + J 3 ⁇ cos ⁇ sin ⁇
  • the proportion J YZ is smaller than the Steiner proportion y s ⁇ z s ⁇ m.
  • the proportion J YZ always controls the compressor while the fraction y s - z s - m always excites (set by the position in the quadrant Q2, Q4 according to FIG Fig. 7 ).
  • Fig. 2 are the calculation scheme and the Fig. 1 corresponding diagram given for a nearly identical engine.
  • the height of the swash plate was increased from 10 mm to 18 mm.
  • the relevant mass moment of inertia J z increases to twice the value.
  • a regulating behavior of the swashplate engine can be seen. This trend is indicated by the inserted arrow, where "n” is to denote the speed (compare the trend with Fig. 1 !).
  • the swashplate tilt angles of the compressors are reduced by a minimum value and a maximum Value limited. For example, values between a tilt angle of approx. 0 ° and a maximum of approx. 25 ° are conceivable. In practice, the values are more likely between 1 ° and 18 °.
  • the diagram of Fig. 4 contains the result of the calculations for a design on the tilt angle 16 °, which is to be considered as the maximum tilt angle for this engine example.
  • the height of the swash plate has been adjusted to 14.292 mm, the moment balance also shows balanced conditions. It should be mentioned again that of course other swash plate parameters can be used for the adjustment of the mass moment of inertia. For ease of comparison, however, the parameter swash plate height has been selected by way of example only.
  • the slope of the control characteristics is essentially determined by the spring force acting on the swashplate mechanism.
  • the characteristic curves were calculated with a spring constant with respect to the return spring (return to minimum stroke) of 60 N / mm. If the spring constant were chosen to be smaller, the curves would be less sloping in the direction of larger tilt angles. If the spring constant chosen larger, the curves would be more sloping towards greater tilt angle.
  • Each 5000 RPM curve is representative of a set of curves at a particular operating point. If it is taken into account that a certain control pressure of at least 2-3 bar above the suction pressure is required and a favorable control behavior is achieved in that the characteristic curves have a certain as far as possible linear gradient, so it is plausible that a closely spaced "curve bundle "is more likely for all operating ranges in the desired range of the map than control curves, the more" drift apart ".
  • the essential measure is that the Deviationsmoment the swash plate is structurally specified so that it causes a "Germanregeln" of the swash plate in the range of small tilt angle together with the piston or separately.
  • the slope of the moment M k ges due to the mass forces of the pistons must be smaller than the slope of the moment due to the Deviationsmoments.
  • a swash plate mechanism is specified by which the design (the subject invention) can be implemented constructively, wherein Fig. 6 ; this is an exploded perspective view and Fig. 7 shows two side views of the essential components at minimum and maximum tilt angle.
  • the illustrated pivoting ring mechanism 100 includes an annular swashplate, i. a pivot ring 101, which is mounted on a drive shaft 104 in a tilt-adjustable manner via a guide or sliding sleeve 102 and a compression spring 103 located in the latter.
  • the pivot ring 101 is driven in rotation by the drive shaft 104 and is articulated about a special embodiment of the guide sleeve 102 about a pivot axis extending transversely to the drive shaft.
  • This pivot axis is defined by two bearing pins 104a, 104b, which are rotatably received in bearing sleeves 105a, 105b of the guide sleeve 102 and correspondingly arranged radial bores 106a, 106b of the pivot ring 101.
  • the bearing sleeves 105 a, 105 b are dimensioned such that they bridge an annular space formed between the guide sleeve 102 and the pivot ring 101.
  • the pivot ring 101 is pivotally connected to a rotating together with the drive shaft 104 support member 107, wherein this compound is designed as Axialabstützung.
  • This support bow 108 is designed so that it overlaps an effective between a piston 109 of the assembly and the pivot ring hinge assembly, in such a way that regardless of the inclination (the tilt angle) of the Swing ring 101 every collision between this and the support arc 108 on the one hand and a joint assembly comprising a flask 110 on the other hand is excluded.
  • the support member 107 is part of a rotatably connected to the drive shaft 104 disc 111th
  • a support surface of the support arch 108 extends approximately concentric with the center of an effective between the piston 109 and the pivot ring 101 joint assembly.
  • the axial support is thus effective outside of said hinge assembly, with the result that it is not affected by axial support measures.
  • the connection between the pivot ring 101 and the support arc 108 is made by two connecting pins 112a, 112b, which in a 90 ° opposite to the aforementioned holes 106a, 106b offset bore pair 113a, 113b of the pivot ring and in correspondingly arranged holes 114a, 114b of Support bow intervene yourself.
  • the joint arrangement with respect to the piston foot 110 of the piston 109 is - according to the prior art - formed by two spherical segment-shaped hinge blocks 115a, 115b, the spherical surfaces in a correspondingly shaped lower end face of the piston 109 on the one hand and a corresponding surface of an opposite extension 117 of the piston 110th on the other hand.
  • a gap 116 is formed, in which the pivot ring 101 engages such that opposite end surface portions touch the flat surfaces of the joint stones.
  • the pivot bearing of the pivot ring 101 only for torque transmission and the support member 108 only serves for the axial support of the piston 109 and the gas force support.
  • the torque transmission is thus decoupled from the axial support of the pivot ring 101.
  • the support surface for the support arc 108 on the support member 107 is formed as a portion 118 of a cylinder surface.
  • the support sheet 108 is slidably mounted in the radial direction relative to the pivot ring 101.
  • the invention initially aims at the conventional tilt angle range between a minimum and a maximum tilt angle and in a further step to minimize the minimum tilt angle in the direction 0 °.
  • Fig. 11 and 12 the control curves for the cases already described are shown. To take into account are the spring constants chosen differently for the "upset” case and the “offsetting” case. The choice of different spring constants is necessary to set a meaningful slope of the characteristics, which is necessary for control. Characteristic of the control characteristics in the diagram according to the subject invention is also the intersection at about 2 °, which shows the "trend reversal" of the resulting moment.

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

Claims (8)

  1. Compresseur à pistons axiaux, en particulier compresseur pour l'installation de climatisation d'un véhicule automobile, avec un boîtier et une unité de compresseur placée dans le boîtier et entraînée par un arbre d'entraînement (104) pour l'aspiration et la compression d'un fluide réfrigérant, dans lequel l'unité de compresseur comprend des pistons (109) effectuant un mouvement de va-et-vient axial dans un bloc-cylindres et un disque pivotant tournant avec l'arbre d'entraînement (104) qui entraîne les pistons sous forme de disque en nutation ou de disque oscillant ou de bague pivotante (101),
    caractérisé en ce que
    le disque pivotant est construit et dimensionné par la détermination de la géométrie et/ou de la masse et/ou du centre de gravité de masse de telle manière que son couple Msw résultant du couple de déviation Iyz, pour lequel on applique Msw = Iyz * ω2, c'est-à-dire le couple résultant de l'inertie de masse et du centre de gravité de masse du disque pivotant, conjointement avec le couple Mk,ges résultant des masses déplacées en translation, en particulier le piston, y compris, le cas échéant, les coulisseaux (115a, 115b), les tiges de pistons ou d'autres éléments similaires, dans la région du petit angle de basculement en cas d'augmentation de la vitesse de rotation et avec une différence de pression constante Δp entre le côté de haute pression et le côté de basse pression, entraîne une augmentation de l'angle de basculement et, de ce fait, un accroissement de la capacité de refoulement et il en résulte une réduction de l'angle de basculement et, de ce fait, une diminution de la capacité de refoulement après le dépassement d'un angle limite de basculement αgrenz, pour lequel on applique Msw = Mk,ges, en cas d'augmentation de la vitesse de rotation et avec une différence de pression constante.
  2. Compresseur à pistons axiaux selon la revendication 1,
    caractérisé en ce que
    le disque oscillant (101) est construit et dimensionné de telle manière que la courbe du couple Msw résultant du couple de déviation Iyz en fonction de l'angle de basculement α à la vitesse de rotation identique présente sensiblement une pente plus importante en terme de grandeur que la courbe du couple Mk,ges résultant des masses déplacées en translation en fonction de l'angle de basculement.
  3. Compresseur à pistons axiaux selon la revendication 1 ou 2,
    caractérisé en ce que
    le signe de la somme du couple Mk,ges résultant des masses déplacées en translation et du couple Msw résultant du couple de déviation lyz dans la région de l'angle de basculement entre un angle de basculement minimal prédéterminé αmin et un angle de basculement max αmax varie, en particulier, entre "plus" et "moins", ce qui indique une transition entre une augmentation de l'angle de basculement et un accroissement de la capacité de refoulement causé par celle-ci et une diminution de l'angle de basculement et, de ce fait, de la capacité de refoulement.
  4. Compresseur à pistons axiaux selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    un point de basculement du disque pivotant (101) est déterminé comme point de coupe des axes de rotation de l'arbre d'entraînement (104) et du disque pivotant.
  5. Compresseur à pistons axiaux selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    en divisant le compartiment comprenant l'arbre d'entraînement (104) et le disque pivotant (101) en quatre quadrants (Q1, Q2, Q3, Q4), le centre de gravité du disque pivotant se trouve soit dans un premier quadrant avant (Q1) délimité par l'arbre d'entraînement et la face avant du disque pivotant comprenant le support de piston, dirigée vers le piston, soit dans un deuxième quadrant avant (Q2) sur la face opposée au premier quadrant (Q1) par rapport à l'arbre d'entraînement soit dans un troisième quadrant arrière (Q3) disposé derrière, c'est-à-dire sur la face opposée au piston, du disque pivotant par rapport au disque pivotant à la hauteur du deuxième quadrant (Q2) soit dans un quatrième quadrant arrière (Q4) disposé derrière, c'est-à-dire sur la face opposée au piston, du disque pivotant par rapport au disque pivotant à la hauteur du premier quadrant (Q1).
  6. Compresseur à pistons axiaux selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le disque pivotant (101), d'une part, et le piston (109), y compris, le cas échéant, les coulisseaux (115a, 115b), les tiges de pistons ou d'autres éléments similaires, d'autre part, sont construits et dimensionnés de telle manière que, avec un angle de basculement α sensiblement de 0°, le couple Msw résultant du couple de déviation lyz du disque de basculement est supérieur à zéro et le couple Mk,ges résultant des masses déplacées en translation est sensiblement égal à zéro, de sorte qu'un couple total positif entraîne une augmentation de l'angle de basculement α du disque pivotant alors qu'au-delà d'un angle de basculement prédéterminé dans la région entre 1,5° et 2,5°, en particulier un angle d'environ 2°, l'augmentation du couple Mk,ges résultant des masses déplacées en translation surcompense l'augmentation du couple Msw résultant du couple de déviation Iyz de telle manière qu'à partir de cette valeur, il se produit une diminution de l'angle de basculement du disque pivotant.
  7. Compresseur à pistons axiaux selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le disque pivotant (101) est construit et dimensionné de telle manière que son couple Msw résultant du couple de déviation lyz avec un angle de basculement dans la région entre 0,4 et 0,8°, en particulier un angle d'environ 0,6°, est égal à zéro.
  8. Compresseur à pistons axiaux selon la revendication 6 ou 7,
    caractérisé en ce que
    la valeur de l'angle de basculement à partir de laquelle le couple total constitué par le couple Mk,ges résultant des masses déplacées en translation et le couple Msw résultant du couple de déviation Iyz du disque de basculement entraîne une diminution de l'angle de basculement et/ou la valeur de l'angle de basculement avec laquelle le couple Msw résultant du couple de déviation Iyz est égal à zéro sont réglées grâce à une prédétermination appropriée de la position du centre de gravité du disque pivotant (101).
EP04765823A 2003-11-19 2004-10-05 Compresseur a pistons axiaux, en particulier compresseur pour installation de climatisation d'un vehicule automobile Not-in-force EP1692396B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10354038A DE10354038B4 (de) 2003-11-19 2003-11-19 Axialkolbenverdichter, insbesondere Verdichter für die Klimaanlage eines Kraftfahrzeuges
PCT/EP2004/011113 WO2005050016A1 (fr) 2003-11-19 2004-10-05 Compresseur a pistons axiaux, en particulier compresseur pour installation de climatisation d'un vehicule automobile

Publications (2)

Publication Number Publication Date
EP1692396A1 EP1692396A1 (fr) 2006-08-23
EP1692396B1 true EP1692396B1 (fr) 2008-03-26

Family

ID=34609116

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04765823A Not-in-force EP1692396B1 (fr) 2003-11-19 2004-10-05 Compresseur a pistons axiaux, en particulier compresseur pour installation de climatisation d'un vehicule automobile

Country Status (5)

Country Link
EP (1) EP1692396B1 (fr)
JP (1) JP2007511702A (fr)
AT (1) ATE390560T1 (fr)
DE (2) DE10354038B4 (fr)
WO (1) WO2005050016A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7444921B2 (en) 2006-08-01 2008-11-04 Visteon Global Technologies, Inc. Swash ring compressor
DE102007058064A1 (de) * 2007-12-03 2009-06-04 Valeo Compressor Europe Gmbh Verdichter
KR101193399B1 (ko) * 2012-06-22 2012-10-26 주식회사 두원전자 용량가변형 사판식 압축기
CN112937251A (zh) * 2021-04-29 2021-06-11 吉林大学 一种车载空调压缩机控制方法及系统

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6365177A (ja) * 1986-09-05 1988-03-23 Hitachi Ltd 可変容量斜板式圧縮機
JPH01262378A (ja) * 1988-04-08 1989-10-19 Hitachi Ltd 可変容量斜板式圧縮機
JPH0552183A (ja) * 1991-08-21 1993-03-02 Hitachi Ltd 可変容量形圧縮機
JP3417652B2 (ja) * 1994-04-21 2003-06-16 株式会社豊田自動織機 容量可変型斜板式圧縮機
DE19616961C2 (de) * 1996-04-27 2002-11-07 Daimler Chrysler Ag Hubkolbenmaschine mit Taumelscheibengetriebe
DE19839914A1 (de) * 1998-09-02 2000-03-09 Luk Fahrzeug Hydraulik Axialkolbenmaschine
EP1151197B1 (fr) * 1998-09-02 2003-09-24 LuK Fahrzeug-Hydraulik GmbH & Co. KG Machine a pistons axiaux
JP2002031043A (ja) * 2000-07-14 2002-01-31 Toyota Industries Corp 圧縮機

Also Published As

Publication number Publication date
WO2005050016A1 (fr) 2005-06-02
DE10354038A1 (de) 2005-06-23
EP1692396A1 (fr) 2006-08-23
ATE390560T1 (de) 2008-04-15
DE10354038B4 (de) 2006-06-22
DE502004006690D1 (de) 2008-05-08
JP2007511702A (ja) 2007-05-10

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