WO2006018162A1 - Compresseur a pistons axiaux - Google Patents

Compresseur a pistons axiaux Download PDF

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Publication number
WO2006018162A1
WO2006018162A1 PCT/EP2005/008530 EP2005008530W WO2006018162A1 WO 2006018162 A1 WO2006018162 A1 WO 2006018162A1 EP 2005008530 W EP2005008530 W EP 2005008530W WO 2006018162 A1 WO2006018162 A1 WO 2006018162A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
compressor according
swash plate
angle
piston
Prior art date
Application number
PCT/EP2005/008530
Other languages
German (de)
English (en)
Inventor
Otfried Schwarzkopf
Original Assignee
Zexel Valeo Compressor Europe 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 Zexel Valeo Compressor Europe Gmbh filed Critical Zexel Valeo Compressor Europe Gmbh
Priority to US11/660,521 priority Critical patent/US20090104048A1/en
Priority to EP05771046A priority patent/EP1778977A1/fr
Publication of WO2006018162A1 publication Critical patent/WO2006018162A1/fr

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
    • 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
    • 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

Definitions

  • the invention relates to an axial piston compressor, in particular a compressor for the air conditioning system of a motor vehicle according to the preamble of claim 1.
  • the momentum (referred to in the expanded text as M sw ) usually acts as a result of the rotating masses; Only in the area of very small tilt angles can an adjusting moment be generated, for example, by an exposed center of gravity position (Steiner component in the calculation of the moment of deviation J yz ) in the swash plate (see DE 195 14 748 C2). Even in the area of small tilt angles, the proportion of the deviation moment J without stone fraction prevails, and the swashplate has an increasingly declining tilting moment as the tilt angle increases.
  • EP 0 809 027 A1 Another engine is known from EP 0 809 027 A1, which is characterized in that the delivery rate of the compressor is compensated by the dynamic behavior of the engine of the compressor, so that the delivery rate can be kept constant. Specifically, it says there as follows: "For a constant control of the flow rate at varying rotational speeds, the restoring torque of the Tau ⁇ melusion can be exploited, which counteracts their inclination due to dynamic forces on the co-rotating disc part.”
  • the desired control behavior of the compressor is primarily not achieved with the component mass of the swashplate in relation to the translationally moved masses, but taking into account the mass moment of inertia of the unit "swash plate", which depends more on its geometry than on the component mass Speed variations or speed changes to compensate for the moment due to translationally moving masses directly by the moment due to rotating masses, or even overcompensate.
  • the delivery volume is directly proportional to the speed, ie doubles the speed, so doubles the volume.
  • the tilting moment of the swash plate which is triggered by the relevant moment of deviation, the following equation applies:
  • the object of the invention is to admit a compressor with optimized control behavior in which a full load state is avoided at high and highest compressor speeds.
  • An essential aspect of the invention is therefore that the tilting behavior of the swash plate is so automatically limiting effect that at high speeds of the compressor, especially at very high speeds or the maximum speed of the compressor, the angle of maximum deflection of the swash plate is smaller than that Angle of maximum deflection ⁇ max at low speeds of the compressor.
  • the compressor operates at high speeds, in particular at its maximum speed, with an excessive delivery volume. Since this measure engages regulating in the delivery volume, the number of required control operations is reduced (usually swash plate compressors are controlled by a pressure difference between a prevailing in the engine room of the compressor pressure and a pressure prevailing at the compressor outlet side pressure, this pressure difference the piston stroke and thus the delivery volume of the compressor determines).
  • a compressor according to the invention is designed such that both the geometry and the dimensioning of all translationally moving parts of the compressor and all rotationally moving parts are such that for predetermined tilt angle of the swash plate, in particular between a predetermined minimum tilt angle and a predetermined maximum tilt angle the moment M k _ ges as a result of the translationally moving masses is chosen to be smaller than the moment M sw due to the Deviationsmoments, ie is chosen smaller than the torque due to the Mas ⁇ inertia of the swash plate, that at high speeds of the compressor, especially at very high speeds or a maximum speed, the angle of maximum Aus ⁇ steering of the swash plate is smaller than the angle of maximum deflection at smaller ren speeds of the compressor.
  • the translationally moving parts of the compressor include the piston, possibly also the piston rods and sliding blocks or the like.
  • the rotationally moving parts are essentially the swash plate, and possibly one or more drivers to count.
  • it is an embodiment of a compressor according to the invention that is structurally simple to implement and thus inexpensive to produce.
  • the advantages already explained above, in particular the advantage of a small number of control actions, which become necessary during operation of a compressor according to the invention, are fully valid for the prevailing preferred embodiment.
  • He inventive compressor may comprise at least one device which exerts a force on the swash plate.
  • Said device is preferably assigned to the same in addition to a device for adjusting or for controlling the engine room pressure of the compressor.
  • This device or these devices may or may act alone as the automatically limiting member of the swash plate, but it may also be arranged in a compressor, in which already the mass distributions or the torque distribution of the swash plate Abregein same at high speeds causes. In this case, an already existing due to the geometry of the swashplate mechanism tendency of the compressor to be depressed at high speed, supported or amplified.
  • the at least one device for exerting the actuating force optionally comprises an elastic element, which may be present in particular in the form of a return spring, and / or an actuator or an actuating piston.
  • a compressor according to the invention may comprise a centrifugal force-dependent actuator and / or a further spring.
  • the at least one device for exercising the actuating force comprises a throttle point, whose cross-section can be varied by means of an actuator, in particular by means of an actuating piston.
  • the throttle point may be arranged in particular on the suction or pressure side of the compressor. If the throttle point is arranged on the suction side of the compressor, the density of the suction gas can thereby be regulated or lowered as desired.
  • a thrust in the engine of the compressor prevailing pressure and / or the prevailing at the outlet side of the compressor pressure is to be preferred.
  • These manipulated variables are easily accessible.
  • the actuator is controlled or controlled internally, in particular via a magnetic coil or the like device.
  • a constant cross section of the throttle is conceivable.
  • the center of gravity of the swash plate is on the tilting axis thereof.
  • the tilting axis of the swashplate in turn, preferably lies on the central axis of the drive shaft.
  • the swivel disk is annular, i. designed as a swivel ring. This ensures an optimum relationship between the mass of the swash plate (which is low) or the swivel ring and its or their mass moment of inertia (which is high).
  • the angle of maximum deflection of the swash plate in the range of small and medium speeds of the compressor corresponds to an angle oc max
  • the angle of maximum deflection at the maximum speed of the compressor corresponds approximately to an angle of ⁇ max / 2.
  • Areas of low and medium speed extend in the parlance of the present application to about half the maximum speed of the compressor. In compressors of modern design, which reach a maximum speed of about 8000 to 10,000 revolutions per minute, thus extending a range of low and medium speeds up to about 4000 revolutions per minute, it being understood that the above figuress ⁇ of course are to be regarded as exemplary only.
  • the swash plate of a compressor according to the invention is preferably for speeds from about 4000 to 5000 revolutions per minute no longer up to one or the angle cx max ver pivoted.
  • an optimal load limitation is guaranteed, which has advantageous effects especially under the safety aspect.
  • Both a risk of icing and the risk of bursting of the compressor housing is significantly reduced compared to compressors according to the prior art.
  • the limitation of the pivot angle for increasing rotational speeds of the compressor becomes stronger. Also for this imple mentation form, the advantages arise, in particular when considering the safety aspect, analogous to the foregoing.
  • the ratio of deviation moment in z-direction and total mass of all translationally movable parts J z / m k _ ges is in a further preferred embodiment at least about 2000 mm 2 , even more advantageous is a value of more than 3000 mm 2 . Due to the large ratio between Deviationsmoment and total mass of the translationally movable parts, the desired control characteristic is achieved in a simple manner.
  • a "suitable" spring constant should be chosen (this determines the slope of the control characteristic.)
  • a return spring which exerts a restoring force on the deflected swivel disk, has a spring constant It is even more advantageous to use return springs having a spring constant of less than 30 N / mm, of course, the moments of the translationally and rotationally moving parts are respectively adapted accordingly springs with such spring constants are available inexpensively, require a small installation space and are also low-wear.
  • the swashplate has a minimum and maximum stop defined directly or indirectly (via the sliding sleeve).
  • the maximum stop is not reached at high speeds and is fixed in the embodiments described above, and can not be regulated.
  • a compressor according to the invention has a speed-dependent stop, which limits the angle of maximum deflection of the swash plate as a function of the compressor speed.
  • This speed-dependent stop serves as a further measure to ensure that at high speeds, the angle of maximum deflection of the swash plate is lower than pay at low Dreh ⁇ . It is conceivable in this case, for example, a paragraph on the drive shaft, which prevents pivoting beyond a predetermined angle.
  • another construction for example, has a displaceably mounted on the drive shaft sleeve or the like., would be conceivable.
  • the control of the stop can for example be done via the (speed-dependent) centrifugal force.
  • Fig. 1 is a sketch of a pivot ring of a compressor according to the invention
  • FIG. 2 shows a sketch of a swivel disk for explaining the coordinate system used in the present application
  • FIG. 3-7 diagrams showing the control characteristics of two embodiments of a compressor according to the invention as a function of various parameters such as speed, suction pressure, compression pressure and spring constant a remindstell ⁇ feather;
  • Fig. 8 is a diagram illustrating the control characteristics of a compressor according to the invention as a function of other (additional) parameters.
  • the tilting moment of schwenkba ⁇ ren share the swash plate means can then be expressed in simplified form by equations that are relevant for an annular swash plate component.
  • J yz Ji cos 2 COSCt 3 - J 2 cosß 2 cosß 3 - J 3 cos ⁇ 2 cos ⁇ 3
  • Direction angle of the z-axis ⁇ 3 ⁇ with respect to the main axes of inertia ⁇ , ⁇ , ⁇
  • J should have a certain size; J y2 T> - J 3 TJ 2 inevitably increases.
  • I 7Z -Ji cos ⁇ sin ⁇ + J 3 cos ⁇ sin ⁇
  • the (tilt) moment of the swivel ring can be deliberately adjusted by various parameters (geometry, density distribution, mass, center of mass) as a result of the associated deviation moment
  • M sw should be significantly larger than M k .
  • Piston including sliding block (pair) mass of all pistons including sliding blocks m sw mass of swivel ring r a outer radius of swivel ring t ⁇ inner radius of swivel ring h height of swivel ring g density of swivel ring
  • the center of gravity position should largely have no influence. That When calculating the governing moment of deviation, the proportion of Steiner to be considered for the center of gravity is essentially
  • the ratio J y / m k tot or J 2 / m k makes sense, regardless of the refrigerant (which may be, for example, CO 2 , Rl 34a, Rl 52a, etc.), the moment ratio
  • the preferred point from guide forming a compressor according to the invention a ratio J j k _ ./m tot of more than 1000 mm 2 or more than 1500 mm 2, while the ratio J 2 / m k ges in both cases, well over 2000 mm 2 , in the second preferred embodiment, even in about 3000 mm 2 .
  • control characteristic curves for the rotational speed 8000 rpm for the three different operating points intersect the x axis (on which the tilting angle of the swash plate or the geometric stroke volume of the compressor is plotted) at approximately half the maximum tilt angle, which in the present preferred embodiment is about 20 °.
  • the intersection with the x-axis can be constructively set, the other operating points include smaller deviations thereof, with control characteristics of the same speed and different operating points are shifted approximately parallel to each other.
  • the information on the geometry of the swash plate, which has a control characteristic, as shown in Fig. 6, can be found in Table 2 above.
  • FIG. 7 shows, analogously to FIG. 3, the known three operating points at a rotational speed of 1000 rpm and 8000 rpm. Desired for a compressor in about an arrangement of the control characteristics according to Figures 3 and 7 with the specified inertia of the swash plates according to Table 1 and Table 2.
  • the Regelkenn ⁇ lines from the diagram of Fig. 3 show in comparison to the control characteristics
  • FIG. 7 shows the desired effect in a comparatively weaker form, whereas the effect in the control characteristics according to FIG. 7 is more pronounced.
  • the control characteristics for high speeds have an intersection with the x-axis, which means that the angle of maximum Aus ⁇ steering for high speeds is less than the angle of maximum deflection for nied ⁇ rige speeds.
  • control characteristics for speeds have such an intersection above about 4000 U / min, ie reduce the angle of maximum deflection of the swash plate.
  • stroke volume it is desirable to limit the stroke volume to about 50% or less, with high speeds as noted above being about 8000 rpm in modern compressors.
  • the Abregein of the compressor would also be achievable by a control intervention, which in addition to the temporal inertia, which includes the control intervention, also ener ⁇ Tische losses play a major role here.
  • the compressor operation initially (at least until the regulation corrected this again and the stroke volume is reduced) requires a very high torque, which is of course extremely undesirable, in particular during overtaking of the vehicle.
  • the safety is increased in a compressor according to the invention, since disturbances of the control valve, for example, by contamination, blocking of the valve seat, icing or the like impair or hinder a control intervention.
  • a strong increase in pressure, especially in high-pressure refrigerants such as CO 2 is very easily a security risk in such a case. Therefore, it makes sense to make at high speed larger tilt angle of the swash plate not reachable.
  • Figures 3, 4, 5, 6 and 7, which relate to compressors in which the high-pressure refrigerant CO 2 is used, qualitativelys ⁇ course also for other refrigerants, such as R134a, R152a etc ., can be used. Only the y-axis of the diagrams would have to be adjusted with respect to the indicated pressures.
  • the desired control characteristic (with points of intersection of the corresponding curves with the x-axis) is achieved essentially by a suitable selection of M sw and M k .
  • the fine adjustment of the desired Regel ⁇ characteristic can also be done by other means, such as a suitable selection of the spring constant of the return spring.
  • Fig. 8 in which the interaction between the tilt angle of the swivel or swash plate and the pressure in the engine room or the differential pressure between the engine and the suction chamber is shown as a function of various parameters.
  • Fig. 8 can be the
  • a steeper control characteristic can be achieved.
  • a throttling on the suction side for example by means of a variable or even fixed cross section, results in a curve shifted parallel to lower pressures compared to the control characteristic without additional actuating force.
  • An analogue control characteristic results when the return spring is preloaded.
  • the desired control characteristic with intersections of the corresponding curve with the X-axis at the desired location can be generated in a simple manner, the variety of possibilities a wide range of control (depending on the application of the compressor) allows.
  • one or more measures can be combined and thus any desired control characteristics can be achieved.

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

Abstract

L'invention concerne un compresseur à pistons axiaux, notamment un compresseur destiné au système de climatisation d'un véhicule automobile, comportant un carter et une unité compresseur, logée dans ce dernier, entraînée par l'intermédiaire d'un arbre d'entraînement et servant à aspirer et à comprimer un réfrigérant. L'unité compresseur présente des pistons effectuant un mouvement alternatif dans le sens axial dans un bloc cylindre et un plateau pivotant (plateau oscillant, disque oscillant ou bague pivotante), entraînant les pistons, solidaire en rotation de l'arbre d'entraînement. Ce plateau pivotant est conçu ou monté de sorte que son basculement soit limité automatiquement de façon à ce que, à des vitesses de rotation élevées du compresseur, en particulier à des vitesses de rotation très élevées ou à la vitesse de rotation maximale, l'angle de la déviation maximale du plateau pivotant soit inférieur à l'angle de la déviation maximale amax à de faibles vitesses de rotation du compresseur.
PCT/EP2005/008530 2004-08-18 2005-08-05 Compresseur a pistons axiaux WO2006018162A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US11/660,521 US20090104048A1 (en) 2004-08-18 2005-08-05 Axial Piston Compressor
EP05771046A EP1778977A1 (fr) 2004-08-18 2005-08-05 Compresseur a pistons axiaux

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004040042A DE102004040042A1 (de) 2004-08-18 2004-08-18 Axialkolbenverdichter
DE102004040042.3 2004-08-18

Publications (1)

Publication Number Publication Date
WO2006018162A1 true WO2006018162A1 (fr) 2006-02-23

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2005/008530 WO2006018162A1 (fr) 2004-08-18 2005-08-05 Compresseur a pistons axiaux

Country Status (4)

Country Link
US (1) US20090104048A1 (fr)
EP (1) EP1778977A1 (fr)
DE (1) DE102004040042A1 (fr)
WO (1) WO2006018162A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007134760A1 (fr) * 2006-05-23 2007-11-29 Valeo Compressor Europe Gmbh Procédé de régulation du débit massique de fluide frigorigène d'un compresseur
WO2007134665A1 (fr) * 2006-05-23 2007-11-29 Valeo Compressor Europe Gmbh procédé de régulation du flux massique de fluide frigorigène d'un compresseur

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5857402A (en) * 1996-08-05 1999-01-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor method and apparatus
EP0907020A1 (fr) * 1997-01-24 1999-04-07 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compresseur a plateau oscillant a cylindree variable presentant un element ameliore de support de plateau oscillant
DE19839914A1 (de) * 1998-09-02 2000-03-09 Luk Fahrzeug Hydraulik Axialkolbenmaschine
EP1091122A2 (fr) * 1999-10-08 2001-04-11 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compresseur à capacité variable
EP1167760A2 (fr) * 2000-06-19 2002-01-02 Kabushiki Kaisha Toyota Jidoshokki Compresseur à plateau en biais
US20020040638A1 (en) * 2000-10-11 2002-04-11 Halla Climate Control Corporation Swash plate compressor having variable capacity

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5857402A (en) * 1996-08-05 1999-01-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor method and apparatus
EP0907020A1 (fr) * 1997-01-24 1999-04-07 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compresseur a plateau oscillant a cylindree variable presentant un element ameliore de support de plateau oscillant
DE19839914A1 (de) * 1998-09-02 2000-03-09 Luk Fahrzeug Hydraulik Axialkolbenmaschine
EP1091122A2 (fr) * 1999-10-08 2001-04-11 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compresseur à capacité variable
EP1167760A2 (fr) * 2000-06-19 2002-01-02 Kabushiki Kaisha Toyota Jidoshokki Compresseur à plateau en biais
US20020040638A1 (en) * 2000-10-11 2002-04-11 Halla Climate Control Corporation Swash plate compressor having variable capacity

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007134760A1 (fr) * 2006-05-23 2007-11-29 Valeo Compressor Europe Gmbh Procédé de régulation du débit massique de fluide frigorigène d'un compresseur
WO2007134665A1 (fr) * 2006-05-23 2007-11-29 Valeo Compressor Europe Gmbh procédé de régulation du flux massique de fluide frigorigène d'un compresseur

Also Published As

Publication number Publication date
EP1778977A1 (fr) 2007-05-02
DE102004040042A1 (de) 2006-02-23
US20090104048A1 (en) 2009-04-23

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