EP0809026B1 - Compresseur - Google Patents

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Publication number
EP0809026B1
EP0809026B1 EP97100207A EP97100207A EP0809026B1 EP 0809026 B1 EP0809026 B1 EP 0809026B1 EP 97100207 A EP97100207 A EP 97100207A EP 97100207 A EP97100207 A EP 97100207A EP 0809026 B1 EP0809026 B1 EP 0809026B1
Authority
EP
European Patent Office
Prior art keywords
plate
spring
compressor according
arrangement
swash plate
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 - Lifetime
Application number
EP97100207A
Other languages
German (de)
English (en)
Other versions
EP0809026A1 (fr
Inventor
Harry Stentoft-Nissen
Stig Helmer. Jorgensen
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
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 US08/859,992 priority Critical patent/US5894782A/en
Publication of EP0809026A1 publication Critical patent/EP0809026A1/fr
Application granted granted Critical
Publication of EP0809026B1 publication Critical patent/EP0809026B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04B27/1804—Controlled by crankcase pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18296—Cam and slide
    • Y10T74/18336—Wabbler type

Definitions

  • the invention relates to a compressor with at least a piston movable in a cylinder, a drive shaft and a swash plate arrangement between the piston and the drive shaft, which is a swash plate having a variable inclination angle, and with a spring assembly on the swash plate assembly acts in the direction of minimal displacement.
  • Compressors of this type are used, for example, in motor vehicle air conditioning systems.
  • refrigerants used to date.
  • CO 2 carbon dioxide
  • this refrigerant requires relatively high pressures. Accordingly, the force to be applied by the spring must be correspondingly large.
  • one does not want to increase the size of the compressor The space available is limited, particularly in the motor vehicle sector, where such compressors have to be accommodated in the engine compartment.
  • US-A-41 78 136 shows a multi-compressor one cylinder movable piston, one drive shaft and a swash plate arrangement between the pistons and the drive shaft, which is a variable swash plate Inclination angle, and with a control arrangement, the the angle of inclination of the swash plate assembly changed.
  • the control arrangement has one Control piston, which is movable in a cylinder under the action of hydraulic pressure in a pressure chamber.
  • the control piston moves one Sleeve on the shaft on which the swash plate assembly is articulated.
  • the invention has for its object a compressor to be able to operate even at higher pressures.
  • the spring arrangement is preferably adjacent to a wall arranged an interior of the compressor surrounds. This turns the inside of the compressor into a Available space is used optimally. A Diameter increase of the compressor to the outside not mandatory. Still, it becomes possible to use the spring arrangement radially relatively far out.
  • the spring arrangement is preferably essentially on arranged in the same radius as the piston. In order to the force exerted by the piston is counteracted there, where it originates. Piston and point of application the spring arrangement are then essentially on the same axial line.
  • the spring arrangement between the swash plate arrangement is advantageous and a rotatable base plate clamped. This allows the large diameter the spring arrangement also on that of the swash plate arrangement Maintain the opposite side.
  • the spring can in total in an at least approximately cylindrical one Space can be accommodated without them Support purposes should somehow rejuvenate.
  • the spring arrangement radially outside of a Adjustment mechanism for the swashplate inclination angle is arranged. This also ensures that the forces of the spring arrangement act approximately where the opposing forces of the piston or pistons arise. Moreover is ensured in this way that the spring assembly and the adjustment mechanism is not mutually exclusive hinder. Is radial within the spring arrangement enough space available to the adjustment mechanism to be able to accommodate.
  • the swash plate arrangement preferably has one Pressure plate on which the spring arrangement rests. This provides a relatively large area, which is able to withstand the forces of the spring assembly record and attached to the swashplate assembly pass on.
  • the adjustment mechanism through an opening in the pressure plate is led. This ensures that there is no larger one Height of the compressor is required, although the Pressure plate is used. The pressure plate and the Adjustment mechanism can then, so to speak, in one another to be nested. Despite the presence of the adjustment mechanism becomes an application of pressure plate possible where this is desired. Any Restrictions on the arrangement of the Adjustment mechanism arise from the spring arrangement Not.
  • the pressure plate advantageously has a neck that surrounds the drive shaft and the one on the drive shaft axially displaceable bearing arrangement of the Swashplate.
  • This neck i.e. one of the Pressure plate axially protruding circumferential projection secures on the one hand, a relatively good axial guidance of the pressure plate on the drive shaft. This prevents tipping the pressure plate in relation to the drive shaft. About that this also results in simple transmission options the forces from the spring assembly over the pressure plate on the swash plate assembly.
  • the swash plate arrangement preferably has one both with respect to the swashplate and opposite the swash plate rotates on the piston. In operation then the swashplate rotates, somewhere between the speed of the drive shaft, with which the swashplate rotates, and zero what the "Speed" corresponds to the piston. The speed the swashplate will automatically adjust itself that the smallest amount of energy is necessary. With others Words make the losses as small as possible held. With this configuration, on the one hand, that the swash plate is relatively wide radially can act outside, so that the pistons essentially be loaded purely axially. This ensures that the Pistons in the cylinders are not loaded on one side, which reduces wear. On the other hand, must are not necessarily large relative speeds between the pistons and the swash plate, which in turn lead to higher losses in the warehouse would.
  • the swashplate is advantageous compared to the swashplate radially inside or in the area of the adjustment mechanism supported. This ensures that the Compressive forces of the pistons more or less directly on the Pressure plate can be transferred.
  • the spring arrangement a coaxially arranged around the drive shaft Spring on.
  • the spring then surrounds, if necessary by far, the drive shaft. This is a very easy way, especially with regard to the assembly.
  • the spring in the circumferential direction has a non-uniform pressure distribution and Anti-rotation and positioning device provided which is the area with the highest pressure in the area fixed at the top dead center of the swash plate.
  • a coil spring is used as the spring is made, whose two end faces have been made parallel are, for example by surface grinding.
  • the counterforce the spring where the surface grinding to a thinning of the last turn of the spring has led.
  • the one exerted by the pistons The counterforce in the circumferential direction is also not uniform. Shortly before reaching the top dead center of the Swashplate, i.e.
  • the spring arrangement has a plurality of individual springs which in a strip with a predetermined distance around the drive shaft are arranged around. Even with such The desired spring force amplification can be achieved on the one hand by individual springs achieve. The force on the swashplate assembly then results from the sum of Forces of the single springs. On the other hand, it can also compensate for the stress where it arises, namely more or less on the same axial line, on which the pistons are also arranged.
  • the individual springs have different spring constants. So that carries one takes into account the fact that, as explained above, in Circumferential direction on an uneven force distribution the swash plate arrangement works. Where the piston is just before its top dead center, is the counterforce the highest. It is therefore sufficient to also use the use appropriately strong springs. The remaining Feathers can then be weaker. They basically serve taken only to stabilize the swash plate arrangement, i.e. they are said to tip indefinitely prevent.
  • At least one individual spring is preferably a predetermined one Angle before top swashplate dead center arranged. As stated above, this is the Point where the highest load is expected. If the machine can be operated in both directions you should use two single springs.
  • a compressor 1 (FIG. 1) has a drive shaft 2 on. It is therefore also used as a shaft-driven compressor designated.
  • the drive shaft 2 is through a Shaft bushing 3 in a housing that out a front part 26, a middle part 27 and a rear part 28 exists.
  • the housing parts 26, 27, 28 are using known means, for example threaded bolts 29, connected to each other in the axial direction.
  • the piston 9 or the piston 9 is driven via a swash plate assembly 30.
  • the swash plate assembly 30 has a swash plate 5 which a swash plate 4 is rotatably mounted.
  • the swash plate 5 is in turn via slide bearing 7 connected to the piston 9.
  • the plain bearings 7 have hemispherical sliding shoes 8 on the front and rear, i.e. axially from both sides on the swashplate issue.
  • the sliding shoes 8 are correspondingly negative trained bearing shells 31, which in turn are attached in the piston 9.
  • the swash plate can on the one hand 5 turn freely in relation to piston 9.
  • the swash plate 5 can also change the radial orientation of the Change swash plate 5 to piston 9. this means for example, that the swash plate 5 in the event of a change the inclination of the swash plate 4 further radially outside or further in with respect to the piston 9 works.
  • the swash plate In the swashplate position shown 4, the swash plate is relatively far radially Outside. If the angle between the swash plate 4 and the drive shaft 2 enlarged, the pulls Swash plate 5 with its sliding surface accordingly further radially backwards. This ensures that the piston 9 is always subjected to a force can be essentially parallel to theirs Attacks direction of movement.
  • the cylinder points in a manner known per se 10 a suction valve opening 11 through which a coolant can be sucked in.
  • a pressure valve opening 12 provided via the compressed refrigerant can be output from the cylinder.
  • the pressure valve opening 12 can be closed by a valve element 32 become.
  • Appropriate valves for the suction valve opening 11 are not shown here, but at There is a need.
  • a base plate 16 is used to drive the swash plate 4 rotatably connected to the drive shaft 2.
  • the Base plate 16 is an articulated arm 13 rotatably connected.
  • the swash plate 4 is on one Pivotal point 14 connected to the articulated arm 13, i.e. she can be pivoted about this pivot point 14.
  • the articulated arm 13 is in turn via a Pivot 15 connected to the base plate 16.
  • a flange 25 is arranged and non-rotatably connected to it.
  • On the drive shaft 2 is a pressure plate 18 slidably arranged in the axial direction. Between the pressure plate 18 and the flange 25, a compression spring 17 is arranged and clamped. The compression spring 17 pushes the pressure plate 18 forward, i.e. to the left in the figure, thus pushing the Swashplate 4 also in this direction. Since the Swash plate 4 over the articulated arm 13 with the base plate 16 is connected, this leads to the fact that Swashplate assumes a slight inclination so that the Piston 9 performs a correspondingly small stroke.
  • the swash plate 4 is not just about this Swivel point pivotable, it also rotates around one Pivotal point 19 of a guide arrangement 20 that is common with the pressure plate 18 on the drive shaft 2 is displaceable in the axial direction.
  • the pressure plate 18 has a through opening 35, through which the articulated arm 13 is guided.
  • the compression spring 17 has a relatively large diameter, i.e. surrounds them the drive shaft 2 coaxial and can additionally also include the articulated arm 13 on the outside. This will pressurizing the pressure plate 18 relatively possible far outside without the function of the articulated arm 13 is affected by the compression spring 17. Corresponding This has a favorable effect on the dimensioning the compression spring 17 and the size of the compressor 1 off.
  • the compression spring 17 coaxially surrounds the shaft 2. she attacks on the pressure plate 18 relatively far outside, namely in the area of its radial edge. With that, the Compression spring 18 practically the largest diameter that is possible. It is the wall of the housing interior 33, which is formed here by the central part 27, adjacent. Of course there is a certain distance, because the compression spring 18 together with the Drive shaft 2 rotates.
  • the compression spring 17 virtually forms a wooden cylinder.
  • the Cylinder wall is on the same circumferential line, on which the pistons 9 are also arranged.
  • the pressure plate 18 has a neck 36 with which it is mounted on the drive shaft 2.
  • the neck 36 surrounds the drive shaft and ensures that the Pressure plate 18 even in a possibly one-sided Load their orientation perpendicular to the drive shaft 2 maintains.
  • the neck 36 of the pressure plate 18 acts against the guide arrangement 20 for the swash plate 4.
  • the compression spring 17 Because of their training as a coil spring, the is flattened on both sides, the compression spring 17 a non-uniform pressure distribution in the circumferential direction. This results among other things from the fact that the end turns 37, 38 of the compression spring 17 a decreasing Have strength.
  • the compression spring 17 is now opposite the pressure plate 18 aligned and held so for example by a pin 39 that the angular area with the greatest force under the upper one Dead center of the swash plate 4 is located.
  • the upper Dead center is the point at which the pistons 9 are their largest Deflection and the cylinder 10 its smallest volume occupies. Practicing shortly before this operating position the gas volume enclosed in the cylinder 10 is the largest Back pressure on the piston and thus on the Compression spring 17 out.
  • the piston 9 is on its outer surface with a groove 21 provided.
  • a pin 22 protrudes into the groove 21, for example by the end of a screw 23 is formed radially from the outside through the central part 27 of the housing has been screwed.
  • the pin 22 forms an anti-rotation device together with the groove 21 for the piston 9.
  • the piston 9 is in its back and forth movement Pulled out far into a housing interior 33. It is almost inevitable that a minor Amount of particularly gaseous refrigerant in the Housing interior 33 escapes or leaks. This constant Inflow of refrigerant leads to an increase the pressure inside the housing 33.
  • an opening 24 is provided, which with a schematically shown valve 34 is connected. With With the help of the valve 34, the pressure in the interior of the housing be lowered.
  • the other side of the valve can for example connected to the suction valve opening 11 be, so that the pressure in the housing interior 33 maximum can be reduced to the suction pressure of the compressor can.
  • the swash plate 5 can still freely in relation turn to the piston 9. You can also feel free in relation turn to the swash plate 4 so that a Set the speed of the swash plate 5 at which the friction forces that occur are the lowest. In this way, it is possible for the compressor 1 with a relatively good efficiency and a relative small wear works.
  • the forces on the piston 9 are practically limited to axial direction so that the piston 9 tilts opposite the cylinder 10 is avoided. This leaves the wear is small and the tightness of the compressor 1 correspondingly large.
  • the compression spring 17 instead of the one compression spring 17 there are now three individual springs 41, 42, 43 are provided, which are also used as compression springs are formed and between the flange 25 and the pressure plate 18 are arranged.
  • the compression springs 41-43 are also arranged so that they are as far as possible attack radially outside, i.e. in the area of the edge of the Pressure plate 18.
  • the springs 41-43 are on one Arranged in a circle. This is advantageous, however not necessarily.
  • the feathers also form in the present Fall an isosceles triangle whose base is through the springs 41, 42 is limited. This configuration too is beneficial but not mandatory.
  • the spring 43 has a weaker spring constant than that two other springs 41, 42, which are adjacent to the articulated arm 13 are arranged.
  • the articulated arm 13 is located at the point where the swash plate 4 has its upper Has dead center.
  • the springs 41, 42 are one predetermined angle before or after this top dead center, i.e. exactly where it is in cylinder 10 compressed gas develops its greatest resistance before it can escape from the cylinder 10. Basically taken only one of the two springs 41, 42 would be necessary. The other of the two springs 42, 41 is provided, however, so that you can turn the compressor in both directions can operate.
  • the third spring 43 basically serves taken only for stabilization to prevent that the pressure plate 18 tilts.
  • a larger one can also be used with the three individual springs Generate spring force than with the known individual Spring which is arranged around the drive shaft 2. So regardless of whether the spring arrangement by a Compression spring 17 formed with the drive shaft 2 surrounds as large a radius as possible, or whether it passes through Single springs 41-43 is formed, one can on this Way to operate a compressor at high pressure without that the size must be increased significantly.
  • FIG. 3 shows a third embodiment of a compressor, which corresponds essentially to that of FIG. 1.

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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)
  • Air-Conditioning For Vehicles (AREA)

Claims (15)

  1. Compresseur (1) avec au moins un piston (9) mobile dans un cylindre (10), un arbre moteur (2) et un agencement de plateaux oscillants (4, 5), compris entre le piston (9) et l'arbre moteur (2) et présentant un disque en nutation (4) d'un angle d'inclinaison variable, et avec un agencement élastique (17 ; 41 - 43) qui agit sur l'agencement de plateaux oscillants dans le sens d'un déplacement minimal, caractérisé en ce que l'agencement élastique (17 ; 41 - 43) attaque un bord radial d'une plaque de compression (18) qui agit sur l'agencement de plateaux oscillants (4, 5).
  2. Compresseur suivant la revendication 1, caractérisé en ce que l'agencement élastique (17 ; 41 - 43) est disposé au voisinage d'une paroi, qui enveloppe un espace interne (33) du compresseur.
  3. Compresseur suivant l'une des revendications 1 et 2, caractérisé en ce que l'agencement élastique (17 ; 41 - 43) est essentiellement disposé sur le même rayon que le piston (9).
  4. Compresseur suivant l'une des revendications 1 à 3, caractérisé en ce que l'agencement élastique (17 ; 41 - 43) est fixé entre l'agencement de plateaux oscillants et une plaque de base (25) montée en rotation.
  5. Compresseur suivant l'une des revendications 1 à 4, caractérisé en ce que l'agencement élastique (17 ; 41 - 43) est disposé dans le sens radial à l'extérieur d'un mécanisme de déplacement (13 - 15) pour l'angle d'inclinaison du disque en nutation (4).
  6. Compresseur suivant l'une des revendications 1 à 5, caractérisé en ce que l'agencement de plateaux oscillants présente une plaque de compression (18) sur laquelle s'applique l'agencement élastique (17 ; 41 - 43).
  7. Compresseur suivant la revendication 6, caractérisé en ce que le mécanisme de déplacement (13) est guidé au travers d'une ouverture (35) dans la plaque de compression (18).
  8. Compresseur suivant l'une des revendications 6 et 7, caractérisé en ce que la plaque de compression (18) présente un col (36), qui enveloppe l'arbre moteur et s'applique sur un agencement de palier (20), mobile dans le sens axial sur l'arbre moteur (2), du disque en nutation (4).
  9. Compresseur suivant l'une des revendications 6 à 8, caractérisé en ce que l'agencement de plateaux oscillants présente un plateau oscillant (5) pouvant tourner aussi bien par rapport au disque en nutation (4) que par rapport au piston (9).
  10. Compresseur suivant la revendication 9, caractérisé en ce que le plateau oscillant (5) est supporté dans le sens radial par rapport au disque en nutation (4) à l'intérieur ou dans la zone du mécanisme de déplacement (13).
  11. Compresseur suivant l'une des revendications 1 à 10, caractérisé en ce que l'agencement élastique présente un ressort (17) disposé de façon coaxiale autour de l'arbre moteur (2).
  12. Compresseur suivant la revendication 11, caractérisé en ce que le ressort (17) présente une distribution de pression irrégulière dans le sens périphérique et en ce qu'est prévu un dispositif de positionnement et de fixation (39), qui fixe la zone de pression maximale dans la zone du point mort haut du disque en nutation (4).
  13. Compresseur suivant l'une des revendications 1 à 10, caractérisé en ce que l'agencement élastique présente plusieurs ressorts individuels (41 - 43), disposés en une bande autour de l'arbre moteur à une distance prédéfinie.
  14. Compresseur suivant la revendication 13, caractérisé en ce que les ressorts individuels (41 - 43) présentent différentes constantes de rappel.
  15. Compresseur suivant l'une des revendications 13 et 14, caractérisé en ce qu'au moins un ressort individuel (41, 42) est disposé d'un angle prédéfini avant le point mort haut du disque en nutation (4).
EP97100207A 1996-05-24 1997-01-09 Compresseur Expired - Lifetime EP0809026B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US08/859,992 US5894782A (en) 1996-05-24 1997-05-21 Compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19621174 1996-05-24
DE19621174A DE19621174A1 (de) 1996-05-24 1996-05-24 Kompressor, insbesondere für Fahrzeug-Klimaanlagen

Publications (2)

Publication Number Publication Date
EP0809026A1 EP0809026A1 (fr) 1997-11-26
EP0809026B1 true EP0809026B1 (fr) 2001-07-18

Family

ID=7795356

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97100207A Expired - Lifetime EP0809026B1 (fr) 1996-05-24 1997-01-09 Compresseur

Country Status (8)

Country Link
US (1) US5826490A (fr)
EP (1) EP0809026B1 (fr)
AT (1) ATE203306T1 (fr)
DE (2) DE19621174A1 (fr)
DK (1) DK0809026T3 (fr)
FR (1) FR2749045B1 (fr)
GB (1) GB2313416B (fr)
PT (1) PT809026E (fr)

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DE10058447C1 (de) 2000-11-24 2002-01-17 Zexel Valeo Compressor Europe Axialkolbenverdichter für Fahrzeugklimaanlagen
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JPH08189464A (ja) * 1994-11-11 1996-07-23 Toyota Autom Loom Works Ltd 可変容量型圧縮機
TW353705B (en) * 1995-06-05 1999-03-01 Toyoda Automatic Loom Works Reciprocating piston compressor

Also Published As

Publication number Publication date
DE59704059D1 (de) 2001-08-23
PT809026E (pt) 2001-10-31
US5826490A (en) 1998-10-27
FR2749045B1 (fr) 2001-01-05
ATE203306T1 (de) 2001-08-15
FR2749045A1 (fr) 1997-11-28
EP0809026A1 (fr) 1997-11-26
GB2313416A (en) 1997-11-26
GB2313416B (en) 2000-02-09
DE19621174A1 (de) 1997-11-27
GB9710499D0 (en) 1997-07-16
DK0809026T3 (da) 2001-11-19

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