EP1872013B1 - Axial piston compressor - Google Patents
Axial piston compressor Download PDFInfo
- Publication number
- EP1872013B1 EP1872013B1 EP06723979.8A EP06723979A EP1872013B1 EP 1872013 B1 EP1872013 B1 EP 1872013B1 EP 06723979 A EP06723979 A EP 06723979A EP 1872013 B1 EP1872013 B1 EP 1872013B1
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- EP
- European Patent Office
- Prior art keywords
- drive shaft
- compressor according
- support
- power transmission
- support element
- 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.)
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Classifications
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- 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
- F04B27/1072—Pivot mechanisms
Definitions
- the present invention relates to an axial piston compressor, in particular compressor for motor vehicle air conditioning systems, according to the preamble of claim 1.
- sliding blocks are provided between it and the spherically curved inner wall of the engaging chamber on both sides, so that the swivel ring slides in its orbit between them.
- the drive transmission from the drive shaft to the pivot ring is effected by a driving pin fixed in the drive pin, the spherical head engages in a radial bore of the pivot ring.
- the position of the driver head is chosen so that its center coincides with that of the spherical segments.
- this center point is on a circular line connecting the geometric axes of the seven pistons, and continues on a circular line, the centers the spherical joint body connects the pistons. In this way, the top dead center position of the piston is determined and ensures a minimum dead space.
- the head shape of the free Mit supportiveendes allows the change in the inclination of the swash plate, in which the driver head forms a bearing body for a stroke of the piston changing pivotal movement of the swash plate.
- the bearing axis is formed by two coaxially mounted on both sides of a sliding sleeve bearing pin, which are also mounted in radial bores of the swash plate.
- the sliding sleeve preferably has bearing sleeves on both sides which bridge the annular space between the sliding sleeve and the swashplate in the manner of a spoke.
- the force for the angular adjustment of the swash plate and thus for a control of the compressor results from the sum of each of the two sides of the piston against each other acting pressures, so that this force is dependent on the pressure in the engine room.
- the pressure in the engine cavity can be regulated according to the state of the art between a high and a low pressure and accordingly engages in the equilibrium of forces at the swashplate. This affects the inclination of the same.
- the position of the sliding sleeve can be influenced by springs, which also belong to the prior art in various variants.
- the decisive for the delivery position of the sliding sleeve is co-determined by acting on the swash plate inertial forces, wherein the swash plate adjusted with increasing rotational speed, ie changes its tilt angle or tilt angle.
- the trend is to use swash plates with such inertia, which cause a reduction in the stroke of the piston and thus a reduction in the capacity at increasing rotational speed.
- the objects of the EP 0 964 997 B1 and the JP 2003-269330 AA are constructed very expensive, which requires a high number of parts and thus costs, in addition, the storage is overdetermined by two drivers and thus susceptible to wear and the strength of the components, in particular by a hole reveal the shaft is rather low.
- DE 101 52 097 A1 Another compressor is out of the DE 101 52 097 A1 known, which differs significantly from the objects of the above-discussed documents.
- the driver in particular the spherical driver head, is replaced by a hinge pin or bolt.
- this is integrated from the outside into the swash plate and secured with a cup-shaped drive plate, which is part of the drive shaft assembly.
- the subject of DE 101 52 097 A1 has a complex construction, and in addition it should be noted that a large imbalance may occur depending on the tilt angle. This promotes the wear of the compressor and thus reduces its life.
- Another compressor is out of the FR 278 21 26 A1 known, which has a driver which extends radially from the drive shaft and engages in the swash plate. Similar to the solution according to the DE 101 52 097 A1 , In this construction, the swash plate is fixedly mounted on the driver in the radial direction. This is also a key difference in terms of the objects of EP 0 964 997 B1 and the JP 2003-269330 AA.
- the advantage of this concept is that the forces or the surface pressure due to the applied forces (due to the fact that it is relatively small forces) do not cause excessive deformation on and in the driver, whereby the driver can be designed according to lightweight and the tilting of the swash plate can be done relatively hysteresis-free. Disadvantageously, however, it may have the effect that the spherical driving head in a relatively large recess of the swash plate lies.
- the Hertzian pressure can be or must be described by a geometry pairing plane / ball, which is relatively unfavorable, since it requires a high Hertzian pressure.
- DE 10 2005 004 840 From the also unpublished and attributed to the applicant DE 10 2005 004 840 Finally, a compressor is known which offers an improvement in the problem of surface pressure.
- the object of DE 10 2005 004 840 has a supporting element engaging with a pivoting ring, there being a line contact between the supporting element and the pivoting ring. This represents an improvement with respect to the Hertzian pressure in comparison to the prior art explained above.
- it is advantageous for the object of the DE 10 2005 004 840 a drive torque and a twisting torque are decoupled from the gas power support.
- a relatively large recess in the swash plate is necessary so as to ensure a sufficient length of the line contact and to achieve a correspondingly low surface pressure.
- the large recess in the swash plate could lead to deformation of the swivel ring and thus wear due to the gas forces to be transmitted. Furthermore, the Abregel the swash plate (which is dependent on the Deviationsmoment respect to the tilting joint) and the imbalance thereof are adversely affected by a large recess.
- the mass of the gas force support attacks the object of the DE 10 2005 004 840 not with the moment of deviation.
- An essential point of the invention is therefore that a power transmission element is rotatably and / or radially displaceable articulated on the support element.
- the power transmission element may be non-rotatably and / or radially immovably connected to the drive shaft, which ensures a simple construction of a compressor according to the invention.
- the force transmission element can also be rotatably mounted in the drive shaft.
- both the power transmission element and the support element are formed in the shape of a cylinder bolt.
- such a structure is structurally or production-technically easy to implement and, in particular, ensures a low Hertzian pressure between the supporting element and the swashplate due to the cylinder-bolt-shaped design of the support element.
- the support element and the force transmission element form an approximately T-shaped gas force support.
- the support member optionally includes a recess into which engages the force transmission element.
- This recess is in particular a bore, whereby a simple and cost-effective design of a compressor according to the invention is ensured.
- the support element may also be mounted in a cylindrical recess, in particular in a bore in the swash plate.
- the bore extends perpendicular to the drive shaft axis.
- the support element and the force transmission element essentially serve only for the axial support of the pistons and / or a gas force support, while a device independent thereof, in particular a joint connection between Drive shaft and swivel disk essentially only the torque transmission is used.
- a device independent thereof in particular a joint connection between Drive shaft and swivel disk essentially only the torque transmission is used.
- the power transmission element is rotatably mounted in the drive shaft, while the support element is non-rotatably engaged with the force transmission element.
- the power transmission element is optionally a bolt having an at least partially approximately circular or semi-elliptical cross-section.
- the swash plate is preferably pivotally mounted on a longitudinally displaceably mounted along the drive shaft sliding sleeve, wherein the swash plate is connected via drive bolts with the sliding sleeve and / or the drive shaft.
- the drive bolts may be pressed into the sliding sleeve or the swash plate or be secured by axial securing elements in the same.
- the drive bolts preferably protrude into a recess, which may be present in particular in the form of a groove in the drive shaft.
- a connecting element in particular in the form of a feather key, is arranged between the drive shaft and the sliding sleeve, which permits a transmission of forces or moments in the radial direction and is mounted axially displaceably on the drive shaft.
- the support element facing away from the end of the power transmission element can project through the drive shaft and into a longitudinal slot on the sliding sleeve such that a drive torque is transmitted from the drive shaft to the sliding sleeve by the support member remote from the end of the power transmission element.
- Areas of the recess in the swash plate which may be present in particular in the form of a bore, which are not filled by the support element, are preferably filled with a balance weight, in particular in the form of a closure element or with balancing weights in the form of closure elements.
- a device for a reliable transfer of the torsional torque can be provided between the sliding sleeve and the swash plate, a device, in particular at least one cylindrical pin-like element or support or contact surfaces to support an attacking in the drive shaft twisting moment.
- the force transmission element in particular the longitudinal axis of the same, is optionally arranged offset relative to the torque axis, in particular the drive shaft axis.
- the support element and / or the power transmission element can be designed in several parts.
- the force transmission element may further be formed angled, in particular it may comprise a perpendicular to the tilting moment axis and extending therethrough section.
- the power transmission element may be arranged eccentrically in the drive shaft.
- the swivel plate can be made of steel, brass or bronze. Also conceivable is a multicomponent or multi-material swash plate, which comprises combinations of the abovementioned materials. All the materials mentioned above provide good strength and rigidity for the structural design of the swivel disk. Due to the relatively high density of the materials, in particular of bronze or brass, results in an advantageous mass distribution, so that the translational moments of the piston masses can be optimally compensated by the rotational moments of the swash plate. In particular, but not exclusively, in the case where the swash plate is made of steel, it may have a low-wear coating, resulting in a long life of a compressor according to the invention.
- the pistons are made in a preferred embodiment of aluminum or an aluminum alloy, whereby the weight of a corresponding compressor can be kept low.
- the pistons may also be made of steel or a steel alloy, which leads to a high strength of the same, with a matched to the material of the swash plate choice of material (similar coefficients of thermal expansion) is advantageous.
- the support element is barrel-shaped or cigar-shaped or cylindrical, the cylinder having a tapering diameter from the cylinder center to the cylinder ends (axial direction).
- This can ensure that there is only a line contact between the support member and the swash plate and thus jamming between the two components are excluded.
- the line contact is particularly suitable in the case of a swashplate made of steel also for power transmission, so that the embodiment described above, both in combination with drive pin for transmitting torque as well as without the same, i. So in a case in which the force is transmitted via the force transmission element and the support element, is conceivable and advantageous.
- All preferred embodiments of a compressor according to the invention include (not shown in the drawings) a housing, a cylinder block and a cylinder head.
- pistons are mounted axially movable back and forth.
- the compressors are driven by means of a belt pulley by means of a drive shaft 1.
- the present compressors are variable piston-stroke compressors, the piston stroke being regulated by a pressure difference defined by the pressures on a suction-gas side and in an engine chamber.
- the pressure difference is a swash plate in the form of a swivel ring 2 more or less deflected from its vertical position or pivoted. The larger the resulting swing angle, the larger the piston stroke, and accordingly, the higher the pressure at an outlet side of the compressor.
- the swashplate mechanism of a first preferred embodiment of a compressor according to the invention includes.
- the support member 5 is rotatably and radially displaceable articulated on the power transmission element 6, while the power transmission element 6 rotatably and radially non-displaceably connected to the drive shaft 1.
- Both the support element 5 and the force transmission element 6 is formed in the shape of a cylinder bolt.
- the support element 5 is rotatably and radially displaceably articulated on the force transmission element 6, which takes place via a recess 8 in the support element 5, in which the force transmission element 6 engages.
- This recess 8 is in the form of a hole in the support member 5.
- the support element 5 and the force transmission element 6 form an approximately T-shaped gas force support 9 in the assembled state (cf., for example Fig. 3 ).
- the support element 5 is mounted in the swivel ring 2 in a cylindrical recess 10, which is in the form of a bore in the first preferred embodiment described here.
- the bore 10 extends perpendicular to the drive shaft axis 11.
- the sliding sleeve 3 has two flattened sides 13 (off Fig. 1 only a flattened side is visible), which are in sliding engagement with corresponding flats 14 on the pivot ring 2.
- the drive bolts 7 also ensure a connection between the sliding sleeve 3 and the drive shaft 1 and a resulting force or torque transfer.
- the drive pin 7 protrude into a recess in the drive shaft in the form of grooves 15 (wherein Fig.
- the drive pin 7 are pressed into corresponding recesses 17 in the pivot ring 2. It should be noted at this point that the drive pin 7 can also be pressed into the sliding sleeve 3 as an alternative to pressing in the pivot ring 2.
- the spring 4 serves as a connecting element, which is arranged between the drive shaft 1 and the sliding sleeve 3, and allows a transfer of forces in the axial direction. It is mounted axially displaceably on the drive shaft 1.
- the support element 5 facing away from the end of the power transmission element 6 projects through a longitudinal slot 18, which is formed on the sliding sleeve 3, in the drive shaft 1 in.
- the sliding sleeve may be formed such that a longitudinal slot 18 opposite longitudinal slot is provided on the sliding sleeve, in which the support member 5 opposite end of the power transmission element 6 projects and thus transmits a drive torque from the drive shaft 1 to the sliding sleeve 3.
- Fig. 1 in an exploded view shown construction is in Fig. 2 shown in a joined state.
- Fig. 2 can be seen that the support member 5, the bore 10 in the pivot ring 2 is not completely filled.
- These areas, which are indicated by arrows 19, 20 and not filled by the support member 5 are (in the Fig. 2 not shown) closed with a balance weight in the form of a closure element and filled by this substantially.
- the kinematics of the pivot ring 2 can be optimized so that a desired control behavior results in or amplified, which usually means in compressors modern design that the compressor for increasing speed has an increasingly abregard tendency.
- Fig. 6a is a section along the plane EE of Fig. 3 shown. Since the cylinder-bolt-shaped or barrel-shaped contour of the support element 5 has a non-negligible extension perpendicular to the plane of the twisting torque (indicated by the axis of the twisting torque 22), a twisting moment (which acts perpendicular to the tilting moment of the pivoting ring and inter alia occurs because the maximum gas force occurs on a piston at the time of opening of the valve and not at the dead center of the piston) there, that is, therefore, be introduced to the cylindrical support member 5, if not according to the invention mounted rotatably about its central axis in the power transmission element 6.
- a construction according to the invention ensures that the twisting moment (torsion) is introduced only into the elements provided for this purpose, which may be, for example, the pin-like drive bolts 7 or also any support surfaces.
- An introduction of the torque in the power transmission element 6 is excluded by a construction according to the invention.
- the axis of the torque is denoted by the reference numeral 22 (see. Fig. 6a ).
- FIG. 6b An alternative embodiment is in Fig. 6b in a representation analogous to Fig. 6a shown.
- the support element 5 has a cigar-shaped contour, ie the support element 5 is shaped like a cylinder, which in the cylinder center has its largest diameter and then decreases in diameter in the direction of the cylinder ends.
- a separation of the Antziebsfunktion and the function is achieved as a gas force support, since there is no surface contact between the support member 5 and swivel ring 2.
- both compressors are provided in the present invention, which can transmit the driving torque from the shaft to the pivot ring completely or partially by the nature of the support of the support member 5 and the power transmission element 6, and compressor provided are in which the transmission of the drive torque substantially not by the support member 5 and the power transmission element 6, but as described above, carried by the drive pin 7.
- a line contact would be sufficient to transmit torques.
- the representation of the barrel shape as in Fig. 6b may be very excessive, but it is also conceivable a kind of "crowning" in the micrometer range.
- the swivel ring 2 made of steel and provided with a coating in the embodiment described above is wear and friction minimized between the sliding blocks of the piston and the pivot ring 2, alternatively can be made of brass or bronze.
- the materials mentioned ensure that the design requirements are met.
- the pivoting rings 2 used are namely rings that are very high compared to the prior art.
- the height is desired in order to be able to support the gas force support, which is composed of support element 5 and force transmission element 6, on the other hand, the height is advantageous in order to be able to assign the component a sufficient mass inertia.
- the mentioned materials such as steel, brass or bronze offer particular, since due to the height of the swivel ring 2 these materials Ensure sufficient strength and rigidity to prevent deformation. In swivel rings according to the prior art, this is often not secured.
- the density of bronze or brass may be slightly greater than the density of steel or gray cast iron (a swivel ring 2 according to the invention may of course also be made of gray cast iron). The density increase or the higher density of bronze or brass can be used to even better compensate or overcompensate the piston masses.
- the height of the swivel ring 2 causes the pistons, which in the application discussed here comprise the swivel ring 2 and are mounted by means of two sliding blocks on this, have to have a large opening for embracing the swivel ring 2.
- the pistons are made of an aluminum alloy. Since brass has an aluminum-like thermal expansion, such a combination of materials for a reduced wear and increased life of a compressor according to the invention, since the play of the sliding blocks in the piston compared to the state during assembly increases only slightly or not at all. This leads to a low noise and prevents sliding blocks can fall out due to a large game. If the swivel ring 2 is made of steel, then pistons, which are also made of steel, offer the same advantages. Alternatively, however, other material combinations (in particular from the viewpoint of a weight reduction of a compressor according to the invention) are conceivable.
- the gas power support 9 largely and preferably free of torque (insofar as a construction is chosen in which the power transmission element 6 on its side facing away from the support member 5 is not in torque transmitting Engagement with the sliding sleeve 3 is), the support function of the pivot ring 2 true with respect to the axially acting piston forces;
- the support member 5 is a large area, ie cylinder bolt or barrel-shaped, with torsional torques can not be initiated because the gas force support 9 either at the transition between the power transmission element 6 and support member 5 or (as will be described below) by a rotatable mounting of the Power transmission element 6 can align in the drive shaft 1 about its central axis; the drive torques are transmitted in a defined manner in the plane perpendicular to the tilting plane of the pivoting ring, it being noted here that there are various possibilities of power transmission or torque transmission.
- the pivot ring 2 is connected via the drive pin 7 with the sliding sleeve 3 and with the drive shaft 1.
- the sliding sleeve 3 is axially displaceably mounted on the drive shaft 1 and allows in conjunction with the spring 4, the drive pin 7 and the gas force support 9, the adjustment of the pivot angle of the pivot ring 2.
- the adjusting pivot angle depends on the gas forces, the inertial properties of the pivot ring 2 and the engaging with this piston, as well as the spring force of the spring 4 from.
- the sum of the moments about the tilting axis 21 is in other words equal to zero (tilting moments equal to zero).
- the drive pin 7 are axially secured against falling out, which takes place in that the bolts are pressed into the sliding sleeve 3 or the pivot ring 2.
- the transmission of the drive torque takes place in the present preferred embodiment directly via the drive pin 7 of the drive shaft 1 on the pivot ring 2.
- Drive pin 7 there are elements (for example Drive pin 7), which are connected to the shaft 1 or project into this.
- Fig. 1 is shown as the drive pin 7, which are connected to the pivot ring 2, project into a groove 15 in the drive shaft 1. Thereby, the drive torque is transmitted directly from the drive shaft 1 to the swing ring 2 by the drive bolts 7.
- a connecting element between the drive shaft 1 and sliding sleeve 3 which allows the transmission of forces or moments in the radial direction, but for example by sliding in a groove of the sliding sleeve 3 allows the axial displacement of the sleeve.
- a connector could e.g. to be a feather key.
- the support member 5 opposite end of the power transmission element 6 is passed through the shaft and protrudes into a slot of the sliding sleeve 3, in which the power transmission element 6 is tightly guided and thereby can transmit the drive torque. Flattenings on the sliding sleeve 3 and the swivel ring 2 then transmit the torque to the swivel ring 2.
- a central point of the present invention is the design of the gas force support 9.
- a gas force support 9 is provided, which is relieved on the one hand, that it transmits no drive torque, but on the other hand with respect to the surface pressure, which results from the transmission of the gas forces , is optimized.
- the power transmission element 6 is rotatably mounted in the drive shaft 1, while the support member 5 rotatably with the power transmission element 6 is engaged.
- the power transmission element 6 is a bolt with a partially semi-elliptical cross section.
- a partially semicircular cross section would come into question.
- the said semi-elliptical cross-section is made in particular Fig. 8b clear.
- the power transmission element 6 is rotatably mounted in the drive shaft 1 about its longitudinal axis.
- the power transmission element 6 has a shoulder 23, which determines the position thereof (in particular in the radial direction) in the drive shaft 1.
- a securing element 24 ensures a safe whereabouts of the gas force support 9 and the support member 5 and the power transmission element 6 in the drive shaft 1.
- the drive pin 7 (from the FIGS. 8a and 8b not apparent) the connection between the sliding sleeve 3 and the drive shaft 1 and the resulting force or torque transfer safely.
- Another possible embodiment comprises a force transmission element 6 which is angled and comprises a section parallel to the axis 22 of the torque and a section extending therethrough.
- the imbalance due to the storage and tilting of the swash plate and other parts associated with the mass characteristics of the swash plate are very low.
- the moment of inertia of the swashplate and other parts attributable to the mass characteristics of the swashplate with respect to the tilting axis are optimized in terms of installation space, i. the compressor has for high speeds and over the entire deflection angle range of the swivel ring 2, i. So in particular, even for small deflection on a regulatory behavior.
- the support member 5 is able by the appropriate design to be able to absorb forces over a large area, resulting in a low Hertzian pressure.
- the gas force support 9 is free of torque that is transmitted between the shaft and swash plate, so that an over-determination of the power transmission function (resulting in a terminal) is avoided. Furthermore, the rigidity of the pivot ring 2 is optimized and an articulation of the pivot ring 2 to the support element 5 is achieved with a low surface pressure, i. ensured a low Hertzian pressure.
- the driving torque could be transmitted from the force-transmitting into the drive shaft 1 power transmission element 6 on the support member 5, but not directly on the pivot ring 2, since the power transmission element 6 in the radial direction (with respect to the drive or the shaft) is not applied (correspondingly large recess in the swivel ring).
- the support member 5 has in the radial direction of the engine / the drive shaft (axial direction with respect to the support member 5) no contact or no contact with the pivot ring 2. Therefore, the gas force support 9, which consists of the power transmission element 6 and the support member 5, the Drive torque is not transmitted to the swivel ring 2.
- the gas forces are transmitted through a bore in the pivot ring 2 on the cylinder pin-shaped support member 5 and then in turn from the bore in the support member 5 to the power transmission element 6. It will be the forces each transferred from a hole on a cylinder with a tight play. This results in significantly lower surface pressures (surface contact) and thus lower wear than in compressors according to the prior art.
- a further significant advantage results with respect to the inertia properties of the swivel ring 2 in combination with the support member 5.
- the support member 5 is connected to the swash plate so that the mass forces due to the mass of the support member 5 with respect to the tilting joint of the swivel ring 2 act directly on the swivel ring 2 (Deviation moment of the arrangement).
- the components of the gas force supports 9 have a very simple geometry and few working surfaces (for example, two cylinders in which one has a bore).
- the essential components of the forces occurring in the swivel ring are transmitted through the Gaskraftstüt2e 9 to the drive shaft and then ultimately collected in the storage of the shaft.
- the support member 5, the recess in the pivot ring 2 as far as possible fills was taken to ensure that the support member 5 does not collide at any possible deflection angle of the pivot ring 2 with the piston.
- the permanent recesses that are not filled by the support member 5, for example, can be filled by plug such that the kinematics of the compressor is optimized.
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Description
Die vorliegende Erfindung betrifft einen Axialkolbenverdichter, insbesondere Verdichter für Kraftfahrzeug-Klimaanlagen, gemäß dem Oberbegriff des Anspruches 1.The present invention relates to an axial piston compressor, in particular compressor for motor vehicle air conditioning systems, according to the preamble of
Im Bereich von Verdichtertriebwerken zeichnet sich eine Tendenz dahingehend ab, daß bei Verdichtern mit variablem Kolbenhub zunehmend Schwenkscheiben in Form eines Schwenkringes, d.h. also ringförmige Schwenkscheiben, Verwendung finden. Ein für das Schwenken der Scheibe notwendiges Kippgelenk wird dabei im wesentlichen in die ringförmige Schwenkscheibe integriert. So ist beispielsweise aus der
Die Antriebsübertragung von der Antriebswelle zum Schwenkring erfolgt durch einen in der Antriebswelle befestigten Mitnehmerbolzen, dessen kugelförmiger Kopf in eine radiale Bohrung des Schwenkringes eingreift. Dabei ist die Position des Mitnehmerkopfes so gewählt, daß sein Mittelpunkt mit demjenigen der Kugelsegmente übereinstimmt. Außerdem liegt dieser Mittelpunkt auf einer Kreislinie, die die geometrischen Achsen der sieben Kolben miteinander verbindet, und weiterhin auf einer Kreislinie, die die Mittelpunkte der kugelförmigen Gelenkkörper der Kolben verbindet. Auf diese Weise ist die obere Totpunktposition der Kolben bestimmt und ein minimaler Schadraum gewährleistet. Die Kopfform des freien Mitnehmerendes ermöglicht die Veränderung der Neigung der Schwenkscheibe, in dem der Mitnehmerkopf einen Lagerkörper für eine die Hubweite der Kolben verändernde Schwenkbewegung der Schwenkscheibe bildet.The drive transmission from the drive shaft to the pivot ring is effected by a driving pin fixed in the drive pin, the spherical head engages in a radial bore of the pivot ring. The position of the driver head is chosen so that its center coincides with that of the spherical segments. In addition, this center point is on a circular line connecting the geometric axes of the seven pistons, and continues on a circular line, the centers the spherical joint body connects the pistons. In this way, the top dead center position of the piston is determined and ensures a minimum dead space. The head shape of the free Mitnehmerendes allows the change in the inclination of the swash plate, in which the driver head forms a bearing body for a stroke of the piston changing pivotal movement of the swash plate.
Eine weitere Voraussetzung für ein Verschwenken der Schwenkscheibe ist die Verschiebbarkeit ihrer Lagerachse in Richtung der Antriebswelle. Hierzu ist die Lagerachse durch zwei gleichachsig beidseitig einer Schiebehülse gelagerte Lagerbolzen gebildet, die außerdem in radialen Bohrungen der Schwenkscheibe gelagert sind. Die Schiebehülse hat hierzu vorzugsweise beidseitig Lagerhülsen, die den Ringraum zwischen der Schiebehülse und der Schwenkscheibe speichenartig überbrücken.Another requirement for pivoting the swash plate is the displaceability of its bearing axis in the direction of the drive shaft. For this purpose, the bearing axis is formed by two coaxially mounted on both sides of a sliding sleeve bearing pin, which are also mounted in radial bores of the swash plate. For this purpose, the sliding sleeve preferably has bearing sleeves on both sides which bridge the annular space between the sliding sleeve and the swashplate in the manner of a spoke.
Die Begrenzung der Verschiebbarkeit der Lagerachse und damit die maximale Schrägstellung der Schwenkscheibe ergibt sich durch den Mitnehmerbolzen, indem dieser ein in der Schiebehülse vorgesehenes Langloch durchdringt, so daß die Schiebehülse an den Enden des Langloches Anschläge findet. Die Kraft für die Winkelverstellung der Schwenkscheibe und damit für eine Regelung des Verdichters ergibt sich aus der Summe der jeweils beidseitig der Kolben gegeneinander wirkenden Drücke, so daß diese Kraft vom Druck im Triebwerksraum abhängig ist. Der Druck im Triebwerksxaum ist entsprechend dem Stand der Technik zwischen einem hohen und einem niedrigen Druck regelbar und greift dementsprechend in das Kräftegleichgewicht an der Schwenkscheibe ein. Dadurch wird die Neigung derselben beeinflußt. Weiterhin kann die Position der Schiebehülse durch Federn beeinflußt werden, welche ebenfalls in verschiedenen Varianten zum Stand der Technik gehören.The limitation of the displaceability of the bearing axis and thus the maximum inclination of the swash plate results from the driving pin by this penetrates a slot provided in the sliding sleeve, so that the sliding sleeve finds at the ends of the slot stops. The force for the angular adjustment of the swash plate and thus for a control of the compressor results from the sum of each of the two sides of the piston against each other acting pressures, so that this force is dependent on the pressure in the engine room. The pressure in the engine cavity can be regulated according to the state of the art between a high and a low pressure and accordingly engages in the equilibrium of forces at the swashplate. This affects the inclination of the same. Furthermore, the position of the sliding sleeve can be influenced by springs, which also belong to the prior art in various variants.
Ferner wird die für die Förderleistung maßgebliche Position der Schiebehülse durch auf die Schwenkscheibe einwirkende Trägheitskräfte mitbestimmt, wobei sich die Schwenkscheibe bei steigender Drehgeschwindigkeit verstellt, d.h. ihren Schwenkwinkel bzw. ihren Kippwinkel ändert. Bei modernen Verdichtern geht der Trend dazu, Schwenkscheiben mit derartigen Trägheitsmomenten zum Einsatz zu bringen, die eine Verringerung der Hubweite der Kolben und damit eine Verringerung der Förderleistung bei ansteigender Drehgeschwindigkeit bewirken.Furthermore, the decisive for the delivery position of the sliding sleeve is co-determined by acting on the swash plate inertial forces, wherein the swash plate adjusted with increasing rotational speed, ie changes its tilt angle or tilt angle. In modern compressors, the trend is to use swash plates with such inertia, which cause a reduction in the stroke of the piston and thus a reduction in the capacity at increasing rotational speed.
Problematisch an der vorstehend erläuterten Konstruktion ist jedoch die hohe Hertzsche Pressung im Bereich des Mitnehmerkopfes und der Schwenkscheibe (System: Kugel/ Zylinder) und die Aufnahme der (axialen) Reaktionskräfte infolge der Gaskraft an den Kolben und der Kräfte infolge des an die Schwenkscheibe zu übertragenden Drehmomentes.The problem with the construction described above, however, is the high Hertzian pressure in the region of the driver head and the swash plate (system: ball / cylinder) and the absorption of (axial) reaction forces due to the gas force on the piston and the forces due to be transferred to the swash plate torque.
Ein dem aus der
Bedeutsam für die Kinematik gemäß den beiden erwähnten Druckschriften, d.h. also bedeutsam für die Kinematik bei den Gegenständen der
Zu den vorstehend erwähnten ungünstigen Eigenschaften tritt hinzu, daß die Gegenstände der
Ein weiterer Verdichter ist aus der
Ein weiterer Verdichter ist aus der
In der unveröffentlichten und auf die Anmelderin zurückgehenden Patentanmeldung
Aus der
Aus der ebenfalls unveröffentlichten und auf die Anmelderin zurückgehenden
Ausgehend vom vorstehend erläuterten Stand der Technik ist es Aufgabe der vorliegenden Erfindung, einen Verdichter anzugeben, dessen Stützelement möglichst großflächig Kräfte aufnehmen kann (was einer geringen Hertzschen Pressung entspricht), wobei eine Unwucht der Schwenkscheibe infolge der Lagerung und des Verkippens derselben und weiterer Teile, die den Masseneigenschaften der Schwenkscheibe zuzuordnen sind, über den gesamten Schwenkwinkelbereich und den gesamten Drehzahlbereich gering ist. Diese Aufgabe wird durch einen Verdichter mit den Merkmalen gemäß dem Patentanspruch 1 gelöst.Based on the above-described prior art, it is an object of the present invention to provide a compressor whose support element can absorb forces over a large area (which corresponds to a low Hertzian pressure), with an imbalance of the swash plate due to the storage and tilting of the same and other parts, which are assigned to the mass properties of the swash plate, over the entire swing angle range and the entire speed range is low. This object is achieved by a compressor having the features according to the
Ein wesentlicher Punkt der Erfindung ist es demnach, daß ein Kraftübertragungselement drehbar und/oder radial verschieblich am Stützelement angelenkt ist. Durch die Anlenkung des Stützelements an das Kraftübertragungselement ist gewährleistet, daß das Stützelement großflächig Kräfte aufnehmen kann, wobei die Masseeigenschaften der Schwenkscheibe optimiert werden, da sich eine derartige konstruktive Maßnahme positiv auf die Masseeigenschaften auswirkt (die Masse des Stützelements kann modellhaft der Schwenkscheibe zugerechnet werden).An essential point of the invention is therefore that a power transmission element is rotatably and / or radially displaceable articulated on the support element. By the articulation of the support member to the power transmission element is ensured that the support element can absorb forces over a large area, the mass properties of the swash plate are optimized because such a constructive action has a positive effect on the mass properties (the mass of the support element can be attributed to the model of the swash plate).
Das Kraftübertragungselement kann drehfest und/oder radial unverschieblich mit der Antriebswelle verbunden sein, was einen einfachen Aufbau eines erfindungsgemäßen Verdichters sicherstellt. Je nach der konstruktiven Realisierung der benötigten Freiheitsgrade kann das Kraftübertragungselement selbstverständlich auch drehbar in der Antriebswelle gelagert sein.The power transmission element may be non-rotatably and / or radially immovably connected to the drive shaft, which ensures a simple construction of a compressor according to the invention. Of course, depending on the structural realization of the required degrees of freedom, the force transmission element can also be rotatably mounted in the drive shaft.
Erfindungsgemäß sind sowohl das Kraftübertragungselement als auch das Stützelement zylinderbolzenförmig ausgebildet. Ein derartiger Aufbau ist einerseits konstruktiv bzw. fertigungstechnisch einfach realisierbar und stellt insbesondere durch die zylinderbolzenförmige Ausbildung des Stützelements eine geringe Hertzsche Pressung zwischen Stützelement und Schwenkscheibe sicher.According to the invention, both the power transmission element and the support element are formed in the shape of a cylinder bolt. On the one hand, such a structure is structurally or production-technically easy to implement and, in particular, ensures a low Hertzian pressure between the supporting element and the swashplate due to the cylinder-bolt-shaped design of the support element.
In einer konstruktiv einfachen Ausführungsform bilden das Stützelement und das Kraftübertragungselement eine in etwa T-förmige Gaskraftstütze.In a structurally simple embodiment, the support element and the force transmission element form an approximately T-shaped gas force support.
Das Stützelement umfaßt optional eine Aussparung, in welche das Kraftübertragungselement eingreift. Bei dieser Aussparung handelt es sich insbesondere um eine Bohrung, wodurch ein einfacher und kostengünstiger Aufbau eines erfindungsgemäßen Verdichters sichergestellt wird.The support member optionally includes a recess into which engages the force transmission element. This recess is in particular a bore, whereby a simple and cost-effective design of a compressor according to the invention is ensured.
Das Stützelement kann ferner in einer zylinderförmigen Aussparung, insbesondere in einer Bohrung in der Schwenkscheibe gelagert sein. Die Bohrung erstreckt sich dabei senkrecht zur Antriebswellenachse. Auch hierbei handelt es sich um eine konstruktiv einfache und damit zu bevorzugende Ausführungsform eines erfindungsgemäßen Verdichters.The support element may also be mounted in a cylindrical recess, in particular in a bore in the swash plate. The bore extends perpendicular to the drive shaft axis. Again, this is a structurally simple and thus preferred embodiment of a compressor according to the invention.
Vorzugsweise dienen das Stützelement und das Kraftübertragungselement im wesentlichen nur zur axialen Abstützung der Kolben bzw. 2u einer Gaskraftabstützung, während eine davon unabhängige Vorrichtung, insbesondere eine Gelenkverbindung zwischen Antriebswelle und Schwenkscheibe im wesentlichen nur der Drehmomentübertragung dient. Dadurch ist die Entkopplung von Antriebsdrehmoment und der Gaskraftabstützung sichergestellt.Preferably, the support element and the force transmission element essentially serve only for the axial support of the pistons and / or a gas force support, while a device independent thereof, in particular a joint connection between Drive shaft and swivel disk essentially only the torque transmission is used. As a result, the decoupling of drive torque and the gas power support is ensured.
In einer weiteren bevorzugten Ausführungsform ist das Kraftübertragungselement drehbar in der Antriebswelle gelagert, während das Stützelement drehfest mit dem Kraftübertragungselement in Eingriff steht. Das Kraftübertragungselement ist optional ein Bolzen mit einem wenigstens teilweise etwa kreisförmigen oder halb elliptischen Querschnitt.In a further preferred embodiment, the power transmission element is rotatably mounted in the drive shaft, while the support element is non-rotatably engaged with the force transmission element. The power transmission element is optionally a bolt having an at least partially approximately circular or semi-elliptical cross-section.
Bei einem erfindungsgemäßen Verdichter ist die Schwenkscheibe bevorzugt an einer längs der Antriebswelle axial verschieblich gelagerten Schiebehülse schwenkbar gelagert, wobei die Schwenkscheibe über Antriebsbolzen mit der Schiebehülse und/oder der Antriebswelle verbunden ist. Dies stellt eine einfache Realisierung der Entkopplung zwischen Antriebsdrehmoment und Gaskraftabstützung sicher. Die Antriebsbolzen können in die Schiebehülse oder die Schwenkscheibe eingepreßt sein oder durch axiale Sicherungselemente in derselben gesichert sein. Vorzugsweise ragen die Antriebsbolzen in eine Aussparung, die insbesondere in Form einer Nut in der Antriebswelle vorliegen kann, hinein. Optional ist ein Verbindungselement, insbesondere in Form einer Paßfeder, zwischen Antriebswelle und Schiebehülse angeordnet, welches eine Übertragung von Kräften bzw. Momenten in radialer Richtung erlaubt und axial verschieblich auf der Antriebswelle gelagert ist. Das dem Stützelement abgewandte Ende des Kraftübertragungselementes kann durch die Antriebswelle hindurch und in einen Längsschlitz an der Schiebehülse hineinragen derart, daß durch das dem Stützelement abgewandte Ende des Kraftübertragungselementes ein Antriebsdrehmoment von der Antriebswelle auf die Schiebehülse übertragen wird. Die vorstehend genannten konstruktiven Merkmale sorgen für eine sichere Entkopplung zwischen Antriebsdrehmoment und Gaskraftabstützung.In a compressor according to the invention, the swash plate is preferably pivotally mounted on a longitudinally displaceably mounted along the drive shaft sliding sleeve, wherein the swash plate is connected via drive bolts with the sliding sleeve and / or the drive shaft. This ensures a simple realization of the decoupling between drive torque and gas force support. The drive bolts may be pressed into the sliding sleeve or the swash plate or be secured by axial securing elements in the same. The drive bolts preferably protrude into a recess, which may be present in particular in the form of a groove in the drive shaft. Optionally, a connecting element, in particular in the form of a feather key, is arranged between the drive shaft and the sliding sleeve, which permits a transmission of forces or moments in the radial direction and is mounted axially displaceably on the drive shaft. The support element facing away from the end of the power transmission element can project through the drive shaft and into a longitudinal slot on the sliding sleeve such that a drive torque is transmitted from the drive shaft to the sliding sleeve by the support member remote from the end of the power transmission element. The above constructive features ensure a safe decoupling between drive torque and gas force support.
Bereiche der Aussparung in der Schwenkscheibe, welche insbesondere in Form einer Bohrung vorliegen kann, die nicht durch das Stützelement ausgefüllt sind, sind bevorzugt mit einem Ausgleichsgewicht, insbesondere in Form eines Verschlußelementes bzw, mit Ausgleichsgewichten in Form von Verschlußelementen ausgefüllt. Dadurch lassen sich die kinematischen Eigenschaften der Schwenkscheibe optimieren, so daß auf eine mit zunehmender Drehzahl zunehmend abregelnde Tendenz des Verdichters hingewirkt werden kann.Areas of the recess in the swash plate, which may be present in particular in the form of a bore, which are not filled by the support element, are preferably filled with a balance weight, in particular in the form of a closure element or with balancing weights in the form of closure elements. As a result, the kinematic properties of the swash plate can be optimized so that one with increasing Speed increasingly abregierende tendency of the compressor can be worked.
Für einen sicheren Übertrag des Verdrehdrehmomentes kann zwischen der Schiebehülse und der Schwenkscheibe eine Vorrichtung, insbesondere wenigstens ein zylinderstiftartiges Element oder Stütz- bzw. Kontaktflächen vorgesehen sein, um ein im Bereich der Antriebswelle angreifendes Verdrehmoment abzustützen.For a reliable transfer of the torsional torque can be provided between the sliding sleeve and the swash plate, a device, in particular at least one cylindrical pin-like element or support or contact surfaces to support an attacking in the drive shaft twisting moment.
Das Kraftübertragungselement, insbesondere die Längsachse desselben, ist optional gegenüber der Drehmomentachse, insbesondere der Antriebswellenachse, versetzt angeordnet. Dabei können das Stützelement und/oder das Kraftübertragungselement mehrteilig ausgebildet sein. Das Kraftübertragungselement kann ferner abgewinkelt ausgebildet sein, insbesondere kann es einen sich senkrecht zu der Kippmomentachse und einen sich durch diese hindurch erstreckenden Abschnitt umfassen. Alternativ oder aber auch zusätzlich kann das Kraftübertragungselement exzentrisch in der Antriebswelle angeordnet sein. Durch die vorstehend beschriebenen konstruktiven Maßnahmen wird die Übertragung des Verdrehmomentes reduziert und Nachteile wie zusätzliche Reibung, Klemmen oder eine Hysterese werden vermieden.The force transmission element, in particular the longitudinal axis of the same, is optionally arranged offset relative to the torque axis, in particular the drive shaft axis. In this case, the support element and / or the power transmission element can be designed in several parts. The force transmission element may further be formed angled, in particular it may comprise a perpendicular to the tilting moment axis and extending therethrough section. Alternatively or in addition, the power transmission element may be arranged eccentrically in the drive shaft. By the constructive measures described above, the transmission of the twisting torque is reduced and disadvantages such as additional friction, terminals or hysteresis are avoided.
Die Schwenkscheibe kann aus Stahl, Messing oder Bronze gefertigt sein. Denkbar ist des weiteren auch eine mehrkomponentige bzw. mehrstoffige Schwenkscheibe, die Kombinationen der vorstehend genannten Werkstoffe umfaßt. All die vorstehend genannten Werkstoffe bieten für die konstruktive Ausgestaltung der Schwenkscheibe eine gute Festigkeit und Steifigkeit. Aufgrund der relativ hohen Dichte der Werkstoffe, insbesondere von Bronze oder Messing, ergibt sich eine vorteilhafte Masseverteilung, so daß die translatorischen Momente der Kolbenmassen optimal durch die rotatorischen Momente der Schwenkscheibe kompensiert werden können. Insbesondere, jedoch nicht ausschließlich, in dem Fall, in dem die Schwenkscheibe aus Stahl gefertigt ist, kann dieselbe eine verschleißarme Beschichtung aufweisen, was zu einer hohen Lebensdauer eines erfindungsgemäßen Verdichters führt.The swivel plate can be made of steel, brass or bronze. Also conceivable is a multicomponent or multi-material swash plate, which comprises combinations of the abovementioned materials. All the materials mentioned above provide good strength and rigidity for the structural design of the swivel disk. Due to the relatively high density of the materials, in particular of bronze or brass, results in an advantageous mass distribution, so that the translational moments of the piston masses can be optimally compensated by the rotational moments of the swash plate. In particular, but not exclusively, in the case where the swash plate is made of steel, it may have a low-wear coating, resulting in a long life of a compressor according to the invention.
Die Kolben sind in einer bevorzugten Ausführungsform aus Aluminium bzw. einer Aluminiumlegierung gefertigt, wodurch das Gewicht eines entsprechenden Verdichters gering gehalten werden kann. Alternativ können die Kolben auch aus Stahl oder einer Stahllegierung gefertigt sein, was zu einer hohen Festigkeit derselben führt, wobei eine auf das Material der Schwenkscheibe abgestimmte Materialwahl (ähnliche thermische Ausdehnungskoeffizienten) vorteilhaft ist.The pistons are made in a preferred embodiment of aluminum or an aluminum alloy, whereby the weight of a corresponding compressor can be kept low. Alternatively, the pistons may also be made of steel or a steel alloy, which leads to a high strength of the same, with a matched to the material of the swash plate choice of material (similar coefficients of thermal expansion) is advantageous.
In einer weiteren günstigen Ausführungsform ist das Stützelement tonnenförmig bzw. zigarrenförmig bzw. zylinderförmig ausgebildet, wobei der Zylinder von der Zylindermitte zu den Zylinderenden hin (axiale Richtung) einen verjüngenden Durchmesser aufweist. Analoges gilt für die Tonnen- oder Zigarrenform. Dadurch kann sichergestellt werden, daß zwischen dem Stützelement und der Schwenkscheibe nur ein Linienkontakt besteht und somit Verklemmungen zwischen den beiden Bauteilen auszuschließen sind. Der Linienkontakt ist insbesondere im Fall einer Schrägscheibe aus Stahl auch zur Kraftübertragung geeignet, so daß die vorstehend beschriebene Ausführungsform sowohl in Kombination mit Antriebsbolzen zum Drehmomentübertrag als auch ohne dieselben, d.h. also in einem Fall, in dem der Kraftübertrag über das Kraftübertragungselement und das Stützelement erfolgt, denkbar und vorteilhaft ist.In a further advantageous embodiment, the support element is barrel-shaped or cigar-shaped or cylindrical, the cylinder having a tapering diameter from the cylinder center to the cylinder ends (axial direction). The same applies to the barrel or cigar form. This can ensure that there is only a line contact between the support member and the swash plate and thus jamming between the two components are excluded. The line contact is particularly suitable in the case of a swashplate made of steel also for power transmission, so that the embodiment described above, both in combination with drive pin for transmitting torque as well as without the same, i. So in a case in which the force is transmitted via the force transmission element and the support element, is conceivable and advantageous.
Die Erfindung wird nachfolgend in Hinsicht auf weitere Vorteile und Merkmale beispielhaft und unter Bezugnahme auf die beiliegenden Zeichnungen beschrieben. Die Zeichnungen zeigen in:
- Fig. 1
- einen Schwenkscheibenmechanismus einer ersten bevorzugten Ausfüh rungsform eines erfindungsgemäßen Verdichters in Explosionsdarstellung;
- Fig. 2
- den Schwenkscheibenmechanismus gemäß
Fig. 1 in zusammengebautem Zustand in einer perspektivischen Ansicht; - Fig. 3
- den Schwenkscheibenmechanismus gemäß
Fig. 1 bei einem maximalen Kippwinkel der Schwenkscheibe im Längsschnitt; - Fig. 4
- den Schwenkscheibenmechanismus gemäß
Fig. 1 bei einem minimalen Kippwinkel der Schwenkscheibe wiederum im Längsschnitt; - Fig. 5
- den Schwenkscheibenmechanismus gemäß
Fig. 4 in einer Schnittansicht entlang der Ebene A-A; - Fig. 6a
- den Schwenkscheibenmechanismus gemäß
Fig. 3 in einer Schnittansicht entlang der Schnittebene E-E; - Fig. 6b
- eine alternative Ausgestaltung eines Schwenkscheibenmechanismus in einer zu
Fig. 6a korrespondierenden Darstellung; - Fig. 7
- eine Draufsicht auf die erste bevorzugte Ausführungsform, teilweise in Schnittdarstellung;
- Fig. 8a+8b
- eine Teilansicht einer zweiten bevorzugten Ausführungsform eines erfindungsgemäßen Verdichters im Längsschnitt (a) und eine Detailansicht einer Verbindung zwischen einem Kraftübertragungselement und einem Stützelement gemäß der zweiten bevorzugten Ausführungsform in Schnittansicht;
- Fig. 9
- eine dritte bevorzugte Ausführungsform eines Schwenkscheibenmechanismus eines erfindungsgemäßen Verdichters in einer Schnittansicht korrespondierend zu
Fig. 6 ; und - Fig. 10
- eine vierte bevorzugte Ausführungsform eines Schwenkscheibenmechanismus in einer Schnittansicht korrespondierend zu
den Figuren 6 und 9 .
- Fig. 1
- a swashplate mechanism of a first preferred embodiment of a compressor according to the invention in exploded view;
- Fig. 2
- the swashplate mechanism according to
Fig. 1 in assembled condition in a perspective view; - Fig. 3
- the swashplate mechanism according to
Fig. 1 at a maximum tilt angle of the swash plate in longitudinal section; - Fig. 4
- the swashplate mechanism according to
Fig. 1 at a minimum tilt angle of the swash plate again in longitudinal section; - Fig. 5
- the swashplate mechanism according to
Fig. 4 in a sectional view along the plane AA; - Fig. 6a
- the swashplate mechanism according to
Fig. 3 in a sectional view along the cutting plane EE; - Fig. 6b
- an alternative embodiment of a swivel mechanism in a too
Fig. 6a corresponding representation; - Fig. 7
- a plan view of the first preferred embodiment, partially in section;
- Fig. 8a + 8b
- a partial view of a second preferred embodiment of a compressor according to the invention in longitudinal section (a) and a detailed view of a connection between a power transmission element and a support member according to the second preferred embodiment in sectional view;
- Fig. 9
- a third preferred embodiment of a swashplate mechanism of a compressor according to the invention in a sectional view corresponding to
Fig. 6 ; and - Fig. 10
- a fourth preferred embodiment of a swashplate mechanism in a sectional view corresponding to the
FIGS. 6 and9 ,
Sämtliche bevorzugte Ausführungsformen eines erfindungsgemäßen Verdichters umfassen (nicht in den Zeichnungen dargestellt) ein Gehäuse, einen Zylinderblock und einen Zylinderkopf. Im Zylinderblock sind Kolben axial hin- und herbewegbar gelagert. Der Antrieb der Verdichter erfolgt über eine Riemenscheibe mittels einer Antriebswelle 1. Bei den vorliegenden Verdichtern handelt es sich um Verdichter mit variablem Kolbenhub, wobei der Kolbenhub durch eine Druckdifferenz, die durch die Drücke auf einer Sauggasseite und in einer Triebwerkskammer definiert ist, geregelt wird. Je nach der Größe der Druckdifferenz wird eine Schwenkscheibe in Form eines Schwenkrings 2 mehr oder weniger aus ihrer vertikalen Lage ausgelenkt bzw. verschwenkt. Je größer der daraus resultierende Schwenkwinkel ist, desto größer ist der Kolbenhub, und dementsprechend wird ein umso höherer Druck an einer Auslaßseite des Verdichters zur Verfügung gestellt.All preferred embodiments of a compressor according to the invention include (not shown in the drawings) a housing, a cylinder block and a cylinder head. In the cylinder block pistons are mounted axially movable back and forth. The compressors are driven by means of a belt pulley by means of a
Aus
Das Stützelement 5 ist drehbar und radial verschieblich am Kraftübertragungselement 6 angelenkt, während das Kraftübertragungselement 6 drehfest und radial unverschieblich mit der Antriebswelle 1 verbunden ist. Sowohl das Stützelement 5 als auch das Kraftübertragungselement 6 ist zylinderbolzenförmig ausgebildet. Wie bereits erwähnt, ist das Stützelement 5 drehbar und radial verschieblich am Kraftübertragungselement 6 angelenkt, was über eine Aussparung 8 im Stützelement 5 erfolgt, in welche das Kraftübertragungselement 6 eingreift. Diese Aussparung 8 liegt in Form einer Bohrung im Stützelement 5 vor. Das Stützelement 5 und das Kraftübertragungselement 6 bilden in zusammengesetztem Zustand eine in etwa T-förmige Gaskraftstütze 9 (vgl. beispielsweise
Die Schiebehülse 3 weist zwei abgeflachte Seiten 13 auf (aus
Die Feder 4 dient als Verbindungselement, welches zwischen Antriebswelle 1 und Schiebehülse 3 angeordnet ist, und einen Übertrag von Kräften in axialer Richtung erlaubt. Sie ist axial verschieblich auf der Antriebswelle 1 gelagert. Das dem Stützelement 5 abgewandte Ende des Kraftübertragungselements 6 ragt durch einen Längsschlitz 18, welcher an der Schiebehülse 3 ausgebildet ist, in die Antriebswelle 1 hinein. An dieser Stelle sei angemerkt, daß alternativ oder auch zusätzlich zum Kraft- bzw. Drehmomentübertrag über die Antriebsbolzen 7 die Schiebehülse derart ausgebildet sein kann, daß ein dem Längsschlitz 18 gegenüberliegend angeordneter Längsschlitz an der Schiebehülse vorgesehen ist, in welchen das dem Stützelement 5 abgewandte Ende des Kraftübertragungselements 6 hineinragt und damit ein Antriebsdrehmoment von der Antriebswelle 1 auf die Schiebehülse 3 überträgt. Es sei an dieser Stelle nochmals kurz erwähnt, daß die Antriebswelle 1 und die Schiebehülse 3 zusätzlich oder alternativ zu der Verbindung bzw. zum Drehmomentübertrag über die Antriebsbolzen 7 zueinander korrespondierende Abflachungen aufweisen können, so daß die Schiebehülse drehfest auf der Antriebswelle gelagert ist (aus
Die in
In den
In
Eine alternative Ausführungsform ist in
Da vorstehend das Material, aus welchem der Schwenkring 2 gefertigt ist, zur Erörterung gelangte, sei an dieser Stelle angemerkt, daß der Schwenkring 2, der in der vorstehend beschriebenen Ausführungsform aus Stahl gefertigt und mit einer Beschichtung versehen ist, welche den Verschleiß und die Reibung zwischen den Gleitsteinen der Kolben und dem Schwenkring 2 minimiert, alternativ auch aus Messing oder Bronze gefertigt sein kann. Die erwähnten Materialien stellen sicher, daß die bauartbedingten Anforderungen erfüllt werden. Bei den verwendeten Schwenkringen 2 handelt es sich nämlich um Ringe, die gegenüber dem Stand der Technik sehr hoch bauen. Die Höhe ist einerseits erwünscht, um die Gaskraftstütze, welche sich aus Stützelement 5 und Kraftübertragungselement 6 zusammensetzt, darin lagern zu können, andererseits ist die Höhe von Vorteil, um dem Bauteil eine ausreichende Massenträgheit zuordnen zu können. Diese ist notwendig, um ein Kippmoment aufgrund des Kreiseleffekts bei der Rotation des Schwenkrings 2 erzeugen zu können, welches groß genug ist, um in gewünschtem Maße die gegenläufig wirksamen Kippmomente infolge der Massenkräfte der Kolben kompensieren bzw. überkompensieren zu können.Since the material from which the
Für derartige Schwenkringe 2 bieten sich die erwähnten Materialien wie Stahl, Messing oder Bronze besonders an, da aufgrund der Höhe des Schwenkrings 2 diese Werkstoffe ausreichende Festigkeit und Steifigkeit gewährleisten, um Deformationen vorbeugen zu können. Bei Schwenkringen entsprechend dem Stand der Technik ist das häufig nicht gesichert. Weiterhin ist die Dichte von Bronze oder Messing je nach Legierung gegebenenfalls etwas größer als die Dichte von Stahl oder von Grauguß (ein erfindungsgemäßer Schwenkring 2 kann selbstverständlich auch aus Grauguß gefertigt sein). Der Dichtezuwachs bzw. die höhere Dichte von Bronze oder Messing kann genutzt werden, um die Kolbenmassen noch besser kompensieren oder überkompensieren zu können. Die Höhe des Schwenkrings 2 führt dazu, daß die Kolben, die in der hier diskutierten Applikation den Schwenkring 2 umfassen und mittels zweier Gleitsteine an diesem gelagert werden, eine große Öffnung für das Umfassen des Schwenkrings 2 aufweisen müssen.For such swivel rings 2, the mentioned materials such as steel, brass or bronze offer particular, since due to the height of the
In der bevorzugten Ausführungsform, in der der Schwenkring 2 aus Messing gefertigt ist, sind die Kolben aus einer Aluminiumlegierung gefertigt. Da Messing eine zum Aluminium ähnliche Wärmeausdehnung hat, sorgt eine derartige Materialkombination für einen verminderten Verschleiß und eine erhöhte Lebensdauer eines erfindungsgemäßen Verdichters, da sich das Spiel der Gleitsteine in den Kolben gegenüber dem Zustand bei der Montage nur unwesentlich oder gar nicht vergrößert. Dies führt zu einer geringen Geräuschbildung und verhindert, daß Gleitsteine infolge eines zu großen Spiels herausfallen können. Ist der Schwenkring 2 aus Stahl gefertigt, so bieten Kolben, die ebenfalls aus Stahl gefertigt sind, dieselben Vorteile. Alternativ sind aber auch andere Werkstoffkombinationen (insbesondere unter dem Gesichtspunkt einer Gewichtsreduzierung eines erfindungsgemäßen Verdichters) denkbar.In the preferred embodiment, in which the
Zur Illustration der Unterschiede, die je nach Material des Schwenkrings 2 auftreten (also je nachdem, ob der Schwenkring 2 aus Stahl oder aus Messing gefertigt ist), sei auf
Es sei an dieser Stelle nochmals kurz auf die Vorteile der Erfindung eingegangen, welche sich wie folgt darstellen: Die Gaskraftstütze 9 nimmt weitgehend und vorzugsweise drehmomentfrei (insofern eine Konstruktion gewählt ist, in welcher das Kraftübertragungselement 6 an seiner dem Stützelement 5 abgewandten Seite nicht in drehmomentübertragendem Eingriff mit der Schiebehülse 3 steht) die Stützfunktion des Schwenkringes 2 im Hinblick auf die axial einwirkenden Kolbenkräfte wahr; das Stützelement 5 ist großflächig, d.h. also zylinderbolzen- oder tonnenförmig ausgebildet, wobei Verdrehmomente nicht eingeleitet werden können, da sich die Gaskraftstütze 9 entweder am Übergang zwischen Kraftübertragungselement 6 und Stützelement 5 oder (wie in der Folge noch beschrieben wird) durch eine verdrehbare Lagerung des Kraftübertragungselements 6 in der Antriebswelle 1 um ihre Mittelachse ausrichten kann; die Antriebsmomente werden definiert in der Ebene senkrecht zur Kippebene des Schwenkrings übertragen, wobei hier angemerkt sei, daß es verschiedene Möglichkeiten der Kraftübertragung bzw. der Drehmomentübertragung gibt. Dadurch, daß das Stützelement 5 sowohl drehbar als auch radial verschieblich an das Kraftübertragungselement 6 angelenkt ist, kann im wesentlichen kein Verdrehmoment (Torsion) übertragen werden. Dies ermöglicht eine definierte Übertragung des Verdrehmomentes an anderer Stelle, wie dies bereits vorstehend erwähnt ist, und verhindert ein Klemmen des Mechanismus. Ebenso ist dadurch eine leichte und schnelle Montage gewährleistet. Eine Überbestimmung in Bezug auf das Verdrehmoment, die sich bei einer zylinderförmigen Gestaltung des Stützelementes 5 ergeben könnte, wird durch die drehbare Lagerung desselben beispielsweise am Kraftübertragungselement 6 vermieden.It should be at this point again briefly on the advantages of the invention addressed, which are as follows: The
In der Folge sei auf die Übertragung des Antriebsdrehmomentes näher eingegangen: Wie bereits in der Beschreibung der
Alternativ ist eine indirekte Übertragung des Antriebsdrehmoments mit einem Kraftfluß über die Schiebehülse 3 denkbar. Dies könnte konstruktiv wie folgt bewerkstelligt werden: ein Verbindungselement zwischen Antriebswelle 1 und Schiebehülse 3, welches die Übertragung von Kräften bzw. Momenten in Radialrichtung zuläßt, jedoch beispielsweise durch Gleiten in einer Nut der Schiebehülse 3 die axiale Verschiebbarkeit der Buchse zuläßt. Ein solches Verbindungselement könnte z.B. eine Paßfeder sein. Das dem Stützelement 5 entgegengesetzte Ende des Kraftübertragungselements 6 wird durch die Welle hindurchgeführt und ragt in einen Schlitz der Schiebehülse 3, in welchem das Kraftübertragungselement 6 eng geführt wird und dadurch das Antriebsdrehmoment übertragen kann. Abflachungen an der Schiebehülse 3 und dem Schwenkring 2 übertragen dann das Moment auf den Schwenkring 2.Alternatively, an indirect transmission of the drive torque with a power flow through the sliding
Ein zentraler Punkt der vorliegenden Erfindung ist die Gestaltung der Gaskraftstütze 9. Im Rahmen der vorliegenden Erfindung wird eine Gaskraftstütze 9 bereitgestellt, welche einerseits dadurch entlastet ist, daß sie kein Antriebsdrehmoment überträgt, andererseits jedoch hinsichtlich der Flächenpressung, die sich aufgrund der Übertragung der Gaskräfte ergibt, optimiert ist.A central point of the present invention is the design of the
Ferner sei an dieser Stelle nochmals auf die korrespondierenden Abflachungen 13, 14 an der Antriebswelle 1 und der Schiebehülse 3 hingewiesen, welche aus
In einer alternativen zweiten bevorzugten Ausführungsform, welche in den
Zwei weitere bevorzugte Ausführungsformen eines erfindungsgemäßen Verdichters finden sich in den
An dieser Stelle sei nochmals zusammenfassend auf die Vorteile der vorliegenden Erfindung eingegangen. Die Unwucht infolge der Lagerung und des Verkippens der Schrägscheibe und weiterer Teile, die den Masseneigenschaften der Schrägscheibe zugeordnet sind, sind sehr gering. Das Massenträgheitsmoment der Schrägscheibe und weiterer Teile, die den Masseneigenschaften der Schrägscheibe bezüglich der Kippachse (Deviationsmoment) zuzuordnen sind, sind hinsichtlich des Bauraums optimiert, d.h. der Verdichter weist für hohe Drehzahlen und über dem gesamten Auslenkwinkelbereich des Schwenkrings 2, d.h. also insbesondere auch für kleine Auslenkwinkel ein abregelndes Verhalten auf. Das Stützelement 5 ist durch die entsprechende Gestaltung in der Lage, großflächig Kräfte aufnehmen zu können, was zu einer geringen Hertzschen Pressung führt. Die Gaskraftstütze 9 ist frei von Drehmoment, das zwischen Welle und Schrägscheibe übertragen wird, so daß eine Überbestimmung der Kraftübertragungsfunktion (was in einem Klemmen resultiert) vermieden wird. Ferner ist die Steifigkeit des Schwenkringes 2. optimiert und eine Anlenkung des Schwenkrings 2 an das Stützelement 5 ist mit einer geringen Flächenpressung, d.h. einer geringen Hertzschen Pressung gewährleistet.At this point, once again summarized on the advantages of the present invention. The imbalance due to the storage and tilting of the swash plate and other parts associated with the mass characteristics of the swash plate are very low. The moment of inertia of the swashplate and other parts attributable to the mass characteristics of the swashplate with respect to the tilting axis (deviation moment) are optimized in terms of installation space, i. the compressor has for high speeds and over the entire deflection angle range of the
Wie beispielsweise
Ein weiterer wesentlicher Vorteil ergibt sich hinsichtlich der Massenträgheitseigenschaften des Schwenkrings 2 in Kombination mit dem Stützelement 5. Das Stützelement 5 ist derart mit der Schwenkscheibe verbunden, daß die Massenkräfte infolge der Masse des Stützelementes 5 bezüglich des Kippgelenks des Schwenkrings 2 direkt auf den Schwenkring 2 wirken (Deviationsmoment der Anordnung). Das bedeutet, daß in Bezug auf das Abregelmoment das Stützelement rechnerisch so behandelt werden kann, als wäre es mit dem Schwenkring starr verbunden. Das wiederum führt zu dem entscheidenden Vorteil, daß selbst eine große Aussparung für das Stützelement nicht nachteilig ist, wenn das Stützelement diese ausfüllt. Dies ist insofern von Bedeutung, da gerade die von der Kippachse weit entfernte Masse des Schwenkrings 2 einen entscheidenden Anteil an dem Abregelmoment des Schwenkrings 2 hat. Diese Eigenschaft des Verkippmechanismus führt zu einem relativ hohen Deviationsmoment (Abregelmoment) des Schwenkrings 2 in Kombination mit dem Stützelement 5, wobei dies sogar noch für kleine Auslenkwinkel des Schwenkrings 2 gilt. Dies ermöglicht insgesamt ein sehr gutes Abregelverhalten des Triebwerks bis hin zu sehr kleinen Auslenkwinkeln. Ferner ist ein erfindungsgemäßer Verdichter kostengünstig herzustellen, da der Auslenk- bzw. Kippmechanismus aus relativ wenigen Teilen besteht. Zudem haben die Bauteile der Gaskraftstützen 9 eine sehr einfache Geometrie und wenig Bearbeitungsflächen (beispielsweise zwei Zylinder, bei welchen einer eine Bohrung aufweist). Die wesentlichen Anteile der im Schwenkring auftretenden Kräfte werden durch die Gaskraftstüt2e 9 auf die Antriebswelle übertragen und dann letztlich in der Lagerung der Welle aufgefangen.A further significant advantage results with respect to the inertia properties of the
Abschließend sei angemerkt, daß das Stützelement 5 die Aussparung im Schwenkring 2 soweit wie möglich ausfüllt, wobei selbstverständlich darauf geachtet wurde, daß das Stützelement 5 bei keinem möglichen Auslenkwinkel des Schwenkrings 2 mit den Kolben kollidiert. Die bleibenden Aussparungen, die nicht durch das Stützelement 5 ausgefüllt werden, können beispielsweise durch Verschlußstopfen derart ausgefüllt werden, daß die Kinematik des Verdichters optimiert ist.Finally, it should be noted that the
Obwohl die Erfindung anhand von Ausführungsformen mit fester Merkmalskombination beschrieben wird, umfaßt sie jedoch auch die denkbaren weiteren vorteilhaften Kombinationen dieser Merkmale, wie sie insbesondere, aber nicht erschöpfend, durch die Unteransprüche angegeben sind. Sämtliche in den Anmeldungsunterlagen offenbarten Merkmale werden als erfindungswesentlich beansprucht, soweit sie einzeln oder in Kombination gegenüber dem Stand der Technik neu sind.However, while the invention will be described in terms of embodiments having a fixed combination of features, it also encompasses the conceivable further advantageous combinations of these features, which are particularly, but not exhaustively, indicated by the subclaims. All disclosed in the application documents features are claimed as essential to the invention, as far as they are new individually or in combination over the prior art.
- 11
- Antriebswelledrive shaft
- 22
- Schwenkringswivel
- 33
- Schiebehülsesliding sleeve
- 44
- Federfeather
- 55
- Stützelementsupport element
- 66
- KraftübertragungselementPower transmission element
- 77
- Antriebsbolzendrive pin
- 88th
- Bohrung im Stützelement 5Bore in the support element. 5
- 99
- GaskraftstützeGas force support
- 1010
- Bohrungdrilling
- 1111
- AntriebswellenachseDrive shaft axis
- 1212
- Aussparung in der Antriebswelle 1Recess in the drive shaft. 1
- 1313
-
abgeflachte Seite der Schiebehülse 3flattened side of the sliding
sleeve 3 - 1414
-
Anflachung am Schwenkring 2Flattening on the
swivel ring 2 - 1515
- Nutgroove
- 1616
- Aussparung in der Schiebehülse 3Recess in the sliding sleeve 3rd
- 1717
-
Aussparung im Schwenkring 2Recess in the
pivot ring 2 - 1818
- Längsschlitzlongitudinal slot
- 19,2019.20
- Pfeilarrow
- 2121
- Kippachsetilt axis
- 2222
- Achse des VerdrehmomentesAxis of twisting moment
- 2323
- Absatzparagraph
- 2424
- Sicherungselementfuse element
- 2525
- Angriffspunktattackpoint
- 2626
- Pfeilearrows
Claims (23)
- Axial piston compressor, especially for motor vehicle air-conditioning systems, with a pivoting plate (2), in particular ring-shaped, adjustable in its inclination to a drive shaft (1) driven in rotation by the drive shaft (1), which is connected with at least one support element (5) - in particular flexible - at a distance from the drive shaft (1) and co-rotating with it in which the pistons each have a hinge assembly in which the tilt plate (2) is in sliding operation, and in which the support element (5) is on the radially external end of a power transfer element (6) rotating with the drive shaft (1) and within it fixed approximately in the radial direction,
characterised in that
the power transfer element (6) is rotatably and/or radially slidable in the link to the support element (5), in which both the power transfer element (6) and the support element (5) are cylinder-shaped. - Compressor according to claim 1,
characterised in that
the power transmission element (6) is connected in a rotationally fixed position and/or without radial displacement to the drive shaft (1). - Compressor according to one of the preceding claims,
characterised in that
the support element (5) and the power transmission element (6) form an approximately T-shaped gas power support (9). - Compressor according to one of the preceding claims, in particular claim 3,
characterised in that
the support element (5) comprises a recess, in particular a boring (8), with which the power transmission element (6) engages. - Compressor according to one of the preceding claims,
characterised in that
the support element (5) is mounted in a cylinder-shaped recess (10), in particular a boring in the pivot plate (2), which extends perpendicular to the driving shaft axis (11). - Compressor according to one of the preceding claims,
characterised in that
the support element (5) and the power transmission element (6) are essentially only for axial support of the pistons or gas power support, while an independent device (7), in particular an articulated connection between the drive shaft (1) and swivel plate (2), is essentially used only for torque transfer. - Compressor according to any one of claims 1 or 3 to 6,
characterised in that
the power transmission element (6) is rotatably mounted in the drive shaft (1), while the support element (5) is rotationally fixed and engaged with the power transmission element (6). - Compressor according to any one of claims 1 or 3 to 7, in particular according to claim 8,
characterised in that
the power transmission element (6) is a stud with an at least partially approximately semicircular or semi-elliptical cross-section. - Compressor according to one of the preceding claims, in which the tilt plate (2) is pivotably mounted in plate sheath (3) axially displaceable along the drive shaft (1),
characterised in that
the pivot disc (2) is connected over the drive pin (7) to the plate sheath (3) and/or the drive shaft (1). - Compressor according to claim 9,
characterised in that
the driving pin (7) is pressed in the plate sheath (3) or the swivel plate (2) or secured by axial securing elements in it. - Compressor according to claims 9 or 10,
characterised in that
the drive pins (7) extend into a recess, in particular a groove (15) in the drive shaft (1). - Compressor according to any one of claims 9 to 11,
characterised in that
a connecting element, in particular a sliding key, is arranged between the drive shaft (1) and plate sheath (3) which allows a transmission of forces or torques in a radial direction and is mounted axially displaceably on the drive shaft (1). - Compressor according to any one of claims 9 to 12,
characterised in that
the end of the power transfer element (6) facing away from the support element (5) protrudes through the drive shaft (1) and penetrates a long slot on the plate sheath (3) in such a way that a drive torque of the drive shaft (1) is transferred to the plate sheath (3) by the end of the power transfer element (6) facing away from the support element (5). - Compressor according to claim 5,
characterised in that
areas of the recess (10), in particular the boring in the pivot plate (2), which are not filled by the support element (5), are closed with a balancing weight, in particular in the form of a sealing element or in the form of lock elements, and in particular is or are substantially filled. - Compressor according to any one of claims 9 to 14,
characterised in that
between the plate sheath (3) and the swivel panel (2) a device, in particular at least a cylindrical pin-like element or supporting or contact surface, is provided to support a torque in the drive shaft (1) area. - Compressor according to one of the preceding claims,
characterised in that
the power transfer element (6), in particular the length axis of it, is displaced against the torque axis or the axis of the torque, and in particular the drive shaft axis (1). - Compressor according to one of the preceding claims, in particular claim 16, characterised in that
the support element (5) and/or the power transfer element (6) are/is multi-part. - Compressor according to one of the preceding claims, in particular claim 17,
characterised in that
the power transfer element (6) is angled, especially comprising one section located perpendicular to the tilt torque axis and one protruding through it. - Compressor according to one of the preceding claims, in particular claim 16,
characterised in that
the power transmission element (6) is arranged eccentric to the drive shaft (1). - Compressor according to one of the preceding claims,
characterised in that
the pivot disc (2) is made of steel or brass or bronze. - Compressor according to one of the preceding claims,
characterised in that
the pivot disc (2) has a wear-resistant coating. - Compressor according to one of the preceding claims,
characterised in that
the pistons are made of aluminium or an aluminium alloy or of steel or a steel alloy. - Compressor according to one of the preceding claims,
characterised in that
the support element is barrel-shaped, cigar-shaped or cylindrical or with a diameter tapered from the middle of the barrel, cigar or cylinder to the end of the barrel, cigar or cylinder.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005018102A DE102005018102A1 (en) | 2005-04-19 | 2005-04-19 | Axial piston compressor for motor vehicle air conditioner, has support unit arranged at radial outer end of force transmitting unit that is hinged on support unit, where transmitting unit is rotatable and radially moveable on support unit |
PCT/EP2006/003021 WO2006111264A1 (en) | 2005-04-19 | 2006-04-03 | Axial piston compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1872013A1 EP1872013A1 (en) | 2008-01-02 |
EP1872013B1 true EP1872013B1 (en) | 2014-11-26 |
Family
ID=35070682
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06723979.8A Not-in-force EP1872013B1 (en) | 2005-04-19 | 2006-04-03 | Axial piston compressor |
Country Status (6)
Country | Link |
---|---|
US (1) | US7980167B2 (en) |
EP (1) | EP1872013B1 (en) |
JP (1) | JP5071810B2 (en) |
CN (1) | CN101194104A (en) |
DE (1) | DE102005018102A1 (en) |
WO (1) | WO2006111264A1 (en) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005039199A1 (en) * | 2005-08-18 | 2007-03-08 | Valeo Compressor Europe Gmbh | axial piston |
DE102006014641A1 (en) * | 2006-03-29 | 2007-11-08 | Valeo Compressor Europe Gmbh | compressor |
DE102007022568A1 (en) * | 2007-05-14 | 2008-11-20 | Robert Bosch Gmbh | Retaining segment |
JP5362718B2 (en) | 2007-07-13 | 2013-12-11 | イクセティック・マク・ゲーエムベーハー | Reciprocating piston engine |
WO2009024248A1 (en) * | 2007-08-22 | 2009-02-26 | Ixetic Mac Gmbh | Reciprocating piston machine |
US20110197751A1 (en) * | 2007-08-25 | 2011-08-18 | Ixetic Mac Gmbh | Reciprocating piston machine |
DE102008017263A1 (en) * | 2008-04-04 | 2009-10-08 | Schaeffler Kg | Compressor, in particular for vehicle air conditioning systems |
DE102016105756B3 (en) * | 2016-03-30 | 2017-08-31 | Hanon Systems | Device for compressing refrigerant with variable displacement with a stop in a sliding sleeve for determining the inclination angle of a drive element |
DE102019117170B4 (en) * | 2019-06-26 | 2023-01-12 | Schaeffler Technologies AG & Co. KG | Belt tensioner with a press-fit form-fit connection |
CN116717453B (en) * | 2023-08-09 | 2024-04-12 | 深圳市深旭机电工程设备有限公司 | Air conditioner compressor |
Family Cites Families (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4007126A (en) * | 1975-07-30 | 1977-02-08 | Scott Paper Company | Electrophotographic master conversion solution |
US4061443A (en) * | 1976-12-02 | 1977-12-06 | General Motors Corporation | Variable stroke compressor |
US4506648A (en) * | 1982-11-01 | 1985-03-26 | Borg-Warner Corporation | Controlled displacement supercharger |
US4674957A (en) * | 1984-12-22 | 1987-06-23 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Control mechanism for variable displacement swash plate type compressor |
JP2979687B2 (en) * | 1991-03-26 | 1999-11-15 | 株式会社豊田自動織機製作所 | Variable capacity swash plate compressor |
KR970003251B1 (en) * | 1992-08-21 | 1997-03-15 | 가부시끼가이샤 도요다 지도쇽끼 세이사꾸쇼 | Variable capacity type swash plate compressor |
JP3277580B2 (en) * | 1993-01-08 | 2002-04-22 | 株式会社豊田自動織機 | Oscillating swash plate type variable displacement compressor |
JP3125952B2 (en) * | 1993-04-08 | 2001-01-22 | 株式会社豊田自動織機製作所 | Variable capacity swash plate compressor |
JPH0814157A (en) * | 1994-06-27 | 1996-01-16 | Sanden Corp | Variable capacity cam plate type compressor |
DE19749727C2 (en) | 1997-11-11 | 2001-03-08 | Obrist Engineering Gmbh Lusten | Reciprocating piston machine with swivel plate gear |
FR2782126B1 (en) | 1998-08-10 | 2000-10-13 | Valeo Climatisation | VARIABLE CYLINDER COMPRESSOR |
JP2002147348A (en) | 2000-11-08 | 2002-05-22 | Sanden Corp | Variable displacement swash plate type compressor |
AU2002213826A1 (en) * | 2000-11-10 | 2002-05-21 | Luk Fahrzeug-Hydraulik Gmbh And Co. Kg | Reciprocating piston engine |
DE10124034A1 (en) | 2001-05-16 | 2002-11-21 | Obrist Engineering Gmbh Lusten | Piston machine with pivot fitting has mean power transmission point of pivot fitting on cylinder jacket of piston axis |
JP2003049767A (en) * | 2001-08-07 | 2003-02-21 | Sanden Corp | Variable displacement compressor |
JP2003083241A (en) * | 2001-09-10 | 2003-03-19 | Sanden Corp | Variable displacement compressor |
JP2003269330A (en) | 2002-03-18 | 2003-09-25 | Sanden Corp | Variable displacement compressor |
JP2003269328A (en) * | 2002-03-18 | 2003-09-25 | Sanden Corp | Variable displacement compressor |
DE10315477B4 (en) | 2003-04-04 | 2005-08-11 | Zexel Valeo Compressor Europe Gmbh | Axial piston compressors, in particular CO2 compressors for automotive air conditioning systems |
DE102004041645A1 (en) | 2004-08-27 | 2006-03-16 | Zexel Valeo Compressor Europe Gmbh | axial piston |
DE102005004840A1 (en) | 2005-02-02 | 2006-08-10 | Valeo Compressor Europe Gmbh | axial piston |
-
2005
- 2005-04-19 DE DE102005018102A patent/DE102005018102A1/en not_active Withdrawn
-
2006
- 2006-04-03 EP EP06723979.8A patent/EP1872013B1/en not_active Not-in-force
- 2006-04-03 JP JP2008506958A patent/JP5071810B2/en not_active Expired - Fee Related
- 2006-04-03 CN CNA2006800169282A patent/CN101194104A/en active Pending
- 2006-04-03 WO PCT/EP2006/003021 patent/WO2006111264A1/en active Application Filing
- 2006-04-03 US US11/912,009 patent/US7980167B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
US7980167B2 (en) | 2011-07-19 |
EP1872013A1 (en) | 2008-01-02 |
CN101194104A (en) | 2008-06-04 |
US20090129947A1 (en) | 2009-05-21 |
WO2006111264A1 (en) | 2006-10-26 |
JP2008537052A (en) | 2008-09-11 |
DE102005018102A1 (en) | 2005-11-03 |
JP5071810B2 (en) | 2012-11-14 |
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