EP1917438A1 - Compresseur a pistons axiaux - Google Patents

Compresseur a pistons axiaux

Info

Publication number
EP1917438A1
EP1917438A1 EP06753984A EP06753984A EP1917438A1 EP 1917438 A1 EP1917438 A1 EP 1917438A1 EP 06753984 A EP06753984 A EP 06753984A EP 06753984 A EP06753984 A EP 06753984A EP 1917438 A1 EP1917438 A1 EP 1917438A1
Authority
EP
European Patent Office
Prior art keywords
drive shaft
compressor according
swash plate
transmission element
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.)
Withdrawn
Application number
EP06753984A
Other languages
German (de)
English (en)
Inventor
Otfried Schwarzkopf
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Compressor Europe GmbH
Original Assignee
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 Valeo Compressor Europe GmbH filed Critical Valeo Compressor Europe GmbH
Publication of EP1917438A1 publication Critical patent/EP1917438A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • 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.
  • Compressor known in which the lifting movement of the piston takes place by the engagement of an oblique to the machine shaft annular disc in an engagement chamber.
  • the engagement chamber is provided adjacent to the closed cavity of the piston.
  • so-called 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 is located on a circular line connecting the geometric axes of the seven pistons, and on a circular line connecting the centers of the spherical joints of the pistons.
  • the top dead center position of the piston is determined and ensures a minimum Schadra order. It should be noted at this point that the dead center is constant for all deflection angle or tilt angle of the pivot ring and thus the above-mentioned minimum dead space is guaranteed.
  • the head shape of the free driver end makes it possible to change the inclination of the swashplate, in which the driver head has a bearing body forms 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 P c in the engine room is according to the prior art between a high and a low pressure (suction pressure) adjustable and engages accordingly in the balance of forces on the swash plate. 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 adjusts with increasing rotational speed, i. changes its tilt angle or tilt angle.
  • the trend is to bring pans with such moments of inertia are used, which cause a ⁇ ⁇ reduction in the stroke of the piston and thus a reduction in the capacity at increasing rotational speed.
  • EP 0 964 997 B1 and JP 2003-269330 AA are designed to be very expensive, which requires a high number of parts and therefore costs, with the additional storage being overdetermined by two drivers and thus susceptible to wear is and the strength of the components, in particular by a hole reveal the shaft is rather low.
  • DE 101 52 097 Al Another compressor, which differs considerably from the objects of the above-discussed documents, is known from DE 101 52 097 Al.
  • 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 matter of DE 101 52 097 A1 also has an elaborate construction, it being additionally noted that a large unbalance can occur depending on the tilt angle. This promotes the wear of the compressor and thus reduces its service life.
  • Another compressor is known from FR 278 21 26 Al, which has a driver which extends radially from the drive shaft and engages in the swash plate. Similar to the solution according to DE 101 52 097 Al, also in this construction, the swash plate is fixedly mounted on the driver in the radial direction. This is also a key difference with respect to the objects of EP 0 964 997 Bl and JP 2003-269330 AA.
  • the power transmission between the driving head and the swash plate can be optimally executed (power transmission through surface contact).
  • the problem may be the displacement of the driver in the drive shaft, since there are high forces to be absorbed as a result of the bending moment and the parts must therefore be made very stiff.
  • This rigid design requires an increased mass of the compressor.
  • 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 relatively hysteresis-free or at relatively low hysteresis.
  • the spherical driver head lies in a relatively large recess of the swash plate.
  • 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 discloses a compressor which offers an improvement with regard to the problem of surface pressure.
  • the subject matter of DE 10 2005 004 840 has a support element which engages with a swivel ring, whereby a line contact is formed between the support element and the swivel ring. This represents an improvement with respect to the Hertzian pressure in comparison with the prior art explained above. It also has the advantageous effect that in the subject matter of DE 10 2005 004 840 a drive torque and a twisting moment are decoupled from the gas force support. However, a relatively large recess in the swash plate is necessary in order to ensure a sufficient length of the line contact.
  • a determination of the required diameters or cross-sectional profile of the force transmitting element leads to the conclusion that it would be desirable to reduce the size of such a compressor. Since the force transmission element is integrated into the bore of the support element and for this purpose also provide a sufficient strength for restoring residual wall thickness, there is also a considerable diameter of the support element. A similar problem arises when the support member is finally integrated into the swash plate or the swivel ring. Thus, this type of configuration determines the height of the swash plate in not inconsiderable extent.
  • An essential point of the invention is therefore that the support element in the radial direction and / or perpendicular thereto, in particular in a direction perpendicular to the drive shaft axis, is slidably articulated on the force transmission element.
  • the support member is formed as a cylinder bolt, whereby an optimal Hertzian pressure is ensured at the same time a simple structural design.
  • the support element may have a groove with which the force transmission element is in operative engagement.
  • the support member may also have a pocket-shaped recess, wherein pocket-shaped in the sense of the present application in particular denotes a rectangular or round or elliptical recess in the support element.
  • at least the end region of the force-transmission element facing the support element is optionally designed in the form of a flat steel, ie with an approximately rectangular peripheral contour.
  • the power transmission element may also be rotatably connected to the drive shaft, which guarantees a simple construction of a compressor according to the invention.
  • the force transmission element can also be rotatably mounted on or in the drive shaft.
  • the power transmission element can also be part of the drive shaft or integrated into it.
  • the power transmission element is formed integrally with the drive shaft. This ensures a functional design with low design effort.
  • the support member and the power transmission element essentially serve only for the axial support of the piston or to a gas force support, while a device independent thereof, in particular a hinge connection between the drive shaft and swash plate essentially serves only for torque transmission. This ensures the decoupling of drive torque and Gaskraftab- support.
  • the swash plate is preferably pivotably mounted on a sliding sleeve axially displaceably mounted along the drive shaft, the swivel disk being connected via drive bolts to the sliding sleeve and / or the drive shaft.
  • the drive bolts can be pressed into the sliding sleeve or the swash plate or secured by axial securing elements or snap rings in or on the same.
  • the drive bolts can protrude into a recess, which can 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 member facing away from the end of the power transmission element can also extend 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.
  • a device for a reliable transfer of the rotational torque, a device, in particular, can also be provided between the sliding sleeve or the drive shaft and the swivel disk. be provided in particular in the form of flattened contact surfaces. It should be mentioned at this point that both embodiments with sliding sleeve and embodiments without sliding sleeve are conceivable, so that the torque transfer on the one hand depending on the embodiment between a corresponding flattening of the drive shaft and a corresponding flattening in the swash plate as well as directly or indirectly via corresponding flats between the drive shaft and / or sliding sleeve on one side and the swash plate on the other side can be done. This ensures a safe torque transfer.
  • the support element is optionally mounted in a cylindrical recess, in particular in a bore in the swash plate.
  • the bore may extend perpendicular to the drive shaft axis.
  • the support element is secured with at least one snap ring in the corresponding recess, in particular cylindrical recess in the swash plate. Additionally and / or alternatively, the support element is secured with at least one threaded fastener in the corresponding recess in the swashplate. This may be a grub screw. It should be noted at this point that a combination of a snap ring and a grub screw for securing the support element is conceivable. In a structurally preferred embodiment, the at least one or in particular two fastening elements are arranged in the recess in the swash plate.
  • the at least one fastening element can be arranged in a radially extending (possibly additional) recess in the swivel disk and extend into a recess, possibly into a further groove in the support element, which is arranged thereon.
  • the groove is preferably arranged along the longitudinal axis of the support element.
  • the power transmission element may be formed at its end facing the drive shaft annular or sleeve-shaped and mounted with the aid of the annular or sleeve-shaped end on the outer diameter of the drive shaft, fastened or slipped over the drive shaft.
  • the power transmission element can also be in operative engagement with an annular or sleeve-shaped element, which in turn is mounted or articulated on the outer diameter of the drive shaft or otherwise in operative engagement with the drive shaft.
  • the power transmission element if it is annular at its end facing the drive shaft or is formed hulsenformig secured or secured in the radial direction by a feather key on the drive shaft. The same naturally also applies if it is a component which is composed of a force transmission element and an annular element.
  • the force transmission element or the ring-shaped / hulsenformige element can also optionally in the axial direction by a machine element, in particular in the form of a groove nut or another axial securing element secured to the drive shaft.
  • the annular or hulsenformige end of the Kraftubertragungselements or the ring or hulsenformige element have at least one extending in the axial direction groove, in which engages or engage the device or devices for transmitting the torque.
  • these are drive bolts, which engage in the corresponding groove.
  • the structural design described above is a structure which does not engage the drive shaft and, in particular, does not interfere with the stability of the drive shaft ,
  • a length compensation which is preferably arranged in approximately the radial direction, can be provided between the support element and the force transmission element.
  • This length compensation can also be implemented alternatively and / or additionally by a telescopic mechanism or the like in addition to an articulation of the support element on the force transmission element, which permits a displacement of the support element in a direction perpendicular to the drive shaft axis.
  • the center of the joint or the articulation between support element and swashplate is preferably radially further away from the drive shaft center axis for small deflection angles of the swashplate than the center of a joint resulting from the articulation of the piston or pistons on the swashplate is.
  • the geometry preferably shifts to the effect that the center of the joint or the articulation of the support member to the swashplate closer to the drive shaft center axis as the center of the joint, which realizes the articulation of the piston to the swashplate aforementioned centers of the joints for at least one, in particular for exactly one tilt angle or Auslenkwmkel the swash plate radially equidistant from the drive shaft center axis.
  • the center axis of the support element or of the force transmission element preferably includes an angle which is not equal to 90 ° with the drive shaft center axis for all deflection angles of the swashplate.
  • the mean deflection angle of the swash plate can be approximately half the difference of maximum angle, below which the central axis of the support element or of the power transmission element is arranged on the swash plate, and the minimum angle at which the center axis of the support element or of the power transmission element is arranged on the swash plate correspond.
  • the radial distance of the joint between the support element and the Kraftubertra- gungselement is greater in a further preferred embodiment for small deflection angle of the swash plate of the drive shaft center axis, as the radial distance of the center of the Piston joints of the drive shaft center axis is.
  • the sum of the moments as a result of the translato ⁇ sch moving masses such as pistons, sliding blocks, etc. and due to the rotationally moving masses (swash plate, etc.) is preferably for all deflection angle, in particular for large deflection and further, in particular for the maximum deflection angle of the swash plate is approximately constant.
  • the sum of the moments is constant 0. This ensures the desired control characteristic of the compressor according to the invention
  • the support element has a recess extending in the radial direction, in which the force transmission element is mounted.
  • the recess may in particular have approximately a rectangular configuration or a rectangular cross section.
  • the cross-section of the recess may optionally increase outwardly in a radially outer region in the radial direction while being approximately constant in a radially inner region of the recess.
  • the radially outer (frontal) edges of the Kraftubertragungselements are arranged for each tilt angle of the swash plate in the radially outer region of said recess. In other words, this means that the end-side edges protrude beyond the region of the approximately constant recess cross-section. Due to the constructive features described above, male ensures that the power transmission element in the storage serving recess of the support member is not tilted or blocked.
  • a compressor according to the invention has a housing and an engine compartment essentially defined by the housing, a fluid connection being arranged between the engine compartment and a suction gas side, which extends at least partially through the drive shaft.
  • a fluid connection being arranged between the engine compartment and a suction gas side, which extends at least partially through the drive shaft.
  • the fluid connection optionally comprises at least one approximately axially extending and at least one approximately radially extending recess in the drive shaft.
  • Recesses can be present in particular in the form of holes. Further preferably, at least the drive shaft-facing end portion of the force-transmitting member is approximately cylindrical, i. So formed with an approximately circular cross-section.
  • the power transmission element can be pressed into the drive shaft or fitted by means of a press fit.
  • the drive shaft-side end of the force-transmitting element has a particularly semicircular or groove-like recess, which is a component of the fluid connection between the engine compartment and the suction gas side.
  • the force transmission element can be mounted centrally in the drive shaft, which prevents imbalances, while at the same time the fluid connection between the engine room and the suction side, which as already mentioned above, serves to control the deflection angle of the swash plate, in a simple manner and in particular without additional Components can be realized.
  • FIG. 1 shows a swashplate mechanism of a preferred embodiment of a compressor according to the invention in an exploded view; 2a + b show the preferred embodiment of FIG. 1 at a minimum deflection angle of the swash plate (a) and at a maximum deflection angle of the swash plate (b),
  • Fig. 3a + b is a schematic representation showing the possibilities for mounting the
  • Pivoting disc of a compressor according to the invention represents
  • FIGS. 4a-c is a schematic illustration of a swashplate mechanism of the preferred embodiment, illustrating a swivel cycle
  • Figure 7 is a qualitative representation of the control characteristic of the preferred embodiment for a specific operating point and different speeds.
  • FIGS. 8a-e show an illustration of various possibilities for securing the articulation of the force transmission element to the support element
  • Fig. 9a + b is a sectional view illustrating another possibility of articulation of the power transmission element to the support member
  • FIG. 10 shows the mechanism according to FIG. 9 in a partial sectional view
  • Fig. 1 1 a drive shaft with Kraftubertragungselement another preferred embodiment of an inventive compressor.
  • the preferred embodiment of a compressor according to the invention comprises (not shown in the drawings) a housing, a cylinder block and a cylinder head.
  • pistons are mounted axially movable back and forth.
  • the compressor described is a variable displacement compressor with the piston stroke regulated by a pressure differential defined by the pressures on a suction gas side and in an engine chamber.
  • a swivel disk in the form of a swivel ring 2 is more or less deflected or pivoted out of its or its vertical position. The greater the resulting swivel angle or deflection angle, the larger is the piston stroke and accordingly, the higher the pressure is provided on an outlet side of the compressor
  • the swash plate mechanism of the preferred embodiment the drive shaft 1, the swivel ring 2, a sliding sleeve 3, mounted on the drive shaft 1 axially against the action of an elastic element in the form of a nng- or helical fitting or restoring spring 4 is, as well as a support element 5 and a force transmission element 6 comprises.
  • the support element 5 is articulated both radially and (in a direction perpendicular to the drive shaft axis) perpendicular to the power transmission element 6, which means that the support element 5 is slidably mounted in a plane (and not only along an axis).
  • the support element 5 is formed zylmderbolzenformig and has a groove 7, by means of which the support member 5 is in operative engagement with the force transmission element 6.
  • the support element 5 facing the end or is the support member 5 facing end portion of the Kraftubertragungselements 6 in the form of a flat steel.
  • This means, therefore, that the said end region of the force transmission element 6 has an approximately right-angled peripheral contour.
  • This approximately rectangular shaped end portion is engaged with the groove 7 of the support member 5 in engagement.
  • the strength of the force transmission element 6 increases, while it is designed to be hulsenformig on its end facing the drive shaft 1.
  • the hulsenformigen part 8 of the power transmission element 6 selbiges is mounted or fixed to the drive shaft 1.
  • the force transmission element 6 is formed in one piece and also in one material with the hulsenformigen part 8.
  • the force transmission element 6 and the hulsenformigen part 8 could be two different components (possibly even from different materials).
  • the force transmission element 6 or the hulsenformige part 8 of the power transmission element 6 has two recesses in the form of grooves 9.
  • the sleeve-shaped part 8 can be pushed under the spring 4 in the assembled state of the swashplate mechanism. This means that the sleeve-shaped part 8 is placed over the drive shaft 1 and radially fixed by the spring 4 on the drive shaft 1.
  • the sliding sleeve 3 which has a recess 10 corresponding to the force transmission element 6, is then slipped over the drive shaft 1.
  • the sliding sleeve 3 also has two recesses in the form of holes 1 1.
  • the force transmission element 6 and the sliding sleeve 3 are secured by a groove nut 12 (see Fig. 2) on the drive shaft 1.
  • a plate spring 23 is further arranged on the drive shaft 1, which ensures that the compressor does not start at a minimum deflection angle of the pivot ring 2.
  • 2 stops in the form of stop plates 24, 25 are arranged on the drive shaft, which limit the deflection angle of the pivot ring.
  • the stop disc 24 serves as a stop for a minimum deflection angle
  • the stop plate 25 serves as a stop for a maximum deflection angle of the pivot ring 2.
  • the support element 5 is mounted in a cylindrical recess in the form of a bore 13 in the pivot ring 2.
  • the bore 13 extends perpendicular to the drive shaft axis.
  • the power transmission element 6, which in the present preferred embodiment of leadership form rotatably connected to the drive shaft 1, in other imple mentation forms also rotatably with the same can be in operative engagement.
  • the drive shaft 1 is not broken through the sleeve-shaped formation or the sleeve-shaped part 8 of the force transmission element 6 and thus has corresponding stability.
  • the clear width of the bore of the pivot ring 2 is at least slightly larger than the corresponding extent of the force transmission element. 6
  • the mechanism of support element 5 and force transmission element 6 is not intended to transmit the torque from the shaft to the swash plate in the form of the swivel ring 2.
  • the bearings between the support element 5 and the power transmission element 6, between the power transmission element 6 and drive shaft 1 and between the support member 5 and pivot ring 2 are not designed to transmit torque. Accordingly, it eliminates a kind of driving function for the support element 5 and the force transmission element 6 This is deliberately chosen for reasons of hysteresis, ie the tilting of the pivot ring 2 and the torque transmission are functionally decoupled from each other.
  • the mechanism of force transmission element 6 and support element 5 essentially absorbs the piston forces.
  • the torque in turn is transmitted from the drive shaft 1 to the swivel ring 2 by a tilting joint (implemented by drive bolt 15) provided on the drive shaft center axis the pivot ring 2 transmitting drive pin 15 are locked or secured to the pivot ring with snap rings 16.
  • the swivel ring 2 has
  • Flattening 17, which corresponds to flattening 18 on the sliding sleeve 3 principle in other forms from export also denkbai that the sliding sleeve 3 is omitted and the torque transmission takes place in any form between drive shaft and pivot ring 2 directly (eg via flats on the drive shaft. 1 and the swivel ring 2).
  • FIGS. 2 a and b the preferred embodiment of the compressor according to the invention is again shown in the assembled state for an angle of minimum deflection (FIG. 2 a) and an angle of maximum deflection (FIG. 2 b).
  • V indicates the position of the joint with groove, that is to say the position of the joint formed by support element 5 and force transmission element 6, while “U” represents the position of the piston.
  • the inventive configuration of support element 5 and force transmission element 6 is both possible that the radius U corresponds to the radius V, and that U is less than V, and also that U is greater than V By the large number of degrees of freedom it comes to a low Hertzian pressure and low wear, since no jamming occurs.
  • Fig. 3a the assembly of the preferred embodiment of the inventive compressor is shown. Since the diameter of the force transmission element 6 includes lent to the sleeve-shaped part 8 is larger than the bore in the pivot ring 2, the pivot ring 2 is slipped over the force transmission element 6 in an oblique position and then spent in a position perpendicular thereto, whereby the force transmission element 6 is moved into the recess 13. If the diameter of the bore in the swivel ring is larger than the diameter of the force transmission element 6 (see FIG. 3b) as in another preferred embodiment of a compressor according to the invention, the swivel ring 2 can be slipped vertically over the force transmission element 6 and through a sideways movement with the same or the support member 5 are brought into operative engagement.
  • FIG. 4 a shows a schematic representation of a swivel disk unit of a compressor according to the invention for large deflection angles; in the figures 4b and 4c further sections of the Fig. 4a for deviating from the Fig. 4a deflection angle of the pivot ring 2 are shown (average and small deflection angle).
  • the kinematics of the oiler take into account the position of the sliding blocks of the pistons through the center at C and the position of the support element 5 at B. The distance between C and B is a snapshot, which depends on the deflection angle. For large deflection angles results (see Fig.
  • Fig. 4c Center B of the support member 5 in the pivot ring 2 with the center of the piston joint or with the circular cylinder, on which lie the centers of the piston joints, coincides.
  • Fig. 4c finally (which corresponds to a small pivot angle) is the center B of the support member 5 radially outside of the circular cylinder b. on which the piston center axes lie.
  • B and C may both coincide in the preferred embodiment, as may be the case that B comes to lie to the left or right of an axis b passing through C.
  • the terms in Figs. 4a to 4c mean the following: A joint (center) of the swing ring 2 on the drive shaft guide; B joint (center) of the support element 5 in the pivot ring 2;
  • Piston used Piston used); c center line of the swivel ring 2, on which (preferably) the centers B and C are located; d support element or force transmission element center axis; e perpendicular connection from the drive shaft center axis to the center B; f perpendicular connection from the drive shaft center axis to the center C; ⁇ tilt angle of the support or force transmission element (constant, structurally selected) ß tilt angle of the swivel ring 2.
  • the center of the joint B moves toward the drive shaft center axis a; This shortens the distance B-D.
  • the degree of freedom necessary for the variation of the route length results from the articulation of the support element 5 according to the invention on the force transmission element 6.
  • the distance B-D is the hypotenuse of the triangle BDF. Catheters D-F and F-B of the right triangle also shorten. For the dead space, which is normally to be minimized, the distance D-F is of great importance.
  • FIG. 6 shows the torque distribution of the preferred embodiment of the compressor according to the invention, from which it can be seen that the sum of the moments as a result of the translationally moving masses and the moments due to the deviation moment of the swash plate is over the entire tilt angle range of the swash plate or of the swash plate Virtually equalize swivel ring 2
  • This torque distribution leads to a control characteristic, as shown in Fig. 7 for a certain operating point and for different speeds n. It can be seen from FIG. 7 that the control characteristic is very similar for different rotational speeds n, which results from the optimized torque distribution of the compressor.
  • FIGS. 8a to e show various possibilities for securing the support element 5 in the corresponding recess (bore 13) in the swivel ring 2.
  • a securing of the support element 5 in the bore 13 is necessary in particular due to the centrifugal forces acting.
  • the securing takes place by means of two snap rings 14.
  • a fuse is provided by a combination of a snap ring 14 and a grub screw 19, which is placed in a corresponding hole in the bore Thread engages, conceivable.
  • the mass inertia of the pivot ring 2 can be favorably influenced by the additional introduction of the mass of the grub screw 19 (which has a large mass compared to a snap ring 14). It is conceivable, with the grub screw the majority of the bore 13, which is not filled with the support member 5 to close Alternatively or additionally, plugs are conceivable at the ends of the bore. These can also be made of a deviating from the material of the pivot ring 2 material, in particular a heavier material, so as to compensate for the lack of inertia
  • a further possibility for securing the support element 5 is shown.
  • no through hole, but only a blind bore 20 is mounted in the swivel ring 2.
  • After mounting the support member 5 is selbiges secured with a snap ring 14.
  • a grub screw and / or a corresponding plug are shown.
  • the support element 5 does not have a continuous groove but only a type of pocket 22, i. So a recess, which is found in the central region of the support element.
  • a recess which is found in the central region of the support element.
  • basically no own backup mechanism is required and the bore 13 can be closed on the sides if necessary with plugs made of any material.
  • Such a configuration is particularly useful when an assembly according to FIG. 3b is performed or can be performed.
  • the recess or pocket 22 shown in FIG. 8d is manufactured, for example, in a simple manner with a disk milling cutter, which ensures simple production.
  • a further possibility for securing the support element is shown.
  • another, provided with a threaded recess in the pivot ring 2 is mounted in the radial direction, in which a grub screw 21 is introduced.
  • the grub screw protrudes beyond the radially outer edge of the bore 13 and engages in a corresponding groove attached to the support member 5, so that the support member 5 is secured against slipping in the bore 13.
  • FIGS. 9a and 9b show a further preferred embodiment of a swash plate mechanism of a compressor according to the invention.
  • This has as the swash plate mechanism, which is shown in Fig. 1, the swivel ring 2 and the sliding sleeve 3, which is mounted axially on the drive shaft 1, on.
  • the swashplate mechanism is shown in Fig. 9a for a minimum deflection angle of the swivel ring 2
  • Fig. 9b illustrates the swashplate mechanism at a maximum deflection angle of the swivel ring 2.
  • the support element 5 (see also in particular Fig. 10) no groove or pocket-shaped recess, but an approximately rectangular recess 26 which extends in the radial direction through the entire support element extends through.
  • the power transmission element 6, which as already mentioned above, has a flat steel-like design at its radially outer end, engages in the recess 26 and thus forms the articulation of the force transmission element 6 on the support element 5.
  • edges 29 protrude beyond the area of the roughly constant recess cross section for each tilt angle of the swashplate with the support element 5 in each operating point of the compressor avoided friction and hysteresis in the area of the mechanism are thereby reduced, resulting in a small Wear and low heat generation during operation leads.
  • a further preferred embodiment of a compressor according to the invention is shown, wherein in this preferred embodiment, the force transmission element is not part of a sleeve or is not connected to a sleeve, but is pressed into the drive shaft.
  • the Kraftubertragungselement has at its radially outer, the support member end facing the shape of a flat steel.
  • the force transmission element 6 is cylindrical, wherein in the region of the drive shaft, ie where the force transmission element is pressed into the drive shaft, the same has an approximately semicircular or groove-like recess 30 has.
  • the recess 30 in the power transmission element 6 is part of a fluid connection
  • This fluid connection serves to regulate the pressure in the engine chamber and thus the regulation of the piston stroke.
  • the fluid connection extends through the drive shaft 1, besides the recess 30, an approximately axially extending recess in the drive shaft, which in the form of a bore
  • the bore 32 is rounded at its suction-gas-side end into a cylindrical recess 33 (bore).
  • Conceivable are more holes in the drive shaft in the radial direction, in particular in the region of the bearing of the drive shaft, whereby the oil collecting on the walls of the bore 32 escape into the bearings and thus can supply the same with an optimal lubrication.
  • a stop disc 35 is attached to the drive shaft 1 in order to limit the maximum pivot angle or deflection angle of the pivot ring 2.
  • the swivel ring 2 is made of steel in the embodiments described above and provided with a coating which minimizes the wear and the friction between the Glcitsteinen the piston and the swivel ring 2.
  • the swivel ring 2 may be made of brass or bronze. The materials mentioned ensure that the design-related requirements are met. In the case of the pivoting rings 2 used are namhch to rings that build very high compared to the prior art.
  • the height is desired in order to be able to support the gas power support, which is composed of the support element 5 and the force transmission element 6; on the other hand, the height is advantageous in order to be able to associate the component with a sufficient mass inertia. This is necessary for a tilting moment due to the gyroscopic effect during the rotation of the swivel ring 2, which is large enough to compensate or overcompensate to the extent desired the counteracting tilting moments due to the mass forces of the piston
  • the materials steel, brass or bronze are particularly suitable for such swivel rings 2, 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 state of the art, this is often not satisfactory - chert.
  • the density of bronze or brass may be somewhat greater than the density of steel or that of gray carbon black (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 (in operation with heat generation) only insignificantly or even not enlarged. This leads to a low noise and prevents sliding blocks can fall out as a result of too big a game.
  • pistons which are also made of steel, offer the same advantages.
  • other material combinations in particular from the viewpoint of a weight reduction of a compressor according to the invention are conceivable.
  • a mechanism as described above ie a swashplate mechanism comprising a swivel ring, is particularly suitable for a compressor employing R744 (CO 2 ).
  • R744 CO 2
  • it can also be used for refrigerants such as Rl 34a, Rl 52a, etc., as well as for refrigerants such as those mentioned in US Pat. No. 6,969,701 and WO 2006/012095 (eg azeotropic mixtures of tetrafluoropropenes and trifluoroiodomethanes).

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

Abstract

L'invention concerne un compresseur à pistons axiaux, en particulier un compresseur conçu pour des installations de climatisation de véhicule automobile. Ce compresseur comprend au moins un piston, ainsi qu'un plateau orientable, en particulier un plateau orientable circulaire qui est animé d'un mouvement de rotation par l'arbre de transmission (1), dont l'inclinaison peut être ajustée par rapport à cet arbre de transmission (1), et qui est relié, en particulier de manière articulée, avec au moins un élément de soutien (5) qui est placé à une distance de l'arbre de transmission (1) et disposé de manière à pouvoir effectuer un mouvement de rotation avec celui-ci. Selon l'invention, le(s) piston(s) comporte(nt) respectivement un ensemble articulation contre lequel le plateau orientable (2) est en contact de glissement. En outre, l'élément de soutien (5) coopère avec un élément de transmission de force (6) qui effectue un mouvement de rotation avec l'arbre de transmission (1). Ledit élément de soutien (5) est articulé sur l'élément de transmission de force (6) de manière à pouvoir être déplacé dans la direction radiale et/ou perpendiculairement à celle-ci, en particulier perpendiculairement à l'axe de l'arbre de transmission.
EP06753984A 2005-08-18 2006-05-30 Compresseur a pistons axiaux Withdrawn EP1917438A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005039199A DE102005039199A1 (de) 2005-08-18 2005-08-18 Axialkolbenverdichter
PCT/EP2006/005151 WO2007019903A1 (fr) 2005-08-18 2006-05-30 Compresseur a pistons axiaux

Publications (1)

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EP1917438A1 true EP1917438A1 (fr) 2008-05-07

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EP06753984A Withdrawn EP1917438A1 (fr) 2005-08-18 2006-05-30 Compresseur a pistons axiaux

Country Status (6)

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US (1) US20090220353A1 (fr)
EP (1) EP1917438A1 (fr)
JP (1) JP2009504981A (fr)
CN (1) CN101287908A (fr)
DE (1) DE102005039199A1 (fr)
WO (1) WO2007019903A1 (fr)

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US9222302B2 (en) 2013-12-27 2015-12-29 Pella Corporation Fenestration covering lift system and method
US9482046B2 (en) 2013-12-27 2016-11-01 Pella Corporation Fenestration covering tilt system and method
DE102018110881A1 (de) * 2018-05-07 2019-11-07 Schaeffler Technologies AG & Co. KG Anordnung zur Fliehkraftsicherung zumindest eines auf einer Rotorwelle einer elektrischen Maschine zur Lagesicherung axial festgesetzten Sicherungsrings und Verwendung einer solchen Anordnung

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Also Published As

Publication number Publication date
JP2009504981A (ja) 2009-02-05
DE102005039199A1 (de) 2007-03-08
CN101287908A (zh) 2008-10-15
US20090220353A1 (en) 2009-09-03
WO2007019903A1 (fr) 2007-02-22

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