US20090220353A1 - Axial Piston Compressor - Google Patents

Axial Piston Compressor Download PDF

Info

Publication number
US20090220353A1
US20090220353A1 US12/064,074 US6407406A US2009220353A1 US 20090220353 A1 US20090220353 A1 US 20090220353A1 US 6407406 A US6407406 A US 6407406A US 2009220353 A1 US2009220353 A1 US 2009220353A1
Authority
US
United States
Prior art keywords
drive shaft
tilt plate
force transmission
compressor according
transmission 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.)
Abandoned
Application number
US12/064,074
Other languages
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
Assigned to VALEO COMPRESSOR EUROPE GMBH reassignment VALEO COMPRESSOR EUROPE GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SCHWARZKOPF, OTFRIED
Publication of US20090220353A1 publication Critical patent/US20090220353A1/en
Abandoned legal-status Critical Current

Links

Images

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, especially a compressor for motor vehicle air-conditioning systems, in accordance with the preamble of claim 1 .
  • spherical segments For sliding engagement that is substantially free from play in any slanting position of the tilt plate or tilt ring there are provided on both sides, between it and the spherically curved inner wall of the engagement chamber, spherical segments, so-called sliding blocks, so that the tilt ring slides between them as it revolves.
  • the drive is transmitted from the drive shaft to the tilt ring by means of a pin for conjoint movement which is attached to the drive shaft and the spherical head of which engages in a radial bore in the tilt ring, the position of the head of the member for conjoint movement being selected so that its centre-point coincides with that of the spherical segments.
  • that centre-point is located on a circular line which connects the geometric axes of the seven pistons with one another and, moreover, on a circular line which connects the centre-points of the spherical articulation members of the pistons.
  • the dead centre is constant for all deflection angles, or tilt angles, of the tilt ring and accordingly the afore-mentioned minimum clearance volume is ensured.
  • the head shape of the free end of the member for conjoint movement makes it possible for the inclination of the tilt plate to change by means of the fact that the head of the member for conjoint movement forms a bearing body for a tilting movement of the tilt plate which changes the stroke distance of the pistons.
  • a further precondition for tilting of the tilt plate is the displaceability of its mounting axis in the direction of the drive shaft.
  • the mounting axis is formed by two mounting pins mounted on the same axis on each side of a sliding sleeve, which mounting pins are additionally mounted in radial bores in the tilt plate.
  • the sliding sleeve preferably has mounting sleeves on each side, which span the annular space between the sliding sleeve and the tilt plate in the manner of spokes.
  • the pressure PC in the drive mechanism chamber can be regulated between a high pressure and a low pressure (inlet pressure) and consequently affects the balance of forces at the tilt plate, which influences the inclination of the latter.
  • the position of the sliding sleeve can moreover be influenced by springs which, in various variants, are likewise included in the prior art.
  • the position of the sliding sleeve which position governs the delivery output, is also determined by the forces of inertia acting on the tilt plate; the position of the tilt plate, that is to say its angle of tilt or slant, changes with increasing speed of rotation.
  • the trend is towards using tilt plates having moments of inertia such that they bring about a reduction in the stroke distance of the pistons and therefore a reduction in delivery output when the speed of rotation increases.
  • a compressor similar to the compressor known from EP 0 964 997 B1 is known from JP 2003-269330 M, although in that compressor a total of two members for conjoint movement are used.
  • a further compressor is known from DE 101 52 097 A1, differing considerably from the subject-matter of the publications discussed hereinbefore.
  • the member for conjoint movement in particular the spherical head of the member for conjoint movement, is replaced by a hinge pin or spindle.
  • This is, however, integrated into the tilt plate from the outside and fastened using a cup-shaped disc for conjoint movement which is a component of the drive shaft assembly.
  • the subject-matter of DE 101 52 097 A1 also has a complicated structural arrangement; in addition it has to be borne in mind that a large imbalance can come about, depending on the angle of tilt. This encourages wear on the compressor and as a result reduces its service life.
  • a further compressor is known from FR 278 21 26 A1, which has a member for conjoint movement extending out from the drive shaft radially and engaging in the tilt plate.
  • the tilt plate in this arrangement is also fixed to the member for conjoint movement in radial extension.
  • the advantage of this approach lies in the fact that the forces or surface contact pressure due to the forces applied (because of the fact that these forces are relatively low) do not cause any excessive deformation at and in the member for conjoint movement, as a result of which the member for conjoint movement can be of correspondingly lightweight construction and tilting of the tilt plate can be accomplished in a relatively hysteresis-free manner or with relatively little hysteresis.
  • a disadvantageous effect can be that the spherical head of the member for conjoint movement is located in a relatively large recess in the tilt plate.
  • the Hertzian stress can or must be described by a plane/sphere geometric pairing, which is relatively disadvantageous because it causes a high degree of Hertzian stress.
  • DE 10 2005 004 840 From the likewise unpublished DE 10 2005 004 840 belonging to the present Applicant, there is known a compressor which provides an improvement in respect of the problem of surface contact pressure.
  • the subject-matter of DE 10 2005 004 840 includes a support element in engagement with a tilt ring, with line contact arising between the support element and the tilt ring. Compared to the previously described prior art, this constitutes an improvement in respect of the Hertzian stress.
  • a likewise advantageous effect is that, in the case of the subject-matter of DE 10 2005 004 840, a drive moment and a torsional moment are decoupled from gas force support.
  • an estimate of the requisite strengths or the dimensions required therefor results in a force transmission element diameter of 8 mm, a supporting element diameter of 14 mm (maximum residual wall thickness 3 mm) and a tilt plate height of 18 mm (maximum residual wall thickness 2 mm). Because the height of the tilt plate substantially influences the bridging region of the piston, which connects the bottom sliding block accommodating means to the top sliding block accommodating means, a more compact mode of construction is desirable. The larger the bridging region, the larger the ensuing bending moments become. Although appropriate dimensioning does prevent this, such a compressor then has a large housing diameter.
  • the problem of the present invention is accordingly to provide a compressor wherein the mounting between the force transmission element and supporting element is so arranged that on the one hand a low degree of deformation in the region of the mounting is ensured whilst at the same time the tilt plate has a height which is as small as possible whilst ensuring consistently low Hertzian stress in the course of force transmission.
  • a fundamental point of the invention accordingly is that the supporting element is in articulated connection with the force transmission element so as to be displaceable in a radial direction and/or perpendicular thereto, especially in a direction perpendicular to the drive shaft axis.
  • the supporting element can be displaceable along an axis or, especially, in a plane.
  • a smaller force transmission element than in the prior art can be used, because the requisite strength and rigidity is provided by a wide mounting.
  • the desired low degree of deformation can also be ensured in a relatively small constructional form.
  • the desired low degree of Hertzian stress is also ensured in the course of force transmission.
  • the supporting element is in the shape of a cylindrical pin, as a result of which optimal Hertzian stress is ensured at the same time as a constructionally simple structure.
  • the supporting element can have a groove with which the force transmission element is in operative engagement.
  • the supporting element can also have a pocket-shaped recess, “pocket-shaped” denoting under the terms of the present invention an especially rectangular but also round or elliptical recess in the supporting element.
  • at least that end region of the force transmission element which faces the supporting element is formed in the shape of a flat steel part, that is to say having an approximately rectangular peripheral contour.
  • the force transmission element can furthermore be connected to the drive shaft in a manner which does not allow relative rotation, which ensures that a compressor according to the invention has a simple structure.
  • the force transmission element can also of course be rotatably mounted on or in the drive shaft.
  • the force transmission element can also be part of the drive shaft or integrated into the latter.
  • the force transmission element is formed in one piece with the drive shaft. This ensures a functional construction at the same time as a low degree of constructional complexity.
  • the supporting element and the force transmission element serve substantially only for providing the pistons with axial support or, that is, for gas force support, whereas an arrangement independent thereof, especially an articulated connection, between the drive shaft and the tilt plate serves substantially only for torque transfer. This ensures decoupling of the drive torque and gas force support.
  • the tilt plate being pivotally mounted on a sliding sleeve mounted so as to be axially displaceable along the drive shaft, the tilt plate being connected by way of drive pins to the sliding sleeve and/or to the drive shaft.
  • the drive pins can be introduced into the sliding sleeve or the tilt plate with a press fit or secured therein or thereon by means of axial securing elements or circlips.
  • the drive pins can project into a recess, which can especially be in the form of a groove in the drive shaft.
  • a connecting element is arranged between the drive shaft and the sliding sleeve, which connecting element allows transfer of forces and moments in a radial direction and which is mounted in axially displaceable manner on the drive shaft. That end of the force transmission element which is remote from the supporting element can also project through the drive shaft and into a longitudinal slot in the sliding sleeve in such a way that drive torque is transferred from the drive shaft to the sliding sleeve by means of that end of the force transmission element which is remote from the supporting element.
  • the above-mentioned constructional features ensure reliable decoupling of drive torque and gas force support, as a result of which both the force transmission element and the supporting element can be of appropriately “slim” construction.
  • the supporting element is optionally mounted in the tilt plate in a cylindrical recess, especially a bore.
  • the bore therein can extend perpendicular to the drive shaft axis. This constructional measure also ensures a simple means of producing a compressor according to the invention.
  • the supporting element is secured in the corresponding recess, especially the cylindrical recess, in the tilt plate by means of at least one circlip. Additionally and/or alternatively, the supporting element is secured in the corresponding recess in the tilt plate by means of at least one threaded fastening element.
  • the latter can be a grub screw. It should be noted at this point that a combination of a circlip and a grub screw is also feasible for securing the supporting element.
  • the at least one fastening element or especially two fastening elements is/are arranged in the recess in the tilt plate.
  • the at least one fastening element can be arranged in a radially extending (optionally additional) recess in the tilt plate and can extend into a recess, optionally a further groove, in the supporting element, which recess is arranged on the latter.
  • the groove is preferably arranged along the longitudinal axis of the supporting element.
  • the force transmission element can, at its end facing the drive shaft, be ring-shaped or sleeve-shaped and, by means of the ring-shaped or sleeve-shaped end, can be mounted on or fastened to the external diameter of the drive shaft or placed over the drive shaft.
  • the force transmission element can also be in operative engagement with a ring-shaped or sleeve-shaped element which is in turn mounted on or in articulated connection with the external diameter of the drive shaft or otherwise in operative engagement with the drive shaft.
  • the force transmission element can, when it is ring-shaped or sleeve-shaped at its end facing the drive shaft, be secured or fastened to the drive shaft in a radial direction by means of a feather key.
  • the force transmission element or the ring-shaped/sleeve-shaped element can optionally be secured to the drive shaft in an axial direction by means of a machine element, especially in the form of a grooved nut or some other axial securing element.
  • the ring-shaped or sleeve-shaped end of the force transmission element or the ring-shaped or sleeve-shaped element can have at least one groove extending in an axial direction, in which the device or devices for transfer of the torque engage(s).
  • said devices are, in a simple embodiment, drive pins which engage in the corresponding groove.
  • the constructional arrangement described above is a structure which does not impinge on the drive shaft, especially not on the stability of the drive shaft.
  • the drive shaft can be of solid construction, on the one hand the radius can be reduced compared to drive shafts through which a bore passes and on the other hand, as a result of the reduction in radius, a weight saving and also a smaller size of construction of a compressor according to the invention can be achieved.
  • a length compensation can be provided, which preferably is arranged in an approximately radial direction.
  • this length compensation can also be implemented, alternatively and/or additionally, by a telescopic mechanism or the like.
  • the centre of the articulation or articulated connection between the supporting element and the tilt plate preferably is, for small angles of deflection of the tilt plate, radially further away from the drive shaft central axis than is the centre of an articulation resulting from the articulated connection of the piston(s) to the tilt plate.
  • the geometry is preferably displaced so that the centre of the articulation or articulated connection of the supporting element to the tilt plate moves closer to the drive shaft central axis than the centre of the articulation produced by the articulated connection of the pistons to the tilt plate.
  • the two afore-mentioned articulation centres are radially the same distance away from the drive shaft central axis for at least one, especially for exactly one, angle of tilt, or angle of deflection, of the tilt plate.
  • the afore-mentioned structural features ensure that a compressor according to the invention has optimum kinematics.
  • the central axis of the supporting element and/or of the force transmission element forms with the drive shaft central axis, for all angles of deflection of the tilt plate, preferably an included angle which is not equal to 90°.
  • the middle angle of deflection of the tilt plate corresponds approximately to half the difference of the maximum angle at which the central axis of the supporting element and/or of the force transmission element is arranged at the tilt plate and the minimum angle at which the central axis of the supporting element and/or of the force transmission element is arranged at the tilt plate.
  • the radial spacing of the articulation between the supporting element and the force transmission element, more precisely the radial spacing of the centre of said articulation, from the drive shaft central axis is, for small angles of deflection of the tilt plate, greater than the radial spacing of the centre of the piston articulations from the drive shaft central axis.
  • the sum of the moments due to the masses moved in translation such as pistons, sliding blocks etc. and due to the masses moved in rotation (tilt plate etc.) is, preferably for all angles of deflection, especially for large angles of deflection and more especially for the maximum angle of deflection of the tilt plate, approximately constant.
  • the sum of the moments is constant at 0. This provides the desired regulation characteristic of the compressor according to the invention.
  • the supporting element has, extending in a radial direction, a recess in which the force transmission element is mounted.
  • the recess can especially have an approximately rectangular configuration or rectangular cross-section.
  • the cross-section of the recess can, in a radially outer region, become larger in a radial direction towards the outside, whereas it is approximately constant in a radially inner region of the recess.
  • those edges of the force transmission element which are located radially on the outside (end face) are arranged in the radially outer region of said recess for any angle of tilt of the tilt plate.
  • a compressor according to the invention has a housing and a drive mechanism chamber substantially defined by the housing, there being arranged between the drive mechanism chamber and the inlet gas side a fluid connection which extends at least partly through the drive shaft.
  • the fluid connection makes possible regulation of the drive mechanism chamber pressure and, accordingly, regulation of the angle of tilt, or angle of deflection, of the tilt plate.
  • the at least partial arrangement of the fluid connection in the drive shaft ensures that the compressor according to the invention has few component parts and is accordingly economical to manufacture.
  • the fluid connection comprises, in the drive shaft, at least one recess which extends approximately axially and at least one which extends approximately radially.
  • the recesses can especially be in the form of bores.
  • the force transmission element can be pressed into, or fitted by means of a press fit into, the drive shaft.
  • the drive-shaft-related end of the force transmission element has an especially semi-circular or groove-shaped or groove-like recess which is part of the fluid connection between the drive mechanism chamber and the inlet gas side.
  • the force transmission element can be centrally mounted in the drive shaft, which prevents imbalances, whereas at the same time the fluid connection between the drive mechanism chamber and in the inlet gas side, which as already mentioned hereinbefore serves for regulation of the angle of deflection of the tilt plate, can be produced in a simple manner and especially without additional component parts.
  • FIG. 1 shows, in an exploded view, a tilt plate mechanism of a preferred embodiment of a compressor according to the invention
  • FIGS. 2 a+b show the preferred embodiment according to FIG. 1 at a minimum angle of deflection of the tilt plate (a) and at a maximum angle of deflection of the tilt plate (b);
  • FIGS. 3 a+b show, in diagrammatic form, the possibilities for assembly of the tilt plate of a compressor according to the invention
  • FIGS. 4 a - c show, in a diagrammatic representation of a tilt plate mechanism according to the preferred embodiment, a tilting cycle
  • FIG. 5 shows an example of a clearance volume characteristic curve
  • FIG. 6 is an overview of the moments due to the masses moved in translation and due to the moment of deviation of the tilt plate and of the sum of the resulting moments, in each case in dependence on the angle of tilt of the tilting plate;
  • FIG. 7 shows, in a qualitative representation, the regulation characteristic curve of the preferred embodiment for a particular operating point and various speeds of rotation
  • FIGS. 8 a - e show various possibilities for securing the articulated connection of the force transmission element to the supporting element
  • FIGS. 9 a+b show, in a sectional view, a further possibility for articulated connection of the force transmission element to the supporting element
  • FIG. 10 shows, in a partial sectional view, the mechanism according to FIG. 9 ;
  • FIG. 11 shows a drive shaft with a force transmission element of a further preferred embodiment of a compressor according to the invention.
  • 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 in the cylinder block so as to be movable back and forth axially.
  • the compressor drive is provided via a belt pulley by means of a drive shaft 1 .
  • the compressor in the present case is a compressor having variable piston stroke, the piston stroke being regulated by the pressure difference defined by the pressures on the inlet gas side and in the drive mechanism chamber.
  • a tilt plate in the form of a tilt ring 2 is deflected, or tilted, from its vertical position to a greater or lesser degree. The greater the resulting angle of tilt, or angle of deflection, the greater is the piston stroke and, therefore, the higher is the pressure made available on the outlet side of the compressor.
  • the tilt plate mechanism of the preferred embodiment comprises: the drive shaft 1 ; the tilt ring 2 ; a sliding sleeve 3 , which is mounted axially on the drive shaft 1 against the action of a resilient element in the form of a ring-shaped or helical adjusting or restoring spring 4 ; and also a supporting element 5 and a force transmission element 6 .
  • the supporting element 5 is in articulated connection with the force transmission element 6 so as to be displaceable both radially and also perpendicular thereto (in a direction perpendicular to the drive shaft axis), which means that the supporting element 5 is mounted so as to be displaceable in a plane (and not just along an axis).
  • the supporting element 5 is cylindrical-pin-shaped and has a groove 7 , by means of which the supporting element 5 is in operative engagement with the force transmission element 6 .
  • that end which faces the supporting element 5 , or that end region which faces the supporting element 5 , of the force transmission element 6 is formed in the shape of a flat steel part. This means therefore that said end region of the force transmission element 6 has an approximately rectangular peripheral contour. That approximately rectangularly formed end region is in engagement with the groove 7 of the supporting element 5 .
  • the advantage of the arrangement of the force transmission element 6 and the supporting element 5 and, especially, the mounting of one thereof inside the other lies in the fact that the flat steel part does not need to be made too high; the strength and rigidity (low deformation) is provided by the width of the mounting.
  • the thickness of the force transmission element 6 increases, whereas at its end facing the drive shaft 1 it is sleeve-shaped. With the aid of the sleeve-shaped part 8 of the force transmission element 6 , the latter is mounted on and fastened to the drive shaft 1 .
  • the force transmission element 6 is formed in one piece with, and also of one and the same material as, the sleeve-shaped part 8 .
  • the force transmission element 6 and the sleeve-shaped part 8 could of course be two different component parts (even, optionally, made of different materials).
  • the force transmission element 6 , or the sleeve-shaped part 8 of the force transmission element 6 has two recesses in the form of grooves 9 .
  • the sleeve-shaped part 8 can, in the assembled state of the tilt plate mechanism, be slid underneath the spring 4 . This means therefore that the sleeve-shaped part 8 is placed over the drive shaft 1 and is fixed on the drive shaft 1 radially by means of the spring 4 . On that side of the force transmission element 6 which is remote from the spring 4 there is then placed over the drive shaft 1 the sliding sleeve 3 , which has a recess 10 corresponding to the force transmission element 6 .
  • the sliding sleeve 3 furthermore has two recesses in the form of bores 11 .
  • the force transmission element 6 and the sliding sleeve 3 are secured on the drive shaft 1 axially by means of a grooved nut 12 (see FIG. 2 ).
  • a disc spring 23 which ensures that the compressor does not start up with the angle of deflection of the tilt ring 2 being minimal.
  • end-stops in the form of end-stop discs 24 , 25 , which limit the angle of deflection of the tilt ring.
  • the end-stop disc 24 serves as an end-stop for a minimum angle of deflection
  • the end-stop disc 25 serves as an end-stop for a maximum angle of deflection of the tilt ring 2 .
  • the supporting element 5 is mounted in a cylindrical recess in the form of a bore 13 in the tilt ring 2 .
  • the bore 13 extends perpendicular to the drive shaft axis.
  • the supporting element 5 is secured in the tilt ring 2 by means of two circlips 14 .
  • the force transmission element 6 which in the present preferred embodiment is connected to the drive shaft 1 in a manner which does not allow relative rotation, can also, in other embodiments, be in rotatable operative connection therewith. It should furthermore be noted at this point that, as a result of the sleeve-shaped arrangement, or sleeve-shaped part 8 , of the force transmission element 6 , the drive shaft 1 is not penetrated by a hole and accordingly has appropriate stability.
  • the open width of the bore in the tilt ring 2 is at least very slightly larger than the corresponding extent of the force transmission element 6 .
  • the mechanism comprising the supporting element 5 and the force transmission element 6 is not intended for transferring the torque from the shaft to the tilt plate in the form of the tilt ring 2 .
  • the mounting locations between the supporting element 5 and the force transmission element 6 , between the force transmission element 6 and the drive shaft 1 and between the supporting element 5 and the tilt ring 2 are not designed for the purpose of transferring torque. Accordingly, a kind of movement transmission function does not fall on the supporting element 5 and the force transmission element 6 , this having been deliberately so decided for reasons of hysteresis, that is to say the tilting of the tilt ring 2 and the transfer of torque are functionally decoupled from one another.
  • the mechanism comprising the force transmission element 6 and the supporting element 5 basically take up the piston forces.
  • the torque is transferred from the drive shaft 1 to the tilt ring 2 by a tilt-providing articulation (implemented by drive pins 15 ) provided on the drive shaft central axis.
  • the drive pins 15 transferring the torque between the sliding sleeve 3 and the tilt ring 2 are retained, or secured, in the tilt ring by means of circlips 16 .
  • the tilt ring 2 has flattened regions 17 , which correspond to flattened regions 18 on the sliding sleeve 3 .
  • the decoupling of the torque transfer and gas force support makes it possible, in addition to the possibility of making the supporting element 5 and the force transmission element 6 of appropriately small dimensions, to achieve optimised surface contact pressure, especially between the force transmission element 6 and the supporting element 5 and between the supporting element 5 and the tilt ring 2 .
  • optimised surface contact pressure especially between the force transmission element 6 and the supporting element 5 and between the supporting element 5 and the tilt ring 2 .
  • FIGS. 2 a and b show the preferred embodiment of the compressor according to the invention again, in the assembled state, for an angle of minimum deflection ( FIG. 2 a ) and for an angle of maximum deflection ( FIG. 2 b ).
  • “V” indicates the position of the grooved articulation, that is to say the position of the articulation formed by the supporting element 5 and the force transmission element 6
  • “U” indicates the position of the piston.
  • the configuration, in accordance with the invention, of the supporting element 5 and the force transmission element 6 allows both for the radius U to correspond to the radius V and for U to be smaller than V and also for U to be larger than V.
  • the large number of degrees of freedom results in a low degree of Hertzian stress and also in a low degree of wear because no jamming occurs.
  • FIG. 3 a shows the assembly of the preferred embodiment of the compressor according to the invention. Because the diameter of the force transmission element 6 including the sleeve-shaped part 8 is larger than the bore in the tilt ring 2 , the tilt ring 2 is placed in a slanting position over the force transmission element 6 and is then moved into a position perpendicular thereto, as a result of which the force transmission element 6 is moved into the recess 13 . If, as in a further preferred embodiment of a compressor according to the invention which is not described in further detail herein, the diameter of the bore in the tilt ring is larger than the diameter of the force transmission element 6 (see FIG. 3 b in this regard), the tilt ring 2 can be placed over the force transmission element 6 in a perpendicular orientation and, by means of a sideways movement, brought into operative engagement therewith or with the supporting element 5 .
  • FIG. 4 a shows, in diagrammatic form, a tilt plate unit of a compressor according to the invention for large angles of deflection;
  • FIGS. 4 b and 4 c furthermore show details of FIG. 4 a for angles of deflection of the tilt ring 2 which differ from FIG. 4 a (medium and small angles of deflection).
  • the compressor kinematics take into account the position of the sliding blocks of the pistons by means of the centre at C and the position of the supporting element 5 at B.
  • the spacing between C and B is a snapshot view which is dependent on the angle of deflection. Large angles of deflection (see FIG.
  • the centre-point of the articulation B moves towards the drive shaft central axis a; as a result, the line B-D becomes shorter.
  • the degree of freedom required for the variation in the length of the line is obtained from the articulated connection, in accordance with the invention, of the supporting element 5 to the force transmission element 6 .
  • the line B-D is the hypotenuse of the triangle BDF.
  • the catheti D-F and F-B of the right-angled triangle likewise become shorter.
  • the line D-F is of great importance to the clearance volume, which normally should be minimised.
  • the (right-angled) triangle BCG is also of importance. If the centre-point of the articulation B moves towards the drive shaft A, the triangle BCG becomes larger (converse effect to the triangle BDF, which becomes smaller).
  • the line C-G is also of importance to the clearance volume.
  • two contrary effects occur on tilting of the tilt ring 2 , which can be advantageously used for mutual compensation, provided that the parameters are appropriately selected.
  • the supporting element 5 and/or the force transmission element 6 is/are arranged at an angle ⁇ (which is not equal to 0°) in order to produce an effect at all (triangle BDF), which acts counter to the effect due to the triangle BCG.
  • FIG. 5 shows the information relating to the clearance volume characteristic curve for an angle of the gas force support means (composed of the supporting element 5 and the force transmission element 6 ) of 9° included between the latter and a perpendicular to the drive shaft central axis.
  • the diagram of FIG. 5 is to be regarded solely as an example because other clearance volume characteristic curves may be desirable depending on the application. In principle, by appropriately selecting parameters it is possible to obtain a very different behaviour depending on the requirements of the user, although in most cases minimisation of the clearance volume is desirable.
  • FIG. 6 shows the moment distribution of the preferred embodiment of the compressor according to the invention, from which it can be seen that the sum of the moments due to the masses moved in translation and of the moments due to the moment of deviation of the tilt plate almost balances out over the entire tilt angle range of the tilting plate or tilt ring 2 . Attention should be drawn especially to the equalisation of moments for high angles of tilt between 16° and 18°.
  • This moment distribution results in a regulation characteristic curve as is shown in FIG. 7 for a particular operating point and for various speeds of rotation n. From FIG. 7 it can be seen that the regulation characteristic curve is very similar for different speeds of rotation n, which results from the optimised moment distribution of the compressor.
  • FIGS. 8 a to e finally show various possibilities for securing the supporting element 5 in the corresponding recess (bore 13 ) in the tilt ring 2 .
  • Securing the supporting element 5 in the bore 13 is necessary especially because of the centrifugal forces that come into effect.
  • securing is performed by means of two circlips 14 .
  • securing by means of a combination of one circlip 14 and a grub screw 19 which engages in a corresponding thread provided in the bore is also feasible.
  • the supporting element 5 to be secured on both sides of the bore by means of a grub screw.
  • the additional introduction of the mass of the grub screw 19 (which has a large mass compared to a circlip 14 ) can advantageously influence the inertia of mass of the tilt ring 2 . It is feasible for the major part of the bore 13 not occupied by the supporting element 5 to be plugged with the grub screw. Alternatively or additionally, stoppers at the ends of the bore are also feasible. These can be made of a material that differs from the material of the tilt ring 2 , especially of a heavier material, in order by that means to compensate the missing inertia of mass.
  • FIG. 8 b shows a further possibility for securing the supporting element 5 .
  • a through-hole through the tilt ring 2 is not provided but rather just a blind hole 20 .
  • the supporting element 5 is secured by means of a circlip 14 .
  • the supporting element 5 not to have an uninterrupted groove but rather just a kind of pocket 22 , that is to say a recess located in the central region of the supporting element.
  • a securing mechanism as such and the bore 13 can, if required, be plugged at the sides with bungs of any desired material.
  • An arrangement of such a kind is to be recommended especially when assembly in accordance with FIG. 3 b is or can be carried out.
  • the recess or pocket 22 shown in FIG. 8 d is, for example, produced by simple means using a disc milling cutter, which ensures simple manufacture.
  • FIG. 8 e finally shows a further possibility for securing the supporting element.
  • a further, threaded recess into which a grub screw 21 is introduced.
  • the grub screw projects out beyond the radially outer rim of the bore 13 and engages in a corresponding groove provided on the supporting element 5 so that the supporting element 5 is secured against slipping in the bore 13 .
  • FIGS. 9 a and 9 b show a further preferred embodiment of a tilt plate mechanism of a compressor according to the invention.
  • this mechanism comprises the tilt ring 2 and also the sliding sleeve 3 which is axially mounted on the drive shaft 1 . Details will be given hereinbelow only of those features which distinguish the mechanism according to FIGS. 9 a and 9 b from the mechanism according to FIG. 1 . It should be noted at this point that the tilt plate mechanism in FIG. 9 a is shown for a minimum angle of deflection of the tilt ring 2 , whereas FIG. 9 b shows the tilt plate mechanism at a maximum angle of deflection of the tilt ring 2 .
  • the supporting element 5 does not have a groove-shaped or pocket-shaped recess but rather an approximately rectangular recess 26 , which extends through the whole of the supporting element 5 in a radial direction.
  • the force transmission element 6 which as already mentioned hereinbefore is formed like a flat steel part at its radially outer end, engages in the recess 26 and accordingly forms the articulated connection of the force transmission element 6 with the supporting element 5 .
  • the cross-section of the recess 26 becomes larger towards the outside radially (in this respect see the cross-sections in FIGS. 9 a and 9 b ), from which it can be seen that the cross-section in said radially outer region flares in an approximately V-shape, whereas in a radially inner region it is approximately constant (in this respect see also, especially, FIGS. 9 a and 9 b ).
  • the radially outer end-face edges of the force transmission element 6 are, for all angles of tilt of the tilt ring, arranged in the radially outer region (in this respect see FIGS.
  • edges 29 project out from the region of the approximately constant recess cross-section at all angles of the tilt plate.
  • jamming of the edges 29 with the supporting element 5 is avoided at every operating point of the compressor. Friction and hysteresis in the region of the mechanism are reduced thereby, which in use results in a low degree of wear and a low degree of heat generation.
  • FIG. 11 shows a further preferred embodiment of a compressor according to the invention, wherein in this preferred embodiment the force transmission element is not part of a sleeve or not connected to a sleeve but rather is pressed into the drive shaft.
  • the force transmission element is, at its radially outer end facing the supporting element, formed in the shape of a flat steel part.
  • the force transmission element 6 is formed in a cylindrical shape, although in the region of the drive shaft, that is to say where the force transmission element is pressed into the drive shaft, said element has an approximately semi-circular or groove-like recess 30 .
  • the recess 30 in the force transmission element 6 is part of a fluid connection 31 between the drive mechanism space or drive mechanism chamber of the compressor and the inlet gas side.
  • This fluid connection serves for regulation of the pressure in the drive mechanism chamber and, accordingly, for regulation of the piston stroke.
  • the fluid connection extends through the drive shaft 1 and comprises, in addition to the recess 30 , a recess in the drive shaft, which recess extends approximately axially and is in the form of a bore 32 , and a recess which extends approximately radially and which is likewise in the form of a bore 33 . It should be noted at this point that an arrangement of such a kind is not limited to the connection of two chambers, especially the above-mentioned chambers, but that as a result thereof fluid connections between any desired chambers or volumes or regions are possible.
  • the bore 32 opens into a cylindrical recess 33 (bore).
  • An arrangement of such a kind ensures that oil is separated out well in the fluid connection between the drive mechanism chamber and the inlet gas side.
  • the oil that is present in the drive mechanism chamber, wherein oil mist lubrication takes place is spun out of the connection in the direction of the drive mechanism chamber.
  • the oil that reaches the region of the axially extending bore 32 is separated out on the wall of the bore 32 by means of the centrifugal forces and it can then flow back to the bore 33 .
  • the tilt ring 2 is made of steel and provided with a coating which minimises wear and friction between the sliding blocks of the pistons and the tilt ring 2 .
  • the tilt ring 2 can also be made of brass or bronze. The mentioned materials ensure that the requirements brought about by the constructional form are met.
  • the tilt rings 2 that are used are in fact rings whose height is much greater than in the prior art.
  • the height is desirable on the one hand in order that the gas force support means, which is composed of the supporting element 5 and the force transmission element 6 , can be mounted therein; on the other hand, the height is advantageous in order to provide the component with a sufficient inertia of mass. This is necessary in order to be able to generate a tilting moment—due to the centrifugal effect on rotation of the tilt ring 2 —which is sufficiently large to be able, to the desired extent, to compensate or over-compensate the contrarily acting tilting moments due to the mass forces of the pistons.
  • the materials steel, brass or bronze are, as mentioned, especially suitable because, by virtue of the height of the tilt ring 2 , these materials ensure sufficient strength and rigidity to be able to avoid deformation. In the case of tilt rings according to the prior art, this is frequently not ensured.
  • the density of bronze or brass may, depending on the alloy, be somewhat greater than the density of steel or that of grey cast iron (a tilt ring 2 according to the invention can of course also be made of grey cast iron).
  • the density increase, or higher density, of bronze or brass can be utilised in order to be able to compensate or over-compensate the piston masses even better.
  • the height of the tilt ring 2 results in the fact that the pistons, which in the Application being discussed herein engage around the tilt ring 2 and are mounted on the latter by means of two sliding blocks, must have a large opening in order to engage around the tilt ring 2 .
  • the pistons are made of an aluminium alloy. Because brass has similar thermal expansion to aluminium, such a combination of materials ensures reduced wear and an increased service life for a compressor according to the invention, because the play of the sliding blocks in the pistons will (when heat is generated in use) be only insubstantially increased, or not at all increased, compared to the state on assembly.
  • tilt ring 2 is made of steel
  • pistons which are likewise made of steel offer the same advantages.
  • other combinations of materials are also feasible (especially with a view to reducing the weight of a compressor according to the invention).
  • a mechanism as described hereinbefore that is to say a tilt plate mechanism which comprises a tilt ring, is suitable especially for a compressor in which R744 (CO 2 ) is used. It can of course also be used for coolants such as R134a, R152a etc. and also for coolants as are mentioned in U.S. Pat. No. 6,969,701 and WO 2006/012095 (e.g. azeotropic mixtures of tetrafluoropropene and trifluoroiodomethane). Tilting plates like those described hereinbefore, which are relatively tall in height, are frequently operated with sliding blocks providing for the articulated connection of the pistons where the spherical cap of the sliding blocks has a (very) small radius of curvature.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US12/064,074 2005-08-18 2006-05-30 Axial Piston Compressor Abandoned US20090220353A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005039199A DE102005039199A1 (de) 2005-08-18 2005-08-18 Axialkolbenverdichter
DE102005039199.0 2005-08-18
PCT/EP2006/005151 WO2007019903A1 (de) 2005-08-18 2006-05-30 Axialkolbenverdichter

Publications (1)

Publication Number Publication Date
US20090220353A1 true US20090220353A1 (en) 2009-09-03

Family

ID=36694112

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/064,074 Abandoned US20090220353A1 (en) 2005-08-18 2006-05-30 Axial Piston Compressor

Country Status (6)

Country Link
US (1) US20090220353A1 (ja)
EP (1) EP1917438A1 (ja)
JP (1) JP2009504981A (ja)
CN (1) CN101287908A (ja)
DE (1) DE102005039199A1 (ja)
WO (1) WO2007019903A1 (ja)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US20210231155A1 (en) * 2018-05-07 2021-07-29 Schaeffler Technologies AG & Co. KG Arrangement for securing at least one circlip against centrifugal force, which circlip is axially fastened on a rotor shaft of an electrical machine for positional securing, and use of an arrangement of this type

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4175915A (en) * 1978-04-27 1979-11-27 General Motors Corporation Drive shaft lug for variable displacement compressor
US4990063A (en) * 1988-04-20 1991-02-05 Honda Giken Kogyo Kabushiki Kaisha Control cylinder device in variable displacement compressor
US5259736A (en) * 1991-12-18 1993-11-09 Sanden Corporation Swash plate type compressor with swash plate hinge coupling mechanism
US5498140A (en) * 1994-03-16 1996-03-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor
US6164252A (en) * 1997-11-11 2000-12-26 Obrist Engineering Gmbh Reciprocating piston engine with a swivel disk gear
US6213733B1 (en) * 1997-03-03 2001-04-10 Luk Fahrzeug-Hydraulik Gmbh & Co., Kg Compressor for the air-conditioning system of a motor vehicle
US6302658B1 (en) * 1997-08-29 2001-10-16 Luk Fahrzeug-Haydraulik Gmbh & Co. Kg Swash plate-compressor
US6705841B2 (en) * 2002-03-01 2004-03-16 Visteon Global Technologies, Inc. Variable displacement compressor with stepped shaft
US6969701B2 (en) * 2004-04-16 2005-11-29 Honeywell International Inc. Azeotrope-like compositions of tetrafluoropropene and trifluoroiodomethane
US7021193B2 (en) * 2003-06-20 2006-04-04 Visteon Global Technologies, Inc. Variable displacement compressor hinge mechanism

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2846089B2 (ja) * 1990-09-14 1999-01-13 株式会社日立製作所 可変容量形圧縮機
JP2956193B2 (ja) * 1990-10-23 1999-10-04 株式会社豊田自動織機製作所 揺動斜板式可変容量圧縮機
JP3060671B2 (ja) * 1991-11-29 2000-07-10 株式会社豊田自動織機製作所 斜板式容量可変圧縮機
JPH06323249A (ja) * 1993-03-16 1994-11-22 Toyota Autom Loom Works Ltd 斜板式可変容量圧縮機
JP3125952B2 (ja) * 1993-04-08 2001-01-22 株式会社豊田自動織機製作所 容量可変型斜板式圧縮機
JPH10266952A (ja) * 1997-03-25 1998-10-06 Zexel Corp 可変容量型斜板式圧縮機
JP4007637B2 (ja) * 1997-03-31 2007-11-14 サンデン株式会社 可変容量圧縮機
JP2001041153A (ja) * 1999-07-23 2001-02-13 Zexel Valeo Climate Control Corp 可変容量型圧縮機
KR100318772B1 (ko) * 1999-12-16 2001-12-28 신영주 가변용량 사판식 압축기
DE20022242U1 (de) * 2000-03-03 2001-07-19 Luk Fahrzeug-Hydraulik Gmbh & Co Kg, 61352 Bad Homburg Hubkolbenmaschine
JP2003021055A (ja) * 2001-07-11 2003-01-24 Zexel Valeo Climate Control Corp 可変容量型圧縮機
JP4209691B2 (ja) * 2003-01-15 2009-01-14 カルソニックカンセイ株式会社 容量可変斜板式コンプレッサ
DE102005018102A1 (de) * 2005-04-19 2005-11-03 Zexel Valeo Compressor Europe Gmbh Axialkolbenverdichter
US20060285981A1 (en) * 2005-06-21 2006-12-21 Visteon Global Technologies, Inc. Swash ring compressor with spherical bearing

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4175915A (en) * 1978-04-27 1979-11-27 General Motors Corporation Drive shaft lug for variable displacement compressor
US4990063A (en) * 1988-04-20 1991-02-05 Honda Giken Kogyo Kabushiki Kaisha Control cylinder device in variable displacement compressor
US5259736A (en) * 1991-12-18 1993-11-09 Sanden Corporation Swash plate type compressor with swash plate hinge coupling mechanism
US5498140A (en) * 1994-03-16 1996-03-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor
US6213733B1 (en) * 1997-03-03 2001-04-10 Luk Fahrzeug-Hydraulik Gmbh & Co., Kg Compressor for the air-conditioning system of a motor vehicle
US6302658B1 (en) * 1997-08-29 2001-10-16 Luk Fahrzeug-Haydraulik Gmbh & Co. Kg Swash plate-compressor
US6164252A (en) * 1997-11-11 2000-12-26 Obrist Engineering Gmbh Reciprocating piston engine with a swivel disk gear
US6705841B2 (en) * 2002-03-01 2004-03-16 Visteon Global Technologies, Inc. Variable displacement compressor with stepped shaft
US7021193B2 (en) * 2003-06-20 2006-04-04 Visteon Global Technologies, Inc. Variable displacement compressor hinge mechanism
US6969701B2 (en) * 2004-04-16 2005-11-29 Honeywell International Inc. Azeotrope-like compositions of tetrafluoropropene and trifluoroiodomethane

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US20210231155A1 (en) * 2018-05-07 2021-07-29 Schaeffler Technologies AG & Co. KG Arrangement for securing at least one circlip against centrifugal force, which circlip is axially fastened on a rotor shaft of an electrical machine for positional securing, and use of an arrangement of this type
US11939998B2 (en) * 2018-05-07 2024-03-26 Schaeffler Technologies AG & Co. KG Arrangement for securing at least one circlip against centrifugal force, which circlip is axially fastened on a rotor shaft of an electrical machine for positional securing, and use of an arrangement of this type

Also Published As

Publication number Publication date
JP2009504981A (ja) 2009-02-05
DE102005039199A1 (de) 2007-03-08
EP1917438A1 (de) 2008-05-07
CN101287908A (zh) 2008-10-15
WO2007019903A1 (de) 2007-02-22

Similar Documents

Publication Publication Date Title
US7980167B2 (en) Axial piston compressor
EP2012010A1 (en) An axial plunger pump or motor
US6712589B2 (en) Scroll compressors
US20090110568A1 (en) Axial Piston Compressor
JPH1037850A (ja) 揺動板伝動機構を備えた往復動機械
WO2008069001A1 (ja) 揺動板式可変容量圧縮機
US20090220353A1 (en) Axial Piston Compressor
EP2236826B1 (en) Wobble plate type variable displacement compressor
US20030037636A1 (en) Rotor and rotary machine
EP1241353A2 (en) Compressor and pulley for compressor
US6923626B2 (en) Variable displacement compressor with decelerating mechanism for noise inhibition
US20020162720A1 (en) Power transmission mechanism
US20090246050A1 (en) Variable capacity compressor
EP2067994B1 (en) Tilting plate type compressor
JPH02308991A (ja) スクロール型圧縮機
US7490540B2 (en) Reciprocating compressor, in particular CO2 compressor for vehicle air-conditioning units
AU706838B2 (en) Scroll hydraulic machine
US8230773B2 (en) Axial piston compressor, in particular a compressor for the air conditioning system of a motor vehicle
EP1270943A2 (en) Vibration damping system for rotary compressor
US20070081904A1 (en) Variable displacement type compressor
JPH04279776A (ja) 可変容量圧縮機
JP2002340097A (ja) 回転体および圧縮機
JP4545035B2 (ja) シリンダブロック及び同シリンダブロックを備えたアキシャル型ピストンポンプ・モータ
US7455008B2 (en) Swash plate compressor
KR20040012840A (ko) 관절형 배열을 가진 왕복엔진 장치

Legal Events

Date Code Title Description
AS Assignment

Owner name: VALEO COMPRESSOR EUROPE GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SCHWARZKOPF, OTFRIED;REEL/FRAME:022849/0262

Effective date: 20080404

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION