EP3146208A2 - Machine à pistons axiaux - Google Patents

Machine à pistons axiaux

Info

Publication number
EP3146208A2
EP3146208A2 EP15723031.9A EP15723031A EP3146208A2 EP 3146208 A2 EP3146208 A2 EP 3146208A2 EP 15723031 A EP15723031 A EP 15723031A EP 3146208 A2 EP3146208 A2 EP 3146208A2
Authority
EP
European Patent Office
Prior art keywords
piston
machine according
piston machine
axial piston
spherical bearing
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.)
Granted
Application number
EP15723031.9A
Other languages
German (de)
English (en)
Other versions
EP3146208B1 (fr
Inventor
Gert Baitinger
Christoph Beerens
Michael Kreisig
Markus LEUTERT
Rolf Müller
Berthold Repgen
Roland Schacherer
Falk Schneider
Peter Wieske
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.)
Mahle International GmbH
Original Assignee
Mahle International 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 Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP3146208A2 publication Critical patent/EP3146208A2/fr
Application granted granted Critical
Publication of EP3146208B1 publication Critical patent/EP3146208B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F01B3/0017—Component parts, details, e.g. sealings, lubrication
    • F01B3/0023—Actuating or actuated elements
    • F01B3/0026—Actuating or actuated element bearing means or driving or driven axis bearing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0082—Details
    • F01B3/0085—Pistons
    • F01B3/0088—Piston shoe retaining means
    • 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
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • 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
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • F04B27/0882—Pistons piston shoe retaining means
    • 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
    • F04B27/1045—Cylinders
    • 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

Definitions

  • the present invention relates to an axial piston machine with a shaft which is non-rotatably connected to a swash plate, according to the preamble of claim 1.
  • the invention also relates to a heat recovery system with such axial piston machine.
  • a generic axial piston machine with a shaft which is rotatably connected to a swash plate.
  • a plurality of cylinders are arranged, in each of which built and hollow pistons are arranged translationally adjustable.
  • Each of these pistons is coupled via an associated spherical bearing and a sliding block with the swash plate, whereby a movement of the respective piston causes a drive of the swash plate and thus a driving of the shaft.
  • each inlet opening of a cylinder is swept once over a control disk with an eccentrically arranged passage opening at each revolution and thereby supplied to the respective cylinder working fluid.
  • a disadvantage of the known from the prior art axial piston machine is the relatively difficult production of the spherical bearing.
  • the present invention therefore deals with the problem of providing for an axial piston machine of the generic type an improved or at least one alternative embodiment, which is characterized in particular by an improved spherical bearing.
  • the present invention is based on the general idea, a spherical bearing of an axial piston machine no longer as usual in one piece or even in one piece, but now multi-part form and thereby significantly easier to produce.
  • the spherical bearing is part of an axial piston according to the invention, which has a shaft which is rotatably connected to a swash plate.
  • a shaft which is rotatably connected to a swash plate.
  • Each of these pistons is coupled via the said spherical bearing and at least one sliding block with the swash plate.
  • an inlet opening is associated with the cylinder, the axial piston machine additionally having a control disk with an eccentrically arranged passage opening, which sweeps over each inlet opening once each revolution of the control disk and thereby directs working medium, for example exhaust gas, into the associated cylinder.
  • working medium for example exhaust gas
  • the spherical bearing is made in two parts and has a first and a second part, these two parts each having a receptacle or a receiving tray for a sliding block.
  • the spherical bearing is made in two parts with a first and a second part, wherein the first part is connected to the piston skirt and the second part has two receptacles or two receiving shells for the sliding block.
  • the two parts of the spherical bearing, one of which forms a head of the respective piston are firmly connected to each other, for example thermally joined together, welded together, glued, soldered or caulked.
  • the second part of the spherical bearing can be formed in particular as a formed sheet metal bridge and thereby be made for example of a thick-walled sheet metal.
  • a design of the second part as a sintered part is conceivable. It is advantageous if the formed sheet metal bridge is connected to the first part of the spherical bearing by a press fit, welding, soldering and / or thermal joining.
  • At least one receptacle or receiving tray has a coating, in particular a polymer coating, a DLC coating or a polytetrafluoroethylene coating (PTFE) or is nitrided.
  • a coating in particular a polymer coating, a DLC coating or a polytetrafluoroethylene coating (PTFE) or is nitrided.
  • PTFE polytetrafluoroethylene coating
  • a receiving tray made of plastic and / or injected into an associated receptacle of the spherical bearing This can be done in particular on the counter-pressure side of the piston. Due to the design of the receiving bowl made of plastic or the injection of the same in the associated recording of the spherical bearing can turn a comparatively inexpensive, yet wear-resistant and low-friction spherical bearing can be created.
  • the recording can be measured prior to insertion of the receiving tray and thereby be paired with the associated receiving tray, which in turn is dimensioned so dimensioned that it compensates for manufacturing tolerances.
  • the spherical bearing can be adjusted to use a uniformly manufactured (same size) sliding block and the tolerance chain can be reduced down to the top dead center of the piston. Since every tolerance at the residual gas space of the piston at the top dead center towards the cylinder end means a reduction of the efficiency, the compensation of manufacturing tolerances by the described measurement and pairing of the receptacle with the receptacle is particularly advantageous.
  • the spherical bearing is firmly connected to the associated piston and has a bore parallel to the piston axis, into which the respective receiving cup can be inserted.
  • the associated receiving tray has a nipple or extension which is shaped engages conclusively in the associated bore and thereby allows a positive insertion of the receiving tray in the receptacle of the spherical bearing.
  • At least one receiving tray is biased by means of a screw or a spring, in particular by means of a disc spring, in particular from the counter-pressure side against the associated sliding block.
  • At least one sliding block made of plastic in particular of a polymer with polytetrafluoroethylene (PTFE) is formed.
  • PTFE polytetrafluoroethylene
  • a favorable possibility provides that the receptacle and the sliding block are shaped such that the sliding block is in contact with the receptacle in an annular contact area, or that the receptacle shell and the sliding block are shaped such that the sliding block contacts in an annular contact area with the receiving tray is.
  • the sliding block is of hemispherical design and if the annular contact area lies in an angular range of 30 ° to 57 ° relative to a piston axis, relative to a ball center of the sliding block.
  • the receptacle or the receiving tray has an inner contour which is formed from an inner side of a hollow ball rotating about a circular path, wherein the center of the circular path is located on a piston axis and the circular path is in a plane extending substantially perpendicular to the vertical axis.
  • the receptacle or the receiving tray can be formed such that a hemispherical sliding block is in contact with the receptacle or the receiving tray in an annular contact area.
  • At least one piston of the axial piston machine according to the invention may be designed as a built and hollow piston and have a piston skirt made of a tube, whereby the piston itself not only comparatively inexpensive, but also can be easily formed, which in particular when using the axial piston machine according to the invention in a Motor vehicle fuel can be saved.
  • the piston is usually composed of the previously described piston skirt, a piston crown and the spherical bearing, these components, for example, thermally joined together, glued together, welded or can be soldered. This non-exhaustive enumeration already gives an idea of how manifold the connection possibilities of the individual components of the piston are designed. In theory, of course, a compression of the individual parts is conceivable with each other.
  • the piston skirt is formed from a deep-drawn tube and has a closed piston crown.
  • the piston can be made more diverse and inexpensive.
  • the piston skirt is formed from a drawn tube which is formed by means of cold, warm or hot forming.
  • the piston skirt has a coating, in particular a polymer coating.
  • a coating in particular a polymer coating.
  • Layering a DLC coating (Diamond Like Carbon) or a polytetrafluoroethylene coating (PTFE) or is nitrided.
  • DLC coating Diamond Like Carbon
  • PTFE polytetrafluoroethylene coating
  • these coatings not only allow a reduction of the frictional resistance, but also an increase of the wear resistance, so that such a coating allows a smooth and at the same time low-wear guiding of the piston in the cylinder.
  • the piston skirt is crowned.
  • the piston skirt may be concave in order to counteract a possible widening of the piston by the joining of the piston skirt with the spherical bearing.
  • the piston is elliptical, i. has a non-circular outer contour, whereby a rotation of the same about its piston axis can be prevented.
  • the piston skirt has at least two sections in the axial direction, which differ by an outer diameter and / or by an inner diameter. In this way, a possible expansion of the piston can be counteracted by the joining of the piston skirt with the spherical bearing.
  • a cylinder liner can be provided, which has, for example, wear and friction-reducing surface properties, which in turn enables a particularly low-wear and smooth adjustment of the piston in the cylinder.
  • the cylinder liner has a coating, in particular a polymer coating, a DLC coating or a polytetrafluoroethylene coating (PTFE) or nitrided. These coatings not only allow a reduction in the frictional resistance, but also an increase in the wear resistance, so that such a coating enables a smooth and at the same time wear-resistant guiding of the piston in the cylinder.
  • the piston head can also be arranged in the inlet opening at least partially engaging nose, which can be generally referred to as an extension, and which is designed such that even gas, in particular gaseous working medium which is expanded, for blowing on and pressing the piston can pass through the inlet opening, however, unnecessary dead space, which negatively affects the efficiency, is filled.
  • a nose or such an extension can be made together with the piston head, that is, in particular in one piece, with this.
  • At least one spherical bearing on a vent hole which connects a piston interior with the environment.
  • an anti-rotation which prevents rotation of the piston in the cylinder.
  • the rotation can be - as described in the previous paragraphs - designed over a non-circular outer contour of the piston and a suitably designed inner contour of the cylinder, or by a groove and a pin engaging therein, wherein the pin is arranged on the spherical bearing and the groove on a housing, or vice versa.
  • the rotation can be designed by a groove and a key engaging therein, wherein the feather key on the spherical bearing and the groove is arranged on a housing, or vice versa.
  • the groove is formed by at least one guide ring arranged in the housing.
  • the guide ring may be, for example, a formed sheet metal.
  • the guide ring can be produced easily and inexpensively.
  • the guide ring is held by a latching connection in the housing.
  • the latching connection can preferably be formed by a recess in the housing, which defines a position of the guide ring on the periphery.
  • the depression can for example be introduced during casting or by machining.
  • the guide ring has a collar, with which the guide ring is clamped between two housing parts.
  • the axial piston machine according to the invention is particularly preferably used in a heat recovery system of a motor vehicle, since over half of the energy stored in the fuel is lost as waste heat and such a heat recovery system with the axial piston according to the invention can help to use the fuel more efficient and thus the degree of recovery of the motor vehicle.
  • FIG. 1 is a sectional view through an axial piston machine according to the invention
  • FIG. 2 shows a representation as in FIG. 1, but with a differently constructed spherical bearing
  • FIGS. 3-5 each show detailed representations of different spherical bearings
  • FIG. 6 shows a representation as in FIG. 1, but a smaller section and in another again designed spherical bearing
  • Fig. 8 is a detail of a recording or recording tray with a sliding block lying therein, and Fig. 9-12 each detail of different hollow piston calotte bearings.
  • an axial piston machine 1 which may be part of a heat recovery system 2 of a motor vehicle, not shown in detail, a shaft 3, which is rotatably connected to a swash plate 4.
  • a shaft 3 which is rotatably connected to a swash plate 4.
  • Each of these pistons 6 is coupled via a spherical bearing 7 and a sliding block 8 with the swash plate 4 for driving the shaft 3.
  • Each cylinder 5 is also associated with an inlet opening 9, which is each covered by a control disk 10.
  • This control disk 10 has an eccentrically arranged passage opening 1 1 and is also rotatably connected to the shaft 3. During each revolution of the control disk 10 whose passage opening 1 1 passes once each inlet opening 9 of a cylinder 5 and thereby allows access of working fluid in the associated cylinder 5. The working fluid is thereby previously collected in a plenum 12 under pressure, this plenum 12, for example is connected to a circuit of a heat recovery system 2.
  • the inlet opening 9 is arranged in a cylinder cover 13 and is aligned in exactly one rotational position of the control disk 10 with its passage opening 1 first Between the cylinder cover 13 and the control disk 10, a seal 14 is arranged, which seals the cavity 12 relative to the cylinder 5.
  • the spherical bearing 7 is now a multi-part, ie composed of at least two components, whereby its manufacturability can be significantly simplified. If, for example, the spherical bearing 7 according to FIG. 1 is considered, it can be seen that this is made in two parts, with a a first part 15 and a second part 16, wherein the two parts 15, 16 each have a receptacle 17 (see Figure 1) or a receiving tray 18 (see Figures 2 to 5).
  • the second part 16 of the spherical bearing 7 can be formed in a cost effective manner as a formed sheet metal bridge, which in particular the production of the spherical bearing 7 is cheaper and easier.
  • the spherical bearing 7, in particular the receptacles 17 and the receiving trays 18 can be easily reworked or even processed, whereby not only a higher quality, but also a simpler production is possible.
  • the second part 16, in particular the formed sheet metal bridge connected to the first part 15 of the spherical bearing 7 by a press fit, welding, soldering and / or thermal joining.
  • At least one of the receptacles 17 or the receiving shells 18 may additionally have a coating, in particular a polymer coating, a DLC coating or a polytetrafluoroethylene coating (PTFE) or else be nitrided.
  • a coating in particular a polymer coating, a DLC coating or a polytetrafluoroethylene coating (PTFE) or else be nitrided.
  • PTFE polytetrafluoroethylene coating
  • the receiving shells 18 may be formed, for example, of plastic, in particular as a plastic injection molded part, or else be injected into at least one associated receptacle 17 of the spherical bearing 7.
  • the spherical bearing 7 In principle, there are two different production methods of the spherical bearing 7, wherein in a separate receiving tray 18 in the respective part 15, 16 of the spherical bearing 7 is used. The other method, however, provides a receptacle 17 in the respective part 15, 16, wherein in addition to this recording 17 either a wear and / or friction-reducing coating or even a receiving tray 18 can be injected. Looking at Figures 2 to 5, it can be seen that the spherical bearing 7 is fixedly connected to the associated piston 6, for example caulked with this, welded or soldered, and has a parallel to the piston axis 19 bore 20 into which the respective Receiving tray 18 is inserted.
  • the respective receiving tray 18 may for example have an extension 21 or nipple, which engages in the bore 20 in a form-fitting manner.
  • the receiving tray 18 can be generally positively inserted into a corresponding recess 22 on the first or second part 15, 16 of the spherical bearing 7.
  • a screw 23 (see Figure 4) or a spring 24 (see Figure 5), in particular a plate spring, are provided which biases at least one receiving cup 18 in particular from the counter-pressure side against the associated sliding block 8.
  • the sliding block 8 itself may also be made of plastic, in particular of a polymer with polytetrafluoroethylene (PTFE), and thus be on the one hand wear-resistant and on the other hand formed friction.
  • PTFE polytetrafluoroethylene
  • At least one of the images is
  • the sliding block 8 is shaped such that the sliding block 8 is in an annular contact area 38 in contact with the receptacle 17, according to at least one of the receiving shells in a design with receiving shells 18
  • the sliding block 8 may be formed such that the sliding block 8 is in contact with the receiving tray 18 in an annular contact area 38.
  • the contact region 38 extends annularly around the piston axis 19 around. In particular, the contact region 38 extends coaxially to the piston axis 19. This reduces torques that are transmitted through the sliding block 8 via the spherical bearing 7 on the piston 6. This reduces again
  • the contact region 38 is in an angular range of 20 ° to 70 °, more preferably from 25 ° to 60 ° or even more preferably from 30 ° to 57 ° to the piston axis nineteenth
  • the angle range refers to a hemispherical sliding block 8 at an angle 42, measured at a ball center 41 of the sliding block 8, between the piston axis 19 and a connecting line 51 between the ball center 41 and the contact area 38th
  • Such a contact region 38 can be achieved, in particular, in that the receptacle 17 or the receiving shell 18 has an inner contour 43 against which the sliding block 8 rests and which is formed from an inner side of a hollow sphere 40 rotating around a circular path 39, wherein the center 44 of FIG Circular path 39 is located on a piston axis 19 and the circular path 39 is located in a plane lying substantially perpendicular to the piston axis 19.
  • the circular path 39 has a small radius 45, so that the inner contour 43 deviates only slightly from a spherical shape.
  • the radius 46 of the hollow ball 40 is slightly larger than the radius 47 of the hemisphere of the sliding block 8.
  • At least one piston 6 has a made of a tube piston skirt 25, wherein the piston 6 is composed in total of the piston skirt 25, a piston head 26 and the spherical bearing 7.
  • the individual components 25, 26 and 7 can be thermally joined together, caulked together, glued, welded or soldered.
  • the piston skirt 25 and the piston crown 26 may, for example, be formed together from a deep-drawn bowl. Thus, the piston skirt 25 and the piston crown 26 can be formed in one step. A joining of the piston skirt 25 with the piston head 26 is then not necessary. Alternatively or in addition, it can be provided that the piston skirt 25 is formed from a drawn tube, which is formed by cold, warm or hot forming.
  • the piston skirt 25 may also have a coating, in particular a polymer coating, a DLC coating or a polytetrafluoroethylene coating (PTFE) or be nitrided and thereby be made wear-resistant on the one hand and friction-resistant on the other hand.
  • a coating in particular a polymer coating, a DLC coating or a polytetrafluoroethylene coating (PTFE) or be nitrided and thereby be made wear-resistant on the one hand and friction-resistant on the other hand.
  • the piston skirt 25 is convex or convex, as shown for example in Fig. 9. As a result, in particular a jamming of the piston 6 in the cylinder 5 can be reliably avoided.
  • the piston skirt 25 may also be concave, as shown for example in FIG. As a result, a possible widening of the piston 6 by the joining of the piston skirt 25 with the spherical bearing 7 can be reduced. It can also be combined concave and convex areas, so that both jamming of the piston 6 in the cylinder 5 and a widening of the piston 6 can be avoided when joining.
  • the piston skirt 25 has at least two sections in the axial direction which differ in terms of an outer diameter and / or an inner diameter.
  • the piston skirt 25 is constructed in two parts in the axial direction and that a first part 52 and a second part 54 are connected to each other by means of thermal joining, gluing, welding or soldering.
  • Fig. 1 1 shows, for example, a piston 6 with three sections, which differ in each case by the inner diameter and / or the outer diameter.
  • the piston 6 has a non-circular outer contour and the cylinder 5 has a non-circular inner contour formed complementary thereto.
  • at least one anti-rotation 32 may be provided which prevents rotation of the piston 6 about its piston axis 19 in the cylinder 5. This is particularly advantageous if the piston 6 has no non-circular outer contour.
  • the anti-rotation 32 for example, a groove 33 and a pin engaging therein
  • an anti-rotation device 32 may be provided, which has a groove 33 and a key 48 engaging therein, wherein the key 48 is disposed on the spherical bearing 7 and the groove 33 on the housing 35, or vice versa.
  • the groove 33 is at least one in the housing
  • the guide ring 49 may be formed, for example, by a formed sheet metal.
  • the guide ring 49 is held by a latching connection 53 in the housing.
  • the guide ring 49 may have a collar 50, with which the guide ring 49 is clamped between two housing parts.
  • a cylinder liner 27 can be provided in the cylinder 5, which likewise has, for example, a corresponding coating which on the one hand increases the wear resistance and on the other reduces the friction.
  • an insertion phase 28 can be provided on the cylinder 5 or on the cylinder liner 27, which is an insertion of the piston 6 in the Cylinder 5 facilitates. This offers the great advantage that such an insertion phase does not have to be provided on the piston head 26.
  • At least one spherical bearing 7 may have a vent bore 30, which connects a piston interior 31 with the environment or at least allows pressure equalization with that of the environment outside of the piston 6.
  • the axial piston machine 1 described can be part of a heat recovery system 2 of a motor vehicle not drawn otherwise, whereby the efficiency of the motor vehicle can be significantly increased, since the energy is now at least partially usable unused in the environment drained combustion exhaust gases.
  • the housing 35 has an outlet opening 36 through which the working medium / exhaust gas can flow into an annular channel 37.
  • This annular channel 37 may surround the axial piston machine 1 at least partially annular.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne une machine à pistons axiaux (1), comprenant - un arbre (3) qui est lié solidairement en rotation à un plateau oscillant (4), - des cylindres (5) qui sont disposés annulairement autour de l'arbre (3) et coaxialement à celui-ci et dans lesquels des pistons (6) sont disposés de façon déplaçable en translation, chaque piston (6) étant accouplé au plateau oscillant (4) par le biais d'un palier sphérique (7) et d'un bloc coulissant (8), - un orifice d'entrée (9) étant associé à chaque cylindre (5), et - un disque de commande (10) pourvu d'un orifice de passage excentré (11) qui, à chaque rotation du disque de commande (10), passe une fois sur chaque orifice d'entrée (9) et qui dirige ainsi du fluide de travail dans le cylindre associé (5). L'invention est caractérisée en ce qu'au moins un palier sphérique (7) est réalisé en plusieurs parties.
EP15723031.9A 2014-05-23 2015-05-20 Machine à pistons axiaux Not-in-force EP3146208B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014209892.0A DE102014209892A1 (de) 2014-05-23 2014-05-23 Axialkolbenmaschine
PCT/EP2015/061149 WO2015177231A2 (fr) 2014-05-23 2015-05-20 Machine à pistons axiaux

Publications (2)

Publication Number Publication Date
EP3146208A2 true EP3146208A2 (fr) 2017-03-29
EP3146208B1 EP3146208B1 (fr) 2018-08-29

Family

ID=53181300

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15723031.9A Not-in-force EP3146208B1 (fr) 2014-05-23 2015-05-20 Machine à pistons axiaux

Country Status (3)

Country Link
EP (1) EP3146208B1 (fr)
DE (1) DE102014209892A1 (fr)
WO (1) WO2015177231A2 (fr)

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Publication number Priority date Publication date Assignee Title
DE102016213283A1 (de) * 2016-07-20 2018-01-25 Mahle International Gmbh Kolben für eine Axialkolbenmaschine
DE102017105610A1 (de) * 2017-03-16 2018-09-20 Volkswagen Aktiengesellschaft Axialkolbenmotor und Kreisprozessvorrichtung

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JP4539205B2 (ja) * 2003-08-21 2010-09-08 日産自動車株式会社 冷媒圧縮機
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WO2010115010A2 (fr) * 2009-04-01 2010-10-07 Purdue Research Foundation Piston de machine volumétrique doté d'une forme de surface ondulée
DE102009019627A1 (de) * 2009-04-30 2010-11-04 Linde Material Handling Gmbh Hydrostatische Verdrängermaschine
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WO2015177231A3 (fr) 2016-03-24
DE102014209892A1 (de) 2015-11-26
WO2015177231A2 (fr) 2015-11-26
EP3146208B1 (fr) 2018-08-29

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