WO2014195083A1 - Machine à plateau oscillant - Google Patents

Machine à plateau oscillant Download PDF

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Publication number
WO2014195083A1
WO2014195083A1 PCT/EP2014/059545 EP2014059545W WO2014195083A1 WO 2014195083 A1 WO2014195083 A1 WO 2014195083A1 EP 2014059545 W EP2014059545 W EP 2014059545W WO 2014195083 A1 WO2014195083 A1 WO 2014195083A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
fictitious
end portion
dome
longitudinal axis
Prior art date
Application number
PCT/EP2014/059545
Other languages
German (de)
English (en)
Inventor
Dietmar Uhlmann
Markus Nieslony
Arnold Gente
Timo Nafz
Frank Scholz
Original Assignee
Robert Bosch 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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2014195083A1 publication Critical patent/WO2014195083A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/08—Prime-movers comprising combustion engines and mechanical or fluid energy storing means
    • B60K6/12—Prime-movers comprising combustion engines and mechanical or fluid energy storing means by means of a chargeable fluidic accumulator
    • 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
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/007—Swash plate
    • 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
    • F01B3/10—Control of working-fluid admission or discharge peculiar thereto
    • F01B3/103—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block
    • F01B3/106—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block by changing the inclination of the swash plate
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

Definitions

  • the present invention relates to a swash plate machine according to the
  • Swash plate machines serve as axial piston pumps for converting mechanical energy into hydraulic energy and as axial piston motor for converting hydraulic energy into mechanical energy.
  • Cylinder drum with piston bores is rotatably or rotatably mounted and pistons are arranged in the piston bores.
  • the cylinder drum is fixedly connected to a drive shaft and to a first part of the rotating
  • Piston bores temporarily acts a hydraulic fluid under high pressure and on a second part of the rotating piston bores acts temporarily a hydraulic fluid under low pressure.
  • a pivoting cradle is around one
  • Swivel axis mounted pivotably and on the pivoting cradle are sliding shoes, which are attached to a retaining disc.
  • the pistons are attached to the sliding shoes.
  • the retaining disc with the
  • Sliding shoes performs together with the cylinder drum a rotational movement about a rotation axis and a flat bearing surface of the pivoting cradle is at an acute angle, for example between 0 ° and + 20 ° and between 0 ° and -20 ° as a pivot angle, to the axis of rotation of the
  • the pivoting cradle is by two hydraulic pivoting devices, each of which is formed by an adjusting piston and an adjusting cylinder to a Swivel axis pivots.
  • a bearing ball is attached to the adjusting piston and the bearing ball is mounted on a part-spherical bearing dome on the pivoting cradle. Between the bearing ball and the bearing dome a hydrostatically relieved slide bearing is formed.
  • On the bearing ball a production-related center hole is present on the front side, so that at the
  • Swivel cradle applied compressive forces transmitted substantially at the front end portion of the bearing ball on the bearing dome. This leads to a large mechanical wear. Because of the high
  • EP 1 013 928 A2 shows an axial piston pump in a swashplate design with a driven circumferential and a plurality of piston bores having cylinder bores, wherein in each separated by webs piston bores are arranged linearly between a bottom dead center and a top dead center pistons and a low pressure connection kidney and a Hochdruckin kidney having control disk is provided.
  • the CH 405 934 shows a Schrägusionnaxialkolbenpumpe whose non-rotating cylinder block for varying the flow rate in dependence on the delivery pressure is longitudinally displaceable, wherein at the pressed by a spring in the direction of increasing the delivery cylinder block a
  • Control slide unit is attached with a spool.
  • DE 27 33 870 C2 shows a control device for a
  • Oblique disk axial piston pump on each side of the cradle for pivoting the swash plate, each a hydraulically acted upon
  • Swinging wing engages the engine, wherein both motors are controllable by means of a pivotable about the pivot axis of the cradle arranged plate-shaped control valve spool and for adjusting the delivery of the
  • Swash plate machine as axial piston pump and / or axial piston motor, comprising one rotatable about an axis of rotation or
  • Bearing head and / or the at least one bearing dome are designed to the effect that the bearing of the at least one bearing head on the at least one bearing dome outside the fictitious front end portion of the at least one bearing head and / or outside the fictitious rear end portion of at least one bearing dome is executed, in particular a pivot angle of the pivoting cradle, wherein the support surface of the pivoting cradle is aligned perpendicular to the axis of rotation of the drive shaft.
  • the at least one bearing head is outside the front end portion of the at least one bearing dome outside the fictitious rear
  • Bearing head and the at least one bearing dome thus has a large area, so that thereby a low surface pressure between the at least one bearing head and the at least one bearing dome occurs.
  • the low surface pressures lead to a low mechanical wear between the at least one bearing head and the at least one Lagerkalot, so that thereby a long life of
  • Swash plate machine is ensured and also advantageously can be dispensed with a hydrostatic relief of the sliding bearing between the at least one bearing head and the at least one bearing dome.
  • the at least one bearing head and / or the at least one bearing dome has a shape deviating from one, in particular only one, part ball.
  • the at least one bearing head is perpendicular to a longitudinal axis of the at least one of a fictitious plane
  • Bearing head divided into the fictitious front end portion and a fictitious rear end portion and the fictitious front end portion in the extension in the direction of the longitudinal axis comprises less than 70%, 50%, 40%, 30%, 20%, 10% or 5% of the total extent the at least one bearing head in the direction of the longitudinal axis and preferably the fictitious front end portion in the extension in the direction of the longitudinal axis more than 2%, 3%, 5%, 10%, 20% or 30% of the total extent of the at least one bearing head in
  • the at least one bearing dome is subdivided from a fictitious plane perpendicular to a longitudinal axis of the at least one bearing dome into a fictitious front end section and into the fictitious rear end section and the fictitious rear end section in the extension in the direction of the longitudinal axis comprises less than 70%. , 50%, 40% or 30% of
  • Longitudinal axis and preferably includes the fictitious rear end portion in the extension in the direction of the longitudinal axis more than 5%, 10%, 20% or 30% of the total extent of the at least one bearing dome in the direction of
  • the longitudinal axis of the at least one bearing head in an arrangement of the at least one bearing head on the pivoting device corresponds to the direction of movement of the pivoting device, in particular a longitudinal axis of an adjusting cylinder with an adjusting piston and / or the longitudinal axis of the at least one bearing dome in an arrangement the at least one bearing dome on the pivoting of the
  • Direction of movement of the pivoting device corresponds, in particular a longitudinal axis of an adjusting cylinder with an adjusting piston.
  • Arrangement of the bearing dome on the pivoting device thus corresponds to the direction of movement of the pivoting device of the longitudinal axis of the bearing dome and in an arrangement of the bearing head on the pivoting device corresponds to the longitudinal axis of the bearing head of the direction of movement
  • the longitudinal axis of at least one bearing dome or the at least one bearing head and / or the longitudinal axis of the at least one bearing head substantially one Symmetryeachse the at least one bearing head corresponds and / or the longitudinal axis of the at least one bearing dome substantially corresponds to an axis of symmetry of the at least one bearing dome.
  • a pivot angle of 0 ° of the pivoting cradle corresponds to the longitudinal axis of the bearing dome on the pivoting cradle of the longitudinal axis of the bearing head on the pivoting device or vice versa.
  • At least one bearing dome exclusively outside the fictitious front end portion of the at least one bearing head and / or exclusively outside the fictitious rear end portion of the at least one
  • Pivoting cradle in which the bearing surface of the pivoting cradle is aligned perpendicular to the axis of rotation of the drive shaft.
  • Bearing head on the at least one bearing dome in particular exclusively, on the fictitious rear end portion of the at least one bearing head and / or, in particular exclusively, executed on the fictitious front end portion of the at least one bearing dome, in particular at a pivot angle of the pivoting cradle, wherein the bearing surface of the pivoting cradle is aligned perpendicular to the axis of rotation of the drive shaft.
  • Bearing head is at the fictitious rear end section to the fictitious front End section of at least one bearing dome mounted, ie the at least one bearing head is in contact or there is a sliding bearing between the fictitious rear end portion of the bearing head and the fictitious front end portion of at least one bearing dome.
  • a large plain bearing area ie, a large surface area between the bearing head and the bearing dome is present on which both lie on top of each other, so that thereby low surface pressures between the bearing head and the bearing dome occur and this also in manufacturing inaccuracies on the bearing head and the bearing dome ,
  • At least one bearing head partially spherical, in particular with two fictitious partial spheres with a different center, formed.
  • the fictitious rear end portion of the at least one bearing dome is partially spherical, in particular with two fictitious partial spheres having a different center.
  • the radius of the at least one fictitious partial sphere of the at least one bearing dome on the fictitious rear end section is greater than the radius of the at least one fictitious partial sphere of the at least one bearing head on the fictitious front end section.
  • the fictitious front end portion of the at least one bearing head is partially formed as at least one ellipsoid of revolution and / or the fictitious rear end portion of the at least one
  • Lagerkalot is partially formed as at least one ellipsoid of revolution and / or the at least one bearing dome is on the pivoting cradle and the at least one bearing head formed on the at least one pivoting device or vice versa.
  • the pivot axis of the pivoting cradle is aligned perpendicular to the axis of rotation of the drive shaft and the cylinder drum.
  • Inventive drive train for a motor vehicle comprising at least one swash plate machine for converting mechanical energy into hydraulic energy and vice versa, at least one pressure accumulator, wherein the swash plate machine as one in this patent application
  • the drive train comprises two swash plate machines, which are hydraulically connected to each other and act as a hydraulic transmission and / or the drive train comprises two pressure accumulator as
  • the swash plate machine comprises a weighing storage for the pivoting cradle.
  • the swash plate machine comprises a low-pressure opening for introducing and / or discharging hydraulic fluid into and / or out of the rotating piston bores.
  • the swash plate machine includes a high pressure port for discharging and / or introducing hydraulic fluid from and / or into the rotating piston bores.
  • the swashplate machine comprises a drive shaft which is connected at least in a rotationally fixed manner to the cylinder drum and which is mounted rotatably or rotatably about the rotation axis.
  • 1 is a longitudinal section of a swash plate machine
  • Fig. 2 shows a cross section A-A of FIG. 1 a valve disc of
  • Fig. 4 is a longitudinal section of the bearing dome with a bearing head of
  • Fig. 5 shows a longitudinal section of the bearing dome with the bearing head of
  • Fig. 6 is a longitudinal section of the bearing dome with a bearing head of
  • Fig. 8 is a partial longitudinal section of the swash plate machine in a further embodiment
  • a swashplate machine 1 shown in a longitudinal section in FIG. 1 serves as axial piston pump 2 for conversion or conversion of mechanical energy (torque, speed) into hydraulic energy (volume flow, pressure) or as axial piston motor 3 for conversion or conversion of hydraulic energy (volume flow, pressure ) into mechanical energy (torque,
  • a drive shaft 9 is by means of a bearing 10 at a
  • Cylinder drum 5 rotatably and connected in the axial direction
  • Drive shaft 9 and the cylinder drum 5 are formed in one or two parts and the boundary between the drive shaft 9 and the cylinder drum 5 is shown in Fig. 1 by dashed lines.
  • the cylinder drum 5 performs the rotational movement of the
  • Cylinder drum 5 a plurality of piston bores 6 with an arbitrary cross-section, for example square or circular, incorporated.
  • the longitudinal axes of the piston bores 6 are substantially parallel to the axis of rotation 8 of the drive shaft 9 or the cylinder drum 5
  • a pivoting cradle 14 is mounted pivotably about a pivot axis 15 on the housing 4. The pivot axis 15 is perpendicular to the
  • the axis of rotation 8 of the cylinder drum 5 is arranged parallel to and in the plane of the drawing of FIG. 1 and perpendicular to the plane of the drawing of FIG. 2.
  • the housing 4 fluid-tightly defines an interior space 44 which is filled with hydraulic fluid.
  • the pivoting cradle 14 has a flat or planar bearing surface 18 for the indirect support of a retaining disk 37.
  • the retaining disc 37 has holes and within the holes sliding shoes 39 are arranged.
  • the sliding shoes 39 lie directly on the support surface 18.
  • the retaining disc 37 is thus connected to a plurality of sliding shoes 39 and each shoe 39 is connected to a respective piston 7.
  • the sliding shoe 39 has a bearing ball 40 (FIG. 1), which is fixed in a bearing cup 59 on the piston 7, so that a piston joint 22 between the bearing ball 40 and the bearing cup 59 is formed on the piston 7.
  • Bearing ball 40 and bearing cup 59 are both complementary or spherical, so characterized in a corresponding possibility of movement between the bearing ball 40 and the bearing cup 59 on the piston 7, a permanent connection between the piston 7 and the shoe 39 is present.
  • the retaining plate 37 has bores (not shown), within which a sliding shoe 39 is arranged in each case.
  • the sliding blocks 39 are directly on the support surface 18 and are radially within the
  • Support surface 18 of the pivoting cradle 14 is, the retaining disc 37 is pressed by a compression spring 41 under a compressive force in the direction of the support surface 18 and thus also the sliding shoes 39 on the support surface 18th
  • the pivoting cradle 14 is - as already mentioned - pivotally mounted about the pivot axis 15 and further comprises an opening 42 (Fig. 1) for
  • a weighing storage 20 is formed on the housing 4.
  • 14 two bearing sections are formed on the pivoting cradle.
  • the two bearing sections of the pivoting cradle 14 rest on the weighing support 20.
  • the pivoting cradle 14 is thus by means of a
  • Swivel axis 15 pivotally mounted.
  • the support surface 18 according to the sectional formation in Fig. 1 has a pivot angle ⁇ of approximately + 20 °.
  • the pivot angle ⁇ is present between a fictitious plane perpendicular to the axis of rotation 8 and a plane spanned by the flat bearing surface 18 of the pivoting cradle 14 according to the
  • the pivoting cradle 14 can between two pivotal limit angle ⁇ between + 20 ° and -20 ° by means of two
  • Swivel devices 24 are pivoted. At a swivel angle ⁇ of 0 °, the support surface 18 is aligned perpendicular to the axis of rotation 8 of the drive shaft 9.
  • the first and second pivoting means 25, 26 as pivoting means 24 has a connection point 32 between the pivoting device 24 and the
  • the two pivoting devices 24 each have an adjusting piston 29, which is movably mounted in an adjusting cylinder 30.
  • the adjusting piston 29 or an axis of the adjusting cylinder 30 is aligned substantially parallel to the axis of rotation 8 of the cylinder drum 5.
  • Adjusting piston 29 this has a bearing head 19, in which a
  • Bearing cam 31 is mounted.
  • the bearing cap 31 on a pivot arm 16 (Fig. 1 to 2) of the pivoting cradle 14 is present.
  • Pivoting device 25, 26 is thus connected to a respective bearing head 19 on a respective pivot arm 16 with the pivoting cradle 14.
  • the pivoting cradle 14 can be pivoted about the pivot axis 15, as a result Adjustment piston 29 to the open valve 27, 28 with a hydraulic fluid under pressure in the adjusting cylinder 30, a force is applied.
  • this pivotal movement of the pivoting cradle 14 from.
  • a valve disk 1 1 is located on the end of the cylinder drum 5 shown on the right in FIG. 1, with a kidney-shaped high-pressure opening 12 and a kidney-shaped
  • the piston bores 6 of the rotating cylinder drum 5 are thus fluidly connected in an arrangement on the high-pressure opening 12 with the high-pressure opening 12 and in an arrangement on the
  • Low-pressure port 13 fluidly connected to the low pressure port 13. At a swivel angle ⁇ of 0 ° and during operation of the
  • Swash plate machine 1 for example, as axial piston 2, despite a rotational movement of the drive shaft 9 and the cylinder drum 5 no hydraulic fluid conveyed by the axial piston pump 2, since the piston 7 perform no strokes in the piston bores 6.
  • swash plate machine 1 both as axial piston 2 and as
  • Axialkolbenmotor 3 have the temporarily in fluid-conducting connection with the
  • An axial end 66 of the cylinder drum 5 rests on the valve disc 1 1.
  • Opening 63 formed with the bearing 10 and a second side 65 has a recess for supporting the drive shaft 9 with a further storage 10.
  • Swivel cradle 14 is formed by a sliding bearing by a
  • Position head 19 is mounted with a convex surface on a bearing cap 31 with a concave surface.
  • the bearing dome 31 is at the
  • FIGS. 3 to 5 show a first exemplary embodiment of the connection point 32 between the adjusting piston 29 and the pivoting cradle 14.
  • the pivot angle ⁇ of the pivoting cradle 14 is 0 ° and in Fig. 5, the pivot angle ⁇ of the pivoting cradle 14 is approximately 20 °.
  • Bearing head 19 is formed as a part ball with the radius R 2 ' and the center M 3 ' and fixedly connected to the adjusting piston 29.
  • a longitudinal axis 35 of the bearing head 19 corresponds to an axis of symmetry of the bearing head 19 and further corresponds to the longitudinal axis 35 and a longitudinal axis of the adjusting piston 29 and also a longitudinal axis or direction of movement of the adjusting piston 29 within the adjusting cylinder 30.
  • a fictitious plane 38 is perpendicular to the longitudinal axis 35 of Lagerkopfes 19 aligned and divides the bearing head 19 in a fictitious front end portion 17 and in a fictitious rear
  • the bearing head 19 Coaxial and concentric with the longitudinal axis 35, the bearing head 19 also has a center hole 43 on soft production reasons.
  • the centering hole 43 has an outer diameter D 3 and an inner diameter D 4 . It is by means of one in the sectional formation in Fig. 4th as the radius r s shown partial sphere is a continuous transition between the
  • a longitudinal axis 36 of the bearing cap 31 is identical to the pivoting angle ⁇ of 0 ° of the pivoting cradle 14 to the longitudinal axis 35 of the bearing head 19th
  • a notional plane 62 is oriented perpendicular to the longitudinal axis 36 of the bearing cap 31 and divides the bearing cap 31 into a fictitious front
  • the bearing dome 31 has at the fictitious front
  • Lagerkalotte 31 formed by two sub-balls and the two sub-balls have the centers Mi ' and M 2 ' on.
  • the radius of the two partial spheres with the centers Mi ' and M 2 ' is identical and is R-1 ' .
  • Bearing cup 31 are separated from a plane perpendicular to the
  • Endabiteses 34 of the bearing 31 in the direction of the longitudinal axis 36 of the bearing 31 is about 30% of the total extent c
  • Bearing cup 31 in the direction of the longitudinal axis 36 of FIG. 4. Between the bearing head 19 and the bearing cap 31 is only one
  • Longitudinal axis 36 of the bearing cap 31 is identical only at a pivot angle ⁇ of the pivoting cradle 14 of 0 ° as shown in FIG.
  • ⁇ pivot angle
  • Fig. 4 is thus left of the fictitious levels 38, 62 no contact between the bearing cap 31 and the bearing head 19 and only to the right of the levels 38, 62 is on the sliding bearing portion 61, a contact between the bearing head 19 and the bearing cup 31, however not at the insertion cone 68 of the bearing cup 31.
  • the fictitious plane 38 and the fictitious plane 62 are not identical planes 38, 62, as well as the longitudinal axes 36 and 35 fall apart. As shown in FIG. 5, there is no contact of the bearing head 19 with the bearing cup 31 to the left of the fictitious plane 38 of the bearing head 19 and, according to the representation in FIG. 5, there is no contact between the left side of the imaginary plane 62
  • bearing cup 31 and the bearing head 19 In the illustrated in Fig. 3 to 5 the first embodiment of the joint 32, the bearing head 19 partially the shape of only a partial sphere on, d. H. the bearing head 19 is formed in the embodiment shown in Fig. 3 to 5 as a bearing ball 19 or as a bearing part ball 19.
  • the extent d of the front end portion 17 of the bearing head 19 is approximately 20% of the total extent f of the bearing head 19 respectively in the direction of the longitudinal axis 35 of the bearing head 19 and the extension e of the rear end portion 23 of the bearing head 19 in the direction of the longitudinal axis 35 corresponds to approximately 80% of Total expansion f of the bearing head 19 in the direction of the longitudinal axis 35 at a pivot angle of 0 ° in FIG. 5.
  • Fig. 5 result in the swing angle of 20 ° other% values.
  • FIGS. 6 and 7 show a second exemplary embodiment of the connection point 32. In the following, only the differences from the first exemplary embodiment according to FIGS. 3 to 5 will be described essentially.
  • the geometry of the bearing cap 31 corresponds to only one part ball and the bearing cap 31 is formed by a partial sphere with the center M- ⁇ and the radius Ri.
  • the bearing head 19 is formed by two partial spheres with the radii R 2 and the
  • the two radii R 2 of the bearing head 19 are smaller than the radius Ri of the bearing cam 31.
  • the bearing dome 31 is thus formed by only one part ball with the radius Ri and the only one center M- ⁇ and the bearing head 19 of two sub-balls with the centers M 2 and M 3 each with the radii R 2nd
  • the two sub-balls of the bearing head 19 are by a fictitious plane perpendicular to the plane of Fig. 6 and through the Longitudinal axis 35 separated from each other.
  • a sliding bearing region 61 between the bearing head 19 and the bearing cap 31 also forms in the second exemplary embodiment of the connection point 32, so that, for example, at the pivoting angle ⁇ of 0 ° shown in FIG. 6, the pivoting cradle 14 is left of the imaginary planes 38, 62 no contact between the bearing head 19 and the
  • FIG. 8 shows a further partial longitudinal section of the swashplate machine 1.
  • the pivoting cradle 14 has a pivot angle ⁇ of 0 °, d. H. one of the support surface 18 spanned fictitious plane is perpendicular to the axis of rotation 8 of the drive shaft 9.
  • the longitudinal axes 35, 36 are not aligned parallel to the axis of rotation 8, but in an acute
  • FIG. 9 shows a drive train 45 according to the invention.
  • Drive train 45 has an internal combustion engine 46, which drives a planetary gear 48 by means of a shaft 47.
  • Planetary gear 48 two shafts 47 are driven, wherein a first shaft 47 is connected to a clutch 49 with a differential gear 56.
  • a second or other shaft driven by the planetary gear 48 drives a first swash plate machine 50 through a clutch 49, and the first swash plate machine 50 is hydraulically connected by means of two hydraulic lines 52 to a second swash plate machine 51.
  • the first and second swash plate machines 50, 51 thereby form a hydraulic gear 60, and from the second swash plate machine 51, the differential gear 56 can also be driven by means of a shaft 47.
  • Differential gear 56 drives the wheels 57 with the wheel shafts 58.
  • the drive train 45 has two pressure accumulators 53 as a high-pressure accumulator 54 and as a low-pressure accumulator 55.
  • the two accumulators 53 are hydraulically connected by means not shown hydraulic lines with the two swash plate machines 50, 51, so that mechanical energy of the engine 46 in the high-pressure accumulator 54 can be hydraulically stored and also in a recuperation of a motor vehicle
  • the drive train 45 also kinetic energy of the motor vehicle in the high-pressure accumulator 54 can be hydraulically stored.
  • the differential gear 56 can additionally be driven with a swash plate machine 50, 51.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Reciprocating Pumps (AREA)

Abstract

La présente invention concerne une machine à plateau oscillant (1), configurée en pompe à piston axial (2) et/ou en moteur à piston axial (3), qui comporte un tambour cylindrique (5) monté à rotation ou de façon à pouvoir tourner sur un axe de rotation (8) et pourvu d'alésages de piston (6), des pistons (7) montés de manière mobile dans les alésages de piston (6), un berceau pivotant (14) monté à pivotement sur un axe de pivotement (15), au moins un dispositif de pivotement (24) destiné à faire pivoter le berceau pivotant (14), au moins un point de raccordement (32) destiné à relier le ou les dispositifs de pivotement (24) au berceau pivotant (14) qui possèdent chacun un coussinet sphérique (31) pourvu d'une surface concave et une tête de palier (19) pourvue d'une surface convexe. Chacune des têtes de palier (19) est montée dans un coussinet sphérique (31). La ou les têtes de palier (19) comportent une portion d'extrémité avant fictive et le ou les coussinets sphériques (31) comportent une portion d'extrémité arrière fictive. La géométrie de la ou des têtes de palier (19) et/ou celle du ou des coussinets sphériques (31) sont configurées de telle sorte ce que le montage de la ou les têtes de palier (19) sur le ou les coussinets sphériques (31) s'effectue à l'extérieur de la portion d'extrémité avant fictive de la ou des têtes de palier (19) et/ou à l'extérieur de la portion d'extrémité arrière fictive du ou des coussinets sphériques (31), en particulier avec un angle de pivotement du berceau pivotant (14) pour lequel la surface d'appui (18) du berceau pivotant (14) est orientée perpendiculairement à l'axe de rotation (8) de l'arbre d'entraînement (9).
PCT/EP2014/059545 2013-06-05 2014-05-09 Machine à plateau oscillant WO2014195083A1 (fr)

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DE102019205142A1 (de) * 2019-04-10 2020-10-15 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine mit Durchtrieb

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US4142452A (en) * 1976-05-10 1979-03-06 Linde Aktiengesellschaft Axial-piston machine with inclinable control surface
US20030097927A1 (en) * 2001-11-28 2003-05-29 Nick Boone Extended male slipper servo pad arrangement for positioning swashplate and method assembling same
DE102007022568A1 (de) * 2007-05-14 2008-11-20 Robert Bosch Gmbh Niederhaltesegment
DE102011002967A1 (de) * 2011-01-21 2012-07-26 Robert Bosch Gmbh Hybridantrieb für ein Kraftfahrzeug

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CH405934A (de) 1962-07-26 1966-01-15 Weatherhead Co Schrägscheiben-Axialkolbenpumpe
US4076459A (en) 1976-09-14 1978-02-28 Abex Corporation Horsepower limiter control for a variable displacement pump
EP1013928A3 (fr) 1998-12-22 2000-11-08 Parker Hannifin GmbH Pompe à pistons axiaux à plateau en biais avec disposif d'amortissement de pulsation

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Publication number Priority date Publication date Assignee Title
US4142452A (en) * 1976-05-10 1979-03-06 Linde Aktiengesellschaft Axial-piston machine with inclinable control surface
US20030097927A1 (en) * 2001-11-28 2003-05-29 Nick Boone Extended male slipper servo pad arrangement for positioning swashplate and method assembling same
DE102007022568A1 (de) * 2007-05-14 2008-11-20 Robert Bosch Gmbh Niederhaltesegment
DE102011002967A1 (de) * 2011-01-21 2012-07-26 Robert Bosch Gmbh Hybridantrieb für ein Kraftfahrzeug

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