WO2015197403A1 - Machine à plateau oscillant - Google Patents

Machine à plateau oscillant Download PDF

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Publication number
WO2015197403A1
WO2015197403A1 PCT/EP2015/063313 EP2015063313W WO2015197403A1 WO 2015197403 A1 WO2015197403 A1 WO 2015197403A1 EP 2015063313 W EP2015063313 W EP 2015063313W WO 2015197403 A1 WO2015197403 A1 WO 2015197403A1
Authority
WO
WIPO (PCT)
Prior art keywords
swash plate
shaft seal
plate machine
seal
shaft
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.)
Ceased
Application number
PCT/EP2015/063313
Other languages
German (de)
English (en)
Inventor
Matthias Greiner
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.)
Robert Bosch GmbH
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 WO2015197403A1 publication Critical patent/WO2015197403A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • 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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication 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
    • 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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—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
    • 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
    • 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
    • F04B1/22—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 having two or more sets of cylinders or pistons
    • F04B1/24—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 having two or more sets of cylinders or pistons inclined to the main shaft axis

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 is on a retaining disc with sliding shoes.
  • 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 an axis of rotation and a flat bearing surface of the pivoting cradle is at an acute angle to
  • the sliding blocks are mounted with a sliding bearing, which is generally hydrostatically relieved, on the support surface of the pivoting cradle and the sliding blocks are connected to the retaining disc.
  • the drive shaft is guided through an opening on the housing to the outside, so as to the drive shaft from outside the housing of the
  • Swash plate machine to apply a torque or to apply by means of the drive shaft to other parts of a torque can.
  • the interior which is bounded by a housing, is filled with hydraulic fluid under low pressure, since the interior is in fluid communication with a low-pressure opening of the swash plate machine.
  • the drive shaft is sealed with a shaft seal at the opening of the housing, so that from the interior with the hydraulic fluid no hydraulic fluid can flow into the environment due to the passage of the drive shaft through the opening on the housing.
  • the shaft seal is as one
  • Motor vehicle and a swash plate machine as a hydraulic motor also to drive the motor vehicle occur due to the fluid-conducting connection between the interior of the swash plate machine and the low-pressure opening in the interior of different pressures in the range between 2 and 17 bar.
  • EP 1 013 928 A2 shows an axial piston pump in swash plate construction with a driven circumferential and a plurality of arranged therein Cylinder drum having piston bores, in which movable pistons are arranged linearly between a bottom dead center and a top dead center in each of the piston bores separated by webs, and a low-pressure connection kidney and a control disk having high-pressure connection kidneys are 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
  • Swing wing acts on the engine, both motors are controllable by means of a pivotable about the pivot axis of the cradle arranged plate-shaped control valve spool and serve to adjust the flow rate of the pump.
  • Axial piston engine comprising one rotatable about an axis of rotation or
  • Piston bores movably mounted pistons a drive shaft at least rotatably connected to the cylinder drum, which is rotatably mounted about the axis of rotation, pivotally mounted about a pivot axis mounted pivoting cradle with a support surface for supporting the piston on the support surface, a housing having a hydraulic fluid Filled interior limited, with an opening for the passage of the drive shaft and a arranged on the drive shaft shaft seal to the passing through the housing drive shaft and thus the interior with respect to the
  • the swash plate machine a first Shaft seal and a second shaft seal comprises and between the first and second shaft seal, a gap is formed and by means of a return means entering the intermediate space leakage fluid in the interior and / or in a low-pressure opening is returned.
  • Swash plate machine has two shaft seals, namely a first
  • Return means are returned to the interior and / or to the low pressure opening of the swash plate machine. This occurs at the
  • Hydraulic fluid is present, so that at the second
  • the Shaft seal penetrates only a very small amount of leakage in the environment to the outside. Due to the large amount of leakage liquid per unit of time at the first shaft seal, this is hydrostatically relieved, so that advantageously a low friction occurs at the first shaft seal.
  • the arrangement of the gap between the first and second shaft seals means a fluid-conducting connection for the leakage fluid from the intermediate space to the first and second
  • Shaft seal and may also mean a spatial arrangement of the intermediate space between the first and second shaft seal, so that the gap also not spatially between the first and second
  • Shaft seal may be arranged, but with a fluid-conducting connection between the intermediate space and the first and second shaft seal.
  • the return means is formed by a channel, which in fluid-conducting connection with the low-pressure opening of
  • Swash plate machine and / or with the interior is and preferably is the low-pressure opening in fluid communication with the interior.
  • the channel formed for example by a hose and / or a housing bore, makes it possible to return the leakage fluid in the space back into the interior of the swash plate machine and / or to the low-pressure opening, thereby characterized exiting the first shaft seal leakage fluid back to the interior of the
  • the swash plate machine comprises the low-pressure opening for introducing and / or discharging hydraulic fluid into and / or out of the rotating piston bores and a high-pressure opening for discharging and / or introducing hydraulic fluid out of and / or into the rotating piston bores.
  • Hydraulic fluid in the interior and / or at the low-pressure opening so that due to the pressure difference between the intermediate space and the interior and / or the low-pressure opening, the leakage fluid from the intermediate space in the interior and / or in the low-pressure opening is conveyed.
  • the return means comprises a
  • Feed pump for conveying the leakage fluid from the intermediate space to the interior and / or to the low-pressure opening.
  • the first shaft seal is designed such that at the first shaft seal with respect to
  • Hydraulic fluid or leakage fluid a pressure drop of at least 0.5 bar, 1 bar or 2 bar between the interior and the space occurs.
  • first shaft seal is designed as a sliding direction and / or the second shaft seal is designed as a radial shaft sealing ring.
  • the intermediate space between the first shaft seal and the second shaft seal is formed in the axial direction between the first and second shaft seal.
  • the mechanical seal as the first shaft seal comprises a fixed sliding ring and a rotating counter ring and the sliding ring rests on the counter ring, so that between the sliding ring and the counter ring, a first sealing surface is formed and the first
  • Sealing surface is preferably aligned in a radial direction.
  • the swash plate machine in particular the arrangement of the intermediate space and / or the second shaft seal, is designed such that the leakage fluid flows on the first sealing surface in a radial direction to the drive shaft and into the intermediate space.
  • the sliding ring is pressed with an elastic element, in particular a compression spring, on the counter ring, so that lie on the first sealing surface of the sliding ring and the mating ring by means of a force caused by the elastic element force with a surface pressure on each other.
  • an elastic element in particular a compression spring
  • the surface pressure between the counter ring and the sliding ring is increased.
  • the elastic element brings thereby a small force on the slip ring, so that thereby a small friction power between the Sliding ring and / or the mating ring occurs. Deviating from this, the force can also be applied to the mating ring by means of the elastic element.
  • Mating ring a small friction power, preferably less than 0.5 or 1 kW at a speed of the drive shaft of 5000 rev / min, because on the first shaft seal, a large volume flow of leakage fluid occurs. Due to the low friction power, the swash plate machine thus has a high efficiency. Due to the large volume flow
  • the first shaft seal is heavily hydrostatically relieved, so that thereby a small friction loss occurs at the first shaft seal.
  • a second sealing surface on the second shaft seal between a radial outer side of the drive shaft and the second shaft seal, because the second shaft seal directly or indirectly rests on the radial outer side of the drive shaft and / or a first attachment means for the first shaft seal is at least one pre-secondary seal sealed and / or a second attachment means for the second shaft seal is sealed with at least one post-secondary seal.
  • 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 at least one
  • Swivel device for pivoting the swivel cradle.
  • 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. 3 is a partial longitudinal section of the swash plate machine of FIG. 3 in the region of a shaft seal and storage for a drive shaft and
  • FIG. 4 shows a drive train for a motor vehicle.
  • 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 carries out the rotational movement of the drive shaft 9 with due to a rotationally fixed connection.
  • 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 is liquid-tightly bounded by an interior space 44 which is filled with hydraulic fluid.
  • the pivoting cradle 14 has a flat or planar support surface 18 for the indirect support of a retaining disk 37 and for the direct support of sliding shoes 39.
  • the retaining disc 37 is provided with a plurality of sliding shoes 39 and each sliding block 39 is connected to a respective piston 7.
  • the sliding block 39 has a bearing ball 40 (FIG. 1), which is fastened in a bearing socket 59 on the piston 7, so that a piston connection point 22 between the bearing ball 40 and the bearing socket 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 to the piston 7, a permanent connection between the piston 7 and the shoe 39 is present. Due to the connection of the piston 7 with the rotating cylinder drum 5 and the connection of the bearing cups 59 with the
  • Sliding shoes 39 perform the sliding blocks 39 a rotational movement about the rotation axis 8 with and due to the fixed connection or arrangement of the sliding shoes 39 on the retaining disc 37 also performs the retaining disc
  • 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 lie on the
  • 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.
  • the first and second pivoting means 25, 26 as pivoting means 24 has a connection point 32 between the pivoting device 24 and the pivoting cradle 14.
  • 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 has this a bearing cup 31, in which a
  • Bearing ball 19 is mounted.
  • Pivoting device 25, 26 is thus connected to a respective pivot ball 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 this is applied to the adjusting piston 29 at the open valve 27, 28 with a hydraulic fluid under pressure in the adjusting cylinder 30, a force. Not only does the pivoting cradle 14, but also the retaining disc 37 due to the pressurization with the
  • Compression spring 41 this pivotal movement of the pivoting cradle 14 with.
  • 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 pump 2, despite a rotational movement of the drive shaft 9 and the cylinder drum 5, no hydraulic fluid from the axial piston pump 2 promoted because the piston 7 perform no strokes in the piston bores 6.
  • swash plate machine 1 both as axial piston 2 and as
  • Axial piston motor 3 have the piston bores 6, which are temporarily in fluid-conducting connection with the high-pressure opening 12, have a greater pressure on hydraulic fluid than the piston bores 6, which are temporarily in fluid-conducting connection with the low-pressure opening 13.
  • An axial end 66 of the cylinder drum 5 rests on the valve disc 1 1.
  • the retaining disc 37 is formed annularly as a flat disc and thus has an opening 38 for the passage of the drive shaft 9.
  • Retaining disc 37 sliding shoes 39 are fixed with bearing balls 40.
  • Retaining disc 37 has eight holes within which the sliding shoes 39 are arranged, so that the sliding shoes 39 in the radial direction, d. H.
  • the retaining disc 37 and the sliding shoes 39 are formed in several parts.
  • the number of holes corresponds to the number of holes
  • Sliding shoes 39 and piston 7 and in each bore is a sliding shoe 39th attached.
  • the retaining disc 37 is not directly on the support surface 18.
  • the drive shaft 9 is through the opening 63 through the housing 4 of
  • Swash plate machine 1 is sealed at the opening 63 or at the passage of the drive shaft 9 with a first shaft seal 17 as a mechanical seal 75 and with a second shaft seal 23, namely a radial shaft seal 81 with respect to the environment.
  • a first shaft seal 17 as a mechanical seal 75
  • a second shaft seal 23 namely a radial shaft seal 81 with respect to the environment.
  • In an axial direction 68 parallel to the axis of rotation 8 of the cylinder drum 5 and the drive shaft 9 is between the mechanical seal 75 and the radial shaft seal 81 a
  • the mechanical seal 75 comprises a
  • the rotating mating ring 71 is provided with a driving sleeve 76 as a first
  • Fastener 77 indirectly attached to the drive shaft 9, so that the rotating mating ring 71 performs the rotational movement of the drive shaft 9 with.
  • the driving sleeve 76 is positively connected by means of driving pins 80 with the drive shaft 9.
  • a radial direction 69 that is, in a radial direction 69 perpendicular to the axis of rotation 8 of
  • a first pre-side seal 78 is disposed as an O-ring seal 78 between the driver sleeve 76 and the drive shaft 9.
  • a second sub-seal 79 is disposed as an O-ring seal 79.
  • the first pre-side seal 78 serves to the annulus between the
  • An elastic element 73 is also arranged on the driving sleeve 76 as a compression spring 74, so that the rotating mating ring 71 is pressed onto the stationary sliding ring 70 by means of a pressure force applied by the compression spring 74 to the rotating mating ring 71.
  • a radial first sealing surface 72 between the fixed seal ring 70 and the rotating mating ring 71 thus has a surface pressure between the stationary seal ring 70 and the rotating mating ring 71 due to the pressure applied by the compression spring 74 on the rotating mating ring 71 compressive force.
  • the compression spring 74 is dimensioned to the extent that of this only a small compressive force is applied to the rotating mating ring 71.
  • Shaft seal 23, that is, for the radial shaft seal 81 is fixedly connected to the housing 4 and the flange 21, so that the holding plate 23 no
  • a first post-secondary seal 85 is arranged to seal the stationary holding plate 83 with respect to the fixed flange 21.
  • a second post-secondary seal 86th is arranged to seal the stationary retaining plate 83 with respect to the fixed sliding ring 70.
  • the retaining plate 83 has indirect contact with a retaining ring 82 which is fixed to the drive shaft 9.
  • the fixed radial shaft sealing ring 81 rests on a second sealing surface 34 on the rotating driver sleeve 76 and on the second sealing surface 34, the gap 33 is sealed with respect to the environment.
  • Radial shaft sealing ring 81 is thus indirectly on the drive shaft 9.
  • the first sealing surface 72 flowing leakage fluid is collected in the intermediate space 33.
  • the pressure of the hydraulic fluid within the inner space 44 varies between 2 and 17 bar, since the inner space 44 with the
  • Low pressure port 13 is in communication and the low pressure port 13 is hydraulically connected to a low pressure accumulator 55 of a drive train 45.
  • the mechanical seal 75 is designed such that at this a sufficiently large pressure drop occurs, so that the hydraulic fluid or
  • the return means 62 comprises a hose 35 and a housing bore 36, which each form a channel 67.
  • the hose 35 is fixed to a housing bore 36 of the flange 21, so that thereby the hydraulic fluid from the gap 33 can flow through the hose 35 into the housing bore 35 (Fig. 3).
  • the rest of the housing 4 has the housing bore 36, thereby characterized by the housing bore 36 and the other housing 4 the
  • FIG. 13 can be passed (Fig. 1).
  • the housing bore 36 on the remaining housing 4 is closed by means of a releasable closure element 61, so that the housing bore 36 is also accessible for maintenance purposes when the closure element 61 is removed.
  • a check valve 43 in the housing bore 36 serves to ensure that no hydraulic fluid from the
  • Interior 44 can flow from the low-pressure opening 13 to the intermediate space 33.
  • the rotating mating ring 71 is out of the compression spring 74 also by the hydrostatic pressure force of the hydraulic fluid to the rotating mating ring
  • the dimensioning of the rotating mating ring 71 and the compression spring 74 is designed so that the rotating mating ring 71 is pressed only with a small compressive force on the stationary seal ring 70, thereby characterized a large amount of leakage per unit time by the first sealing surface 72 in the Interspace 33 flows in. Due to this large volume flow of leakage liquid, a strong hydrostatic discharge of the rotating mating ring 71 occurs on the stationary seal ring 70, so that thereby the friction between the rotating mating ring 71 and the stationary seal ring 70 is low.
  • the efficiency of the swash plate machine 1 are substantially increased because the hydraulic increased energy losses per unit time due to the larger volume flow of leakage fluid to the mechanical seal 75 are substantially smaller than the reduced friction on the mechanical seal 75.
  • the Hydraulic or leakage fluid only a small pressure, so that by means of the radial shaft seal 81, a substantially complete sealing of the gap 33 is possible with respect to the environment and thus also the entire swash plate machine. 1
  • 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 thereby mechanical energy of the engine 46 in the high-pressure accumulator 54 can be stored hydraulically and also in a recuperation of a motor vehicle with the drive train 45 also kinetic energy of the motor vehicle in the high-pressure accumulator 54 can be stored hydraulically.
  • the differential gear 56 can additionally be driven with a swash plate machine 50, 51.
  • the mechanical seal 75 is required to seal the inner space 44.
  • the large hydrostatic discharge of the mechanical seal 75 caused in an advantageous manner to the mechanical seal 75 low friction losses.
  • the downstream radial shaft seal 81 seals the gap 33 with respect to the environment and due to the in the
  • Interspace 33 occurring pressure of the leakage or hydraulic fluid this can be returned due to the pressure difference of the gap 33 directly or indirectly in the interior 44 without an additional conveyor, such as a feed pump as a return pump, is necessary.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne une machine à plateau oscillant (1) utilisée comme pompe à pistons axiaux (2) et/ou comme moteur à pistons axiaux (3). La machine comprend un tambour cylindrique (5) monté de façon rotative ou tournante sur un axe de rotation (8) et comportant des alésages de piston (6) dans lesquels les pistons (7) sont montés de manière mobile. La machine comporte également un arbre d'entraînement (9) qui est relié au moins solidairement en rotation au tambour cylindrique (5) et qui est monté de façon rotative ou tournante sur l'axe de rotation (8). La machine comporte en outre un berceau pivotant (14) qui est monté à pivotement sur un axe de pivotement (15) et qui possède une surface d'appui (18) destinée à supporter les pistons (7) sur la surface d'appui (18). La machine comporte également un boîtier (4) qui délimite un espace intérieur rempli de fluide hydraulique (44) et qui possède une ouverture (63) destinée au passage de l'arbre d'entraînement (9), ainsi qu'une garniture d'étanchéité (23) disposée au niveau de l'arbre d'entraînement (9) pour réaliser l'étanchéité de l'arbre d'entraînement (9) passant à travers le boîtier (4) et donc de l'espace intérieur (44) par rapport à l'environnement. La machine à plateau oscillant (1) comprend une première garniture d'étanchéité d'arbre (17) et une seconde garniture d'étanchéité d'arbre (23). Un espace de stockage (33) est ménagé entre les première et seconde garnitures d'étanchéité d'arbre (17, 23) et le liquide de fuite qui pénètre dans l'espace intermédiaire peut être renvoyé dans l'espace intérieur (44) et/ou dans un orifice à basse pression à l'aide d'un moyen de recirculation (62).
PCT/EP2015/063313 2014-06-25 2015-06-15 Machine à plateau oscillant Ceased WO2015197403A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014212180.9 2014-06-25
DE102014212180.9A DE102014212180A1 (de) 2014-06-25 2014-06-25 Schrägscheibenmaschine

Publications (1)

Publication Number Publication Date
WO2015197403A1 true WO2015197403A1 (fr) 2015-12-30

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Application Number Title Priority Date Filing Date
PCT/EP2015/063313 Ceased WO2015197403A1 (fr) 2014-06-25 2015-06-15 Machine à plateau oscillant

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DE (1) DE102014212180A1 (fr)
WO (1) WO2015197403A1 (fr)

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2929551A (en) * 1956-09-17 1960-03-22 Gen Motors Corp Refrigerating apparatus
CH405934A (de) 1962-07-26 1966-01-15 Weatherhead Co Schrägscheiben-Axialkolbenpumpe
DE2733870C2 (fr) 1976-09-14 1989-07-20 Abex Corp., New York, N.Y., Us
DE19613609A1 (de) * 1996-04-04 1997-10-09 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit internem Spülkreislauf
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