EP1910674B1 - Displacer unit with a valve plate body - Google Patents

Displacer unit with a valve plate body Download PDF

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Publication number
EP1910674B1
EP1910674B1 EP06762814A EP06762814A EP1910674B1 EP 1910674 B1 EP1910674 B1 EP 1910674B1 EP 06762814 A EP06762814 A EP 06762814A EP 06762814 A EP06762814 A EP 06762814A EP 1910674 B1 EP1910674 B1 EP 1910674B1
Authority
EP
European Patent Office
Prior art keywords
control
displacer unit
unit according
control port
sealing
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.)
Not-in-force
Application number
EP06762814A
Other languages
German (de)
French (fr)
Other versions
EP1910674A1 (en
Inventor
Robert Adler
Georg Siebert
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.)
Linde GmbH
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Linde GmbH
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Filing date
Publication date
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Publication of EP1910674A1 publication Critical patent/EP1910674A1/en
Application granted granted Critical
Publication of EP1910674B1 publication Critical patent/EP1910674B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0011—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons liquid 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0465—Distribution members, e.g. valves plate-like
    • 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
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/0404—Details, component parts specially adapted for such pumps
    • F04B27/0451—Particularities relating to the distribution members
    • F04B27/0465—Particularities relating to the distribution members to plate like distribution members
    • 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
    • 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
    • F04B27/0804—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 rotary cylinder block
    • F04B27/0821—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 rotary cylinder block component parts, details, e.g. valves, sealings, lubrication
    • F04B27/0826—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 rotary cylinder block component parts, details, e.g. valves, sealings, lubrication particularities in the contacting area between cylinder barrel and valve 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F1/00—Pumps using positively or negatively pressurised fluid medium acting directly on the liquid to be pumped
    • F04F1/06—Pumps using positively or negatively pressurised fluid medium acting directly on the liquid to be pumped the fluid medium acting on the surface of the liquid to be pumped
    • F04F1/10—Pumps using positively or negatively pressurised fluid medium acting directly on the liquid to be pumped the fluid medium acting on the surface of the liquid to be pumped of multiple type, e.g. with two or more units in parallel

Definitions

  • the invention relates to a displacement unit having at least one displacement chamber arranged in a cylindrical drum rotating about an axis of rotation, which is connectable to an inlet connection and an outlet connection by means of a control surface, wherein the control surface is formed on a control mirror body, which has a first control opening which communicates with the inlet connection is in communication, and a second control port, which communicates with the outlet port, is provided.
  • control surface is formed on a control mirror body provided with a kidney-shaped control port communicating with the inlet port and a kidney-shaped control port connected with the exhaust port.
  • the control openings are arranged here on a common pitch circle.
  • each displacement chamber rests on the stationary control mirror body, wherein each displacement chamber has a connection opening for connection to the control openings. Between the connection opening and the control openings a flat seal is provided.
  • document DE 199 304 11A discloses a displacer unit according to the preamble of claim 1.
  • the present invention has for its object to provide a displacer unit of the type mentioned, which has low leakage currents and thus is suitable for operation at high maximum operating pressures.
  • the displacer is connected by means of a first connecting channel with the first control port and a second connection channel with the second control port and the connecting channels are provided by means of a respective mechanical seal for sealing against the control port.
  • the control openings of the control mirror body are arranged on separate pitch circles and the displacer connected by means of two arranged on separate pitch circles connecting channels with the corresponding control port, wherein instead of a two-dimensional seal of the prior art by means of the mechanical seals sealing the Verdrängerippo done with the control ports.
  • the mechanical seal is designed as a sliding ring bushing.
  • the connecting channels of the displacement chambers can be sealed in a simple manner with respect to the control openings arranged in the control body.
  • the mechanical seal can be acted upon by means of a spring in the direction of the control mirror body.
  • the designed as a sliding ring bushes mechanical seals are thus biased by the spring and are pressed by the spring to the control surface.
  • a secure concern of the sliding ring bushing is achieved on the control mirror body and thus a secure seal.
  • the mechanical seals are provided with a control surface acting in the direction of the control disk body, wherein the control surface is acted upon by the pressure applied in the connecting channel pressure.
  • a simple construction with low production costs of the provided with the mechanical seals connecting channels can be achieved if the mechanical seal is arranged in a bore-shaped recess of the connecting channel.
  • the mechanical seals are sealed by means of an O-ring with respect to the recess. In this way, a leakage current between the recess and the sliding ring bushing can be effectively avoided with little construction effort.
  • a sealing device for sealing the first control opening relative to the second control opening and / or a sealing device for sealing the first control opening relative to a housing interior and / or a sealing device for sealing the second control opening relative to the housing interior ,
  • sealing devices sealing of the first control opening relative to the second control opening and sealing of the first control opening and the second control opening relative to the housing interior and thus sealing of the control openings can be achieved in a simple manner, whereby leakage flows be avoided between the control ports and from the control openings to the housing interior and thus an operation of the displacer unit is made possible at high operating pressures and high efficiency.
  • the sealing device is in this case designed according to a preferred embodiment as a mechanical seal. With such annular mechanical seals, the control openings can be sealed in a simple manner.
  • sealing device by means of a spring in the direction of the cylinder drum can be acted upon, can be achieved with little construction effort a safe concern of the sealing means formed by the mechanical seals on the cylinder drum to seal the control openings.
  • sealing devices are provided with a control surface acting in the direction of the cylinder drum. This results in a pressure-dependent contact pressure formed as mechanical seals sealing means, so that when operating the displacer unit at high pressures a secure sealing of the control openings with each other and against de housing interior and thus small leaks can be achieved.
  • control surface of the first control opening relative to the second control opening sealing sealing means and the control surface of the second control opening relative to the housing interior sealing sealing means is acted upon by the pending in the second control port pressure and the control surface of the first control port opposite the housing interior sealing sealing means of the pending in the first control port pressure can be acted upon.
  • a displacer unit operated as a compressor in which the first control opening is connected to the inlet connection acted upon by low pressure and the second control opening is connected to the outlet connection leading to the maximum operating pressure, an additional loading of the sealing device sealing the first control opening relative to the housing interior can be effected Low pressure and an additional admission of the first control port relative to the second control port sealing sealing device and the second control opening relative to the housing interior sealing sealing means of the pending in the second control port operating pressure and thus a secure sealing of the first control port and the second control port can be achieved.
  • a simple arrangement of the trained as a mechanical seals sealing device with low construction costs can be achieved if the sealing means are arranged in an annular recess of the control mirror body.
  • Leakage flows between the recesses and the sealing devices can be avoided in a simple manner if the sealing device is sealed according to an expedient development of the invention by means of an O-ring with respect to the recess.
  • control openings are expediently designed as kidney-shaped control openings.
  • the control mirror body by means of an adjusting device, in particular an actuating piston, with respect to the axis of rotation is rotatable, the engagement times of the control ports and in particular the engagement time of the acted upon by the maximum operating pressure control port can be changed in a simple manner.
  • pressure equalizing currents and pressure pulsations which occur when connecting the displacement to the maximum operating pressure leading control port due to the pressure difference between the displacement and the pressure present in the control port pressure can be reduced, whereby in a compressor operated as a Verdrängertechnik pressure pulsations and pressure equalization currents, the energy consumption a displacer unit operated as a compressor can be increased, reduced and avoided.
  • the displacer unit can be operated as a compressor or as a motor and is suitable for operation with liquids as well as with gaseous media, in particular hydrogen.
  • FIG. 1 shows a piston-less displacer unit 1 according to the invention in a longitudinal section.
  • a drive shaft 3 is rotatably mounted about a rotation axis 4.
  • a cylinder drum 5 is rotatably coupled, in which a plurality of displacement chambers 6 designed as displacement cylinders are formed.
  • the displacement chambers 6 are in this case designed as arranged in the cylinder drum 5 radial bores 14 and arranged in a star shape about the rotation axis 4, wherein the longitudinal axis 7 of the displacement 6 is perpendicular to the axis of rotation 4 of the drive shaft 3 and thus the cylinder drum 5.
  • the displacement chambers 6 are in the radially inner region with a first connection channel 8a and a second connection channel 8b in connection, which are radially spaced.
  • the connecting channels 8a, 8b are in operative connection with a disk-shaped control mirror body 9, wherein on the cylinder drum 5 facing end face of the control mirror body 9, a control surface 9a is formed.
  • the control plate 9 By means of the control plate 9, the connection of the displacement chambers 6 with an inlet port 10 and an outlet port 11 is controllable.
  • the cylinder drum 5 is in this case supported in the axial direction on the control mirror 9, which is arranged on a housing cover 12 attached to the housing 2.
  • liquid 15 in particular ionic liquid is arranged.
  • Each displacer 6 is by means of a connecting channel 13 with a cylinder chamber 16 as an axial piston machine in swash plate design trained hydraulic displacer unit 17 in conjunction.
  • the displacer unit 17 embodied as an axial piston machine in this case has a cylinder block 18 which is arranged coaxially with the cylinder drum 5 and is non-rotatably connected with the cylinder drum 5 or the drive shaft 3. It is also possible to form the cylinder block 18 and the cylinder drum 5 as a common and thus one-piece cylinder drum.
  • the cylinder chambers 16 of the axial piston machine are formed by longitudinal bores 20 concentrically arranged in the cylinder block 18, in each of which a piston 21 is arranged to be longitudinally displaceable.
  • the pistons 21 are supported by means of a respective sliding shoe 22 on a swash plate 23. Between piston 21 and shoe 22, a spherical Gleitschuhgelenk is formed.
  • the axial piston machine is designed as an axial piston machine which can be adjusted in the displacement volume, wherein the swashplate 23 is pivotally mounted on the housing 2 and can be tilted relative to the axis of rotation 4 by means of an adjusting device which is no longer shown.
  • the axial piston machine it is also possible to form the axial piston machine with a fixed displacement volume, wherein the swash plate can be formed directly on the housing 2.
  • the cylinder drum 5 and the displacer unit 17 are arranged in the common housing.
  • the cylinder drum 5 and the cylinder block 18 are driven via the drive shaft 3.
  • the axial piston machine operates as a pump and delivers liquid 15 from the cylinder chambers 16 into the displacement chambers 6, whereby the medium flowing into the displacement cylinders 6 via the inlet connection 10 carrying the low pressure is compressed by the liquid 15 and conveyed into the outlet connection 11 leading to the operating pressure.
  • pressurized medium is supplied to the displacement chambers 6 via the inlet connection 10 leading to the operating pressure.
  • the piston 21 are acted upon, the axial piston engine as an engine is operated and a rotational movement of the cylinder drum 5 and the cylinder block 18 is generated, whereby a torque on the drive shaft 3 can be tapped.
  • control mirror body 9 is shown in a plan view of the control surface 9a.
  • the control mirror body 9 has a first control opening 20 which is connected to the inlet connection and which is kidney-shaped.
  • the control openings 20, 21 are arranged radially spaced from each other on different pitch circles.
  • the first connection channel 8a which is in communication with the displacement chamber, controls the first control opening 20.
  • the second connection channel 8b drives the second control opening 21.
  • first connecting channel 8a and the second connecting channel 8b On the first connecting channel 8a and the second connecting channel 8b, respective sliding ring seals 22a, 22b for sealing the connecting channel 8a, 8b with respect to the control openings 20, 21 are arranged.
  • a sealing device 25 is provided, which is formed by an annular mechanical seal 25a.
  • the first control opening 20 is sealed by means of a further sealing device 26 with respect to the housing interior, which is formed as an annular mechanical seal 26a.
  • a further sealing device 27 is provided, which is designed as an annular mechanical seal 27a.
  • annular space 28 is formed, in which the second control port 21 opens.
  • the annular space 28 is thus acted upon by the pending at the second control port 21 pressure.
  • annular space 29 is formed, in which the first control port 20 opens, whereby the annular space 29 is acted upon by the pending at the control port 20 pressure.
  • the control mirror body 9 is connected to an adjusting device 50, which is formed for example as a control cylinder 51, in operative connection, by means of which the control mirror body 9 with respect to the rotation axis 4 is rotatable.
  • an adjusting device 50 which is formed for example as a control cylinder 51, in operative connection, by means of which the control mirror body 9 with respect to the rotation axis 4 is rotatable.
  • the mechanical seals 22a, 22b of the connecting channels 8a, 8b are formed as Gleitringbuchsen, which are arranged in a respective bore-shaped recess 30a, 30b of the connecting channel 8a, 8b.
  • the mechanical seals 22a, 22b are acted upon by means disposed in the recess 30a, 30b spring 31 a, 31 b in the direction of the control mirror body 9.
  • a control surface 32a, 32b is formed, which urges the sliding ring seals 22a, 22b in the direction of the control mirror body 9.
  • control surface 32a, 32b is acted upon by the pressure present in the connecting channel 8a, 8b.
  • O-ring 33a, 33b which is arranged between the recess 30a, 30b and the mechanical seals 22a, 22b, the connecting channels 8a, 8b are sealed against the annular spaces 28, 29.
  • the sealing means 25, 26, 27 are formed as annular sliding ring seals 25a, 26a, 27a, which are arranged in annular recesses 35, 36, 37 of the control mirror body 9.
  • the mechanical seals 25a, 26a, 27a are in this case by means of a respective spring 38, 39, 40, which are arranged in the corresponding recess 35, 36, 37, acted upon in the direction of the cylinder drum 5.
  • control surfaces 41, 42, 43 are formed.
  • control surface 41 formed on the sealing device 25 and the control surface 43 formed on the sealing device 27 are acted upon here by the pressure prevailing in the annular space 28 and thus at the control opening 21.
  • the formed on the sealing device 26 control surface 42 is acted upon by the pressure in the annular space 29 and thus in the control port 20 pending.
  • an O-ring 45 is arranged between the sealing device 25 and the recess 35, by means of which the annular space 28 is sealed by the annular space 29.
  • Another O-ring 46 is arranged on the radially outer region of the sealing device 26 between the sealing device 26 and the recess 36. By means of the O-ring 46, the annular space 29 is sealed against the housing interior.
  • an O-ring 47 is arranged between the recess 37 and the sealing device 27, by means of which the annular space 28 is sealed relative to the housing interior in the region of the drive shaft.
  • the inlet port 10 When operating the displacer unit 1 according to the invention as a compressor, the inlet port 10 is subjected to low pressure.
  • the outlet port 11 is acted upon by the generated operating pressure.
  • the annular space 28, which is connected via the second control opening 21 with the outlet port 11, is acted upon by the generated high pressure.
  • the connection of the first control opening 20 with the displacement chamber 6 is controlled via the connecting channel 8a, wherein a seal is achieved via the mechanical seal 22a.
  • the connection of the second control opening 21 with the displacement chamber 6 via the connecting channel 8b wherein by means of the mechanical seal 22b, a seal is achieved.
  • the mechanical seals 22a, 22b are acted upon here in addition to the springs 31a, 31b by the pressure in the displacement chamber 6 in the direction of the control mirror body 9.
  • the second control opening 21 is in this case dimensioned such that in each case only one displacement chamber 6 communicates with the control opening 21.
  • a leakage flow from the first control surface 20 to the second control surface 21 is avoided by the sealing device 25, which is acted upon by the spring 38 and the pending on the control surface 41 operating pressure in the direction of the cylinder barrel 5.
  • the leakage flow from the second control surface 21 to the housing interior in the region of the drive shaft 3 is avoided by the sealing device 27, which is acted upon in addition to the spring 40 by the pending on the control surface 43 operating pressure in the direction of the cylinder drum 5.
  • the leakage flow from the first control surface 20 to the housing interior is avoided by the sealing device 26, which is acted upon by the spring 39 and the low pressure, which is present at the control surface 42, in the direction of the cylinder drum 5.
  • the displacer unit 1 according to the invention is suitable for operation at high maximum operating pressures, in particular for operating pressures of up to 1000 bar, the displacer unit operated as a compressor having a low energy requirement and high efficiency.
  • the displacer unit according to the invention operated as a compressor can be used for compressing gaseous media, in particular hydrogen.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Rotary Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Sliding Valves (AREA)
  • Rear-View Mirror Devices That Are Mounted On The Exterior Of The Vehicle (AREA)
  • Mounting And Adjusting Of Optical Elements (AREA)
  • Telescopes (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Mechanical Sealing (AREA)

Abstract

A displacer unit with a valve plate body is disclosed. The displacer unit having at least one displacer space which is arranged in a cylindrical drum rotating about an axis of rotation and which can be connected to an inlet connection and an outlet connection by a control surface. The control surface is formed on a valve plate body which is provided with a first control opening, which is connected to the inlet connection, and with a second control opening, which is connected to the outlet connection. The first control opening and the second control opening are spaced apart radially, where the displacer space can be connected to the first control opening by a first connecting passage and to the second control opening by a second connecting passage. The connecting passages are provided with a respective mechanical face seal for sealing relative to the control openings.

Description

Die Erfindung betrifft eine Verdrängereinheit mit zumindest einem in einer um eine Drehachse rotierenden Zylindertrommel angeordneten Verdrängerraum, der mittels einer Steuerfläche mit einem Einlassanschluss und einem Auslassanschluss verbindbar ist, wobei die Steuerfläche an einem Steuerspiegelkörper ausgebildet ist, der mit einer ersten Steueröffnung, die mit dem Einlassanschluss in Verbindung steht, und einer zweiten Steueröffnung, die mit dem Auslassanschluss in Verbindung steht, versehen ist.The invention relates to a displacement unit having at least one displacement chamber arranged in a cylindrical drum rotating about an axis of rotation, which is connectable to an inlet connection and an outlet connection by means of a control surface, wherein the control surface is formed on a control mirror body, which has a first control opening which communicates with the inlet connection is in communication, and a second control port, which communicates with the outlet port, is provided.

Bei gattungsgemäße Verdrängereinheiten, die als Verdichter oder als Motor betrieben werden können, wird mittels der Steuerfläche die abwechselnde Verbindung der in der rotierenden Zylindertrommel angeordneten Verdrängerräume mit dem am Gehäuse ausgebildeten Einlassanschluss und Auslassanschluss sichergestellt. Die Steuerfläche ist an einem Steuerspiegelkörper ausgebildet, der mit einer nierenförmigen, mit dem Einlassanschluss in Verbindung stehenden Steueröffnung und einer nierenförmigen, mit dem Auslassanschluss verbundenen Steueröffnung versehen ist. Die Steueröffnungen sind hierbei auf einem gemeinsamen Teilkreis angeordnet.In generic displacer units which can be operated as a compressor or as a motor, the alternating connection of the displacement chambers arranged in the rotating cylinder drum with the inlet connection and outlet connection formed on the housing is ensured by means of the control surface. The control surface is formed on a control mirror body provided with a kidney-shaped control port communicating with the inlet port and a kidney-shaped control port connected with the exhaust port. The control openings are arranged here on a common pitch circle.

Die rotierende Zylindertrommel liegt hierbei an dem feststehenden Steuerspiegelkörper an, wobei jeder Verdrängerraum eine Verbindungsöffnung zur Verbindung mit den Steueröffnungen aufweist. Zwischen der Verbindungsöffnung und den Steueröffnungen ist eine flächige Abdichtung vorgesehen.The rotating cylinder drum rests on the stationary control mirror body, wherein each displacement chamber has a connection opening for connection to the control openings. Between the connection opening and the control openings a flat seal is provided.

Bei derartigen Verdrängereinheiten ist zur Verringerung der an der flächigen Abdichtung auftretenden Reibung eine hydrostatische Entlastung vorgesehen. Die hydrostatische Entlastung führt jedoch zu Leckageströmen zwischen der Einlassseite und der Auslassseite sowie von der Einlassseite und von der Auslassseite zum Gehäuseinnenraum. Darüber hinaus tritt ein Druckmittelfluss zwischen den Verdrängerräumen auf. Die flächige Abdichtung weist weiterhin bereits bei leichten Beschädigungen oder Abnutzungen eine erhöhten Leckagestrom auf. Durch diese Leckageströme ist der Betrieb der Verdrängereinheit auf einen bestimmten maximalen Betriebsdruck begrenzt. Gattungsgemäße Verdrängereinheiten sind somit für einen Betrieb der Verdrängereinheit bei hohen maximalen Betriebsdrücken, insbesondere Drücken von bis zu 1000 bar, durch die zunehmenden Leckageströme und den daraus bedingten schlechter Wirkungsgrad nicht geeignet.In such displacement units a hydrostatic discharge is provided to reduce the friction occurring at the surface seal. However, the hydrostatic discharge leads to leakage flows between the inlet side and the outlet side and from the inlet side and from the outlet side to the housing interior. In addition, a pressure medium flow occurs between the displacement chambers. The two-dimensional seal continues to have an increased leakage current even with slight damage or wear. Through this Leakage currents, the operation of the displacer unit is limited to a certain maximum operating pressure. Generic displacement units are thus not suitable for operation of the displacer unit at high maximum operating pressures, in particular pressures of up to 1000 bar, due to the increasing leakage currents and the resulting poor efficiency.

Dokument DE 199 304 11A offenbart eine Verdrängereinheit gemäß dem Oberbegriff des Anspruchs 1. Der vorliegenden Erfindung liegt die Aufgabe zugrunde, eine Verdrängereinheit der eingangs genannten Gattung zur Verfügung zu stellen, die geringe Leckageströme aufweist und somit für eine Betrieb bei hohen maximalen Betriebsdrücken geeignet ist.document DE 199 304 11A discloses a displacer unit according to the preamble of claim 1. The present invention has for its object to provide a displacer unit of the type mentioned, which has low leakage currents and thus is suitable for operation at high maximum operating pressures.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, dass der Verdrängerraum mittels eines ersten Verbindungskanals mit der ersten Steueröffnung und mittel eines zweiten Verbindungskanals mit der zweiten Steueröffnung verbindbar ist und die Verbindungskanäle mittels jeweils einer Gleitringdichtung zur Abdichtung gegenüber der Steueröffnung versehen sind. Erfindungsgemäß sind somit die Steueröffnungen des Steuerspiegelkörpers auf getrennten Teilkreisen angeordnet und der Verdrängerraum mittels zweier auf getrennten Teilkreisen angeordneter Verbindungskanäle mit der entsprechenden Steueröffnung verbindbar, wobei anstelle einer flächigen Abdichtung des Standes der Technik mittels der Gleitringdichtungen eine Abdichtung der Verdrängerräume mit den Steueröffnungen erfolgt. Mit einer derartigen Abdichtung durch die Gleitringdichtungen können Leckageströme zwischen den Verdrängerräumen und Leckageströme zwischen der Einlassseite und der Auslassseite sowie von der Einlassseite und von der Auslassseite zum Gehäuseinnenraum wirksam vermieden werden. Die erfindungsgemäße Verdrängereinheit ist hierdurch für einen Betrieb bei hohen maximalen Betriebsdrücken von insbesondere bis zu 1000bar geeignet und weist hierbei einen hohen Wirkungsrad auf.This object is achieved in that the displacer is connected by means of a first connecting channel with the first control port and a second connection channel with the second control port and the connecting channels are provided by means of a respective mechanical seal for sealing against the control port. According to the invention thus the control openings of the control mirror body are arranged on separate pitch circles and the displacer connected by means of two arranged on separate pitch circles connecting channels with the corresponding control port, wherein instead of a two-dimensional seal of the prior art by means of the mechanical seals sealing the Verdrängerräume done with the control ports. With such a seal by the mechanical seals leakage currents between the displacement chambers and leakage flows between the inlet side and the outlet side and from the inlet side and the outlet side to the housing interior can be effectively avoided. The displacer unit according to the invention is thus suitable for operation at high maximum operating pressures of in particular up to 1000bar and in this case has a high degree of efficiency.

Gemäß einer bevorzugten Ausführungsform der Erfindung ist die Gleitringdichtung als Gleitringbuchse ausgebildet. Mittels ringförmiger Gleitringbuchsen können die Verbindungskanäle der Verdrängerräume auf einfache Weise gegenüber den in dem Steuerspiegelkörper angeordneten Steueröffnungen abgedichtet werden.According to a preferred embodiment of the invention, the mechanical seal is designed as a sliding ring bushing. By means of annular sliding ring bushes, the connecting channels of the displacement chambers can be sealed in a simple manner with respect to the control openings arranged in the control body.

Mit besonderem Vorteil ist die Gleitringdichtung mittels einer Feder in Richtung des Steuerspiegelkörpers beaufschlagbar. Die als Gleitringbuchsen ausgebildeten Gleitringdichtungen sind somit von der Feder vorgespannt und werden mittels der Feder an die Steuerfläche gepresst. Hierdurch wird ein sicheres Anliegen der Gleitringbuchse an dem Steuerspiegelkörper und somit eine sichere Abdichtung erzielt.With particular advantage, the mechanical seal can be acted upon by means of a spring in the direction of the control mirror body. The designed as a sliding ring bushes mechanical seals are thus biased by the spring and are pressed by the spring to the control surface. As a result, a secure concern of the sliding ring bushing is achieved on the control mirror body and thus a secure seal.

Gemäß einer bevorzugten Weiterbildung der Verbindung sind die Gleitringdichtungen mit einer in Richtung des Steuerspiegelkörpers wirkenden Steuerfläche versehen, wobei die Steuerfläche von dem in dem Verbindungskanal anstehenden Druck beaufschlagbar ist. Hierdurch wird eine zusätzliche Beaufschlagung der als Gleitringbuchsen ausgebildeten Gleitringdichtungen von dem in dem Verdrängerraum anstehenden Druck und somit eine vom anstehenden Betriebsdruck abhängige Beaufschlagung der Gleitringbuchsen an die Steueröffnungen erzielt, so dass bei einem Betrieb der Verdrängereinheit bei hohen Betriebsdrücken eine sichere Abdichtung der Verdrängerräume gegenüber den Steueröffnungen und somit geringe Leckageströme erzielt werden.According to a preferred embodiment of the compound, the mechanical seals are provided with a control surface acting in the direction of the control disk body, wherein the control surface is acted upon by the pressure applied in the connecting channel pressure. As a result, an additional loading of the formed as sliding ring bushes mechanical seals of the pending in the displacement pressure and thus a dependent on the upcoming operating pressure of the sliding ring bushings is achieved at the control ports, so that during operation of the displacer unit at high operating pressures a secure sealing of the displacer relative to the control ports and thus low leakage currents can be achieved.

Ein einfacher Aufbau mit geringem Herstellaufwand der mit den Gleitringdichtungen versehenen Verbindungskanäle ist erzielbar, wenn die Gleitringdichtung in einer bohrungsförmigen Ausnehmung des Verbindungskanals angeordnet ist.A simple construction with low production costs of the provided with the mechanical seals connecting channels can be achieved if the mechanical seal is arranged in a bore-shaped recess of the connecting channel.

Gemäß einer bevorzugten Ausführungsform der Erfindung ist vorgesehen, dass die Gleitringdichtungen mittels eines O-Rings gegenüber der Ausnehmung abgedichtet sind. Hierdurch kann ein Leckagestrom zwischen der Ausnehmung und der Gleitringbuchse wirksam und mit geringem Bauaufwand vermieden werden.According to a preferred embodiment of the invention it is provided that the mechanical seals are sealed by means of an O-ring with respect to the recess. In this way, a leakage current between the recess and the sliding ring bushing can be effectively avoided with little construction effort.

Besondere Vorteile ergeben sich, wenn gemäß einer Weiterbildung der Erfindung eine Dichteinrichtung zur Abdichtung der ersten Steueröffnung gegenüber der zweiten Steueröffnung und/oder eine Dichteinrichtung zur Abdichtung der ersten Steueröffnung gegenüber einem Gehäuseinnenraum und/oder eine Dichteinrichtung zur Abdichtung der zweiten Steueröffnung gegenüber dem Gehäuseinnenraum vorgesehen ist. Mit derartigen Dichteinrichtungen kann auf einfache Weise eine Abdichtung der ersten Steueröffnung gegenüber der zweiten Steueröffnung sowie eine Abdichtung der ersten Steueröffnung und der zweiten Steueröffnung gegenüber dem Gehäuseinnenraum und somit eine Abdichtung der Steueröffnungen erzielt werden, wodurch Leckageströmen zwischen den Steueröffnungen und von den Steueröffnungen zum Gehäuseinnenraum vermieden werden und somit ein Betrieb der Verdrängereinheit bei hohen Betriebsdrücken und einem hohen Wirkungsgrad ermöglicht wird.Particular advantages arise when, according to a development of the invention, a sealing device is provided for sealing the first control opening relative to the second control opening and / or a sealing device for sealing the first control opening relative to a housing interior and / or a sealing device for sealing the second control opening relative to the housing interior , With such sealing devices, sealing of the first control opening relative to the second control opening and sealing of the first control opening and the second control opening relative to the housing interior and thus sealing of the control openings can be achieved in a simple manner, whereby leakage flows be avoided between the control ports and from the control openings to the housing interior and thus an operation of the displacer unit is made possible at high operating pressures and high efficiency.

Die Dichteinrichtung ist hierbei gemäß einer bevorzugten Ausgestaltungsform als Gleitringdichtung ausgebildet. Mit derartigen ringförmigen Gleitringdichtungen können die Steueröffnungen auf einfache Weise abgedichtet werden.The sealing device is in this case designed according to a preferred embodiment as a mechanical seal. With such annular mechanical seals, the control openings can be sealed in a simple manner.

Sofern die Dichteinrichtung gemäß einer zweckmäßigen Weiterbildung der Erfindung mittels einer Feder in Richtung der Zylindertrommel beaufschlagbar ist, kann mit geringem Bauaufwand ein sicheres Anliegen der von den Gleitringdichtungen gebildeten Dichteinrichtungen an der Zylindertrommel zur Abdichtung der Steueröffnungen erzielt werden.If the sealing device according to an expedient development of the invention by means of a spring in the direction of the cylinder drum can be acted upon, can be achieved with little construction effort a safe concern of the sealing means formed by the mechanical seals on the cylinder drum to seal the control openings.

Besondere Vorteile ergeben sich, wenn die Dichteinrichtungen mit einer in Richtung der Zylindertrommel wirkenden Steuerfläche versehen sind. Hierdurch ergibt sich eine druckabhängige Anpressung der als Gleitringdichtungen ausgebildeten Dichteinrichtungen, so dass bei einem Betrieb der Verdrängereinheit bei hohen Drücken eine sichere Abdichtung der Steueröffnungen untereinander und gegenüber de Gehäuseinnenraum und somit geringe Leckagen erzielt werden.Particular advantages arise when the sealing devices are provided with a control surface acting in the direction of the cylinder drum. This results in a pressure-dependent contact pressure formed as mechanical seals sealing means, so that when operating the displacer unit at high pressures a secure sealing of the control openings with each other and against de housing interior and thus small leaks can be achieved.

Gemäß einer bevorzugten Ausgestaltungsform der Erfindung ist hierbei die Steuerfläche der die erste Steueröffnung gegenüber der zweiten Steueröffnung abdichtenden Dichteinrichtung und die Steuerfläche der die zweite Steueröffnung gegenüber dem Gehäuseinnenraum abdichtenden Dichteinrichtung von dem in der zweiten Steueröffnung anstehenden Druck beaufschlagbar ist und die Steuerfläche der die erste Steueröffnung gegenüber dem Gehäuseinnenraum abdichtenden Dichteinrichtung von dem in der ersten Steueröffnung anstehenden Druck beaufschlagbar ist. Bei einer als Verdichter betriebenen Verdrängereinheit, bei der die erste Steueröffnung mit den von Niederdruck beaufschlagten Einlassanschluss verbunden ist und die zweite Steueröffnung mit dem den maximalen Betriebsdruck führenden Auslassanschluss verbunden ist, kann hierdurch eine zusätzliche Beaufschlagung der die erste Steueröffnung gegenüber dem Gehäuseinnenraum abdichtenden Dichteinrichtung von dem Niederdruck und eine zusätzliche Beaufschlagung der die erste Steueröffnung gegenüber der zweiten Steueröffnung abdichtenden Dichteinrichtung sowie der die zweite Steueröffnung gegenüber dem Gehäuseinnenraum abdichtenden Dichteinrichtung von dem in der zweiten Steueröffnung anstehenden Betriebsdruck und somit eine sichere Abdichtung der ersten Steueröffnung und der zweiten Steueröffnung erzielt werden.According to a preferred embodiment of the invention in this case the control surface of the first control opening relative to the second control opening sealing sealing means and the control surface of the second control opening relative to the housing interior sealing sealing means is acted upon by the pending in the second control port pressure and the control surface of the first control port opposite the housing interior sealing sealing means of the pending in the first control port pressure can be acted upon. In a displacer unit operated as a compressor, in which the first control opening is connected to the inlet connection acted upon by low pressure and the second control opening is connected to the outlet connection leading to the maximum operating pressure, an additional loading of the sealing device sealing the first control opening relative to the housing interior can be effected Low pressure and an additional admission of the first control port relative to the second control port sealing sealing device and the second control opening relative to the housing interior sealing sealing means of the pending in the second control port operating pressure and thus a secure sealing of the first control port and the second control port can be achieved.

Eine einfache Anordnung der als Gleitringdichtungen ausgebildeten Dichteinrichtung mit geringem Bauaufwand ist erzielbar, wenn die Dichteinrichtungen in einer ringförmigen Aussparung des Steuerspiegelkörpers angeordnet sind.A simple arrangement of the trained as a mechanical seals sealing device with low construction costs can be achieved if the sealing means are arranged in an annular recess of the control mirror body.

Leckageströme zwischen den Aussparungen und den Dichteinrichtungen sind auf einfache Weise vermeidbar, wenn die Dichteinrichtung gemäß einer zweckmäßigen Weiterbildung der Erfindung mittels eines O-Rings gegenüber der Aussparung abgedichtet ist.Leakage flows between the recesses and the sealing devices can be avoided in a simple manner if the sealing device is sealed according to an expedient development of the invention by means of an O-ring with respect to the recess.

Die Steueröffnungen sind hierbei zweckmäßigerweise als nierenförmige Steueröffnungen ausgebildet.The control openings are expediently designed as kidney-shaped control openings.

Sofern gemäß einer vorteilhaften Weiterbildung der Erfindung der Steuerspiegelkörper mittels einer Stelleinrichtung, insbesondere eines Stellkolbens, bezüglich der Drehachse verdrehbar ist, kann auf einfache Weise die Eingriffszeitpunkte der Steueröffnungen und insbesondere der Eingriffszeitpunkt der mit dem maximalen Betriebsdruck beaufschlagten Steueröffnung verändert werden. Hierdurch können Druckausgleichsströme und Druckpulsationen, die beim Anschluss des Verdrängerraums an die den maximalen Betriebsdruck führende Steueröffnung aufgrund des Druckunterschiedes zwischen dem Verdrängerraum und dem in der Steueröffnung anstehende Druck auftreten, verringert werden, wodurch bei einer als Verdichter betriebenen Verdrängereinheit Druckpulsationen und Druckausgleichströme, die den Energieverbrauch einer als Verdichter betrieben Verdrängereinheit ansteigen lassen, verringert und vermieden werden können.If according to an advantageous embodiment of the invention, the control mirror body by means of an adjusting device, in particular an actuating piston, with respect to the axis of rotation is rotatable, the engagement times of the control ports and in particular the engagement time of the acted upon by the maximum operating pressure control port can be changed in a simple manner. As a result, pressure equalizing currents and pressure pulsations, which occur when connecting the displacement to the maximum operating pressure leading control port due to the pressure difference between the displacement and the pressure present in the control port pressure can be reduced, whereby in a compressor operated as a Verdrängereinheit pressure pulsations and pressure equalization currents, the energy consumption a displacer unit operated as a compressor can be increased, reduced and avoided.

Die Verdrängereinheit kann als Verdichter oder als Motor betrieben werden und ist für den Betrieb mit Flüssigkeiten als auch mit gasförmigen Medien, insbesondere Wasserstoff, geeignet.The displacer unit can be operated as a compressor or as a motor and is suitable for operation with liquids as well as with gaseous media, in particular hydrogen.

Weitere Vorteile und Einzelheiten der Erfindung werden anhand des in den schematischen Figuren dargestellten Ausführungsbeispiels näher erläutert. Hierbei zeigt

Figur 1
ein erfindungsgemäßes Triebwerk in einem Längsschnitt,
Figur 2
eine Draufsicht auf die Steuerfläche und
Figur 3
eine Seitenansicht der Steuerfläche in einer vergrößerten Darstellung.
Further advantages and details of the invention will be explained in more detail with reference to the embodiment shown in the schematic figures. This shows
FIG. 1
an engine according to the invention in a longitudinal section,
FIG. 2
a plan view of the control surface and
FIG. 3
a side view of the control surface in an enlarged view.

Die Figur 1 zeigt eine erfindungsgemäße, kolbenlose Verdrängereinheit 1 in einem Längsschnitt. Innerhalb eines Gehäuses 2 ist eine Triebwelle 3 um eine Drehachse 4 drehbar gelagert. Mit der Triebwelle 3 ist eine Zylindertrommel 5 drehsynchron gekoppelt, in der mehrere als Verdrängerzylinder ausgebildete Verdrängerräume 6 ausgebildet sind. Die Verdrängerräume 6 sind hierbei als in der Zylindertrommel 5 angeordnete Radialbohrungen 14 ausgebildet und um die Drehachse 4 sternförmig angeordnet, wobei die Längsachse 7 der Verdrängerräume 6 senkrecht zur Drehachse 4 der Triebwelle 3 und somit der Zylindertrommel 5 angeordnet ist.The FIG. 1 shows a piston-less displacer unit 1 according to the invention in a longitudinal section. Within a housing 2, a drive shaft 3 is rotatably mounted about a rotation axis 4. With the drive shaft 3, a cylinder drum 5 is rotatably coupled, in which a plurality of displacement chambers 6 designed as displacement cylinders are formed. The displacement chambers 6 are in this case designed as arranged in the cylinder drum 5 radial bores 14 and arranged in a star shape about the rotation axis 4, wherein the longitudinal axis 7 of the displacement 6 is perpendicular to the axis of rotation 4 of the drive shaft 3 and thus the cylinder drum 5.

Die Verdrängerräume 6 stehen im radial inneren Bereich mit einem ersten Verbindungskanal 8a und einem zweiten Verbindungskanal 8b in Verbindung, die radial beabstandet sind. Die Verbindungskanäle 8a, 8b stehen mit einem scheibenförmigen Steuerspiegelkörper 9 in Wirkverbindung, wobei an der der Zylindertrommel 5 zugewandten Stirnfläche des Steuerspiegelkörpers 9 eine Steuerfläche 9a ausgebildet ist. Mittels des Steuerspiegels 9 ist die Verbindung der Verdrängerräume 6 mit einem Einlassanschluss 10 sowie einem Auslassanschluss 11 steuerbar ist. Die Zylindertrommel 5 ist hierbei in Axialrichtung an dem Steuerspiegel 9 abgestützt, der an einem an dem Gehäuse 2 befestigten Gehäusedeckel 12 angeordnet ist.The displacement chambers 6 are in the radially inner region with a first connection channel 8a and a second connection channel 8b in connection, which are radially spaced. The connecting channels 8a, 8b are in operative connection with a disk-shaped control mirror body 9, wherein on the cylinder drum 5 facing end face of the control mirror body 9, a control surface 9a is formed. By means of the control plate 9, the connection of the displacement chambers 6 with an inlet port 10 and an outlet port 11 is controllable. The cylinder drum 5 is in this case supported in the axial direction on the control mirror 9, which is arranged on a housing cover 12 attached to the housing 2.

In den Verdrängerräumen 6 ist Flüssigkeit 15, insbesondere ionische Flüssigkeit, angeordnet.In the displacement chambers 6 liquid 15, in particular ionic liquid is arranged.

Jeder Verdrängerraum 6 steht mittels eines Verbindungskanals 13 mit einem Zylinderraum 16 einer als Axialkolbenmaschine in Schrägscheibenbauweise ausgebildeten hydraulischen Verdrängereinheit 17 in Verbindung. Die als Axialkolbenmaschine ausgebildete Verdrängereinheit 17 weist hierbei einen Zylinderblock 18 auf, der koaxial zu der Zylindertrommel 5 angeordnet und mit der Zylindertrommel 5 bzw. der Triebwelle 3 drehfest verbunden ist. Es ist ebenfalls möglich, den Zylinderblock 18 und die Zylindertrommel 5 als gemeinsame und somit einstückige Zylindertrommel auszubilden.Each displacer 6 is by means of a connecting channel 13 with a cylinder chamber 16 as an axial piston machine in swash plate design trained hydraulic displacer unit 17 in conjunction. The displacer unit 17 embodied as an axial piston machine in this case has a cylinder block 18 which is arranged coaxially with the cylinder drum 5 and is non-rotatably connected with the cylinder drum 5 or the drive shaft 3. It is also possible to form the cylinder block 18 and the cylinder drum 5 as a common and thus one-piece cylinder drum.

Die Zylinderräume 16 der Axialkobenmaschine sind von in dem Zylinderblock 18 konzentrisch angeordneten Längsbohrungen 20 gebildet, in denen jeweils ein Kolben 21 längsverschiebbar angeordnet sind. Die Kolben 21 sind mittels jeweils eines Gleitschuhs 22 an einer Schrägscheibe 23 abgestützt. Zwischen Kolben 21 und Gleitschuh 22 ist ein kugeliges Gleitschuhgelenk ausgebildet.The cylinder chambers 16 of the axial piston machine are formed by longitudinal bores 20 concentrically arranged in the cylinder block 18, in each of which a piston 21 is arranged to be longitudinally displaceable. The pistons 21 are supported by means of a respective sliding shoe 22 on a swash plate 23. Between piston 21 and shoe 22, a spherical Gleitschuhgelenk is formed.

Die Axialkolbenmaschine ist als im Verdrängervolumen verstellbare Axialkolbenmaschine ausgebildet, wobei die Schrägscheibe 23 am Gehäuse 2 schwenkbar gelagert ist und mittels einer nicht mehr dargestellten Stelleinrichtung bezüglich der Drehachse 4 neigbar ist. Es ist jedoch ebenfalls möglich, die Axialkolbenmaschine mit einem festen Verdrängervolumen auszubilden, wobei die Schrägscheibe unmittelbar am Gehäuse 2 ausgebildet werden kann.The axial piston machine is designed as an axial piston machine which can be adjusted in the displacement volume, wherein the swashplate 23 is pivotally mounted on the housing 2 and can be tilted relative to the axis of rotation 4 by means of an adjusting device which is no longer shown. However, it is also possible to form the axial piston machine with a fixed displacement volume, wherein the swash plate can be formed directly on the housing 2.

Die Zylindertrommel 5 und die Verdrängereinheit 17 sind hierbei in dem gemeinsamen Gehäuse angeordnet.The cylinder drum 5 and the displacer unit 17 are arranged in the common housing.

Bei einer Ausbildung der erfindungsgemäßen Verdrängereinheit 1 als Verdichter wird über die Triebwelle 3 die Zylindertrommel 5 und der Zylinderblock 18 angetrieben. Die Axialkolbenmaschine arbeitet hierbei als Pumpe und fördert Flüssigkeit 15 von den Zylinderräumen 16 in die Verdrängerräume 6, wodurch das über den den Niederdruck führenden Einlassanschluss 10 in die Verdrängerzylinder 6 einströmende Medium durch die Flüssigkeit 15 verdichtet und in den den Betriebsdruck führenden Auslassanschluss 11 gefördert wird.In one embodiment of the displacer unit 1 according to the invention as a compressor, the cylinder drum 5 and the cylinder block 18 are driven via the drive shaft 3. The axial piston machine operates as a pump and delivers liquid 15 from the cylinder chambers 16 into the displacement chambers 6, whereby the medium flowing into the displacement cylinders 6 via the inlet connection 10 carrying the low pressure is compressed by the liquid 15 and conveyed into the outlet connection 11 leading to the operating pressure.

Bei einer Ausbildung des erfindungsgemäßen Triebwerks 1 als Antriebsmaschine wird unter Druck stehendes Medium über den den Betriebsdruck führenden Einlassanschluss 10 den Verdrängerräumen 6 zugeführt. Über die Flüssigkeit 15 werden die Kolben 21 beaufschlagt, wobei die Axialkolbenmaschine als Motor betrieben wird und eine Drehbewegung der Zylindertrommel 5 und des Zylinderblocks 18 erzeugt wird, wodurch ein Drehmoment an der Triebwelle 3 abgegriffen werden kann.In an embodiment of the engine 1 according to the invention as a drive machine, pressurized medium is supplied to the displacement chambers 6 via the inlet connection 10 leading to the operating pressure. About the liquid 15, the piston 21 are acted upon, the axial piston engine as an engine is operated and a rotational movement of the cylinder drum 5 and the cylinder block 18 is generated, whereby a torque on the drive shaft 3 can be tapped.

In der Figur 2 ist der Steuerspiegelkörper 9 in einer Draufsicht auf die Steuerfläche 9a dargestellt. Der Steuerspiegelkörper 9 weist eine mit dem Einlassanschluss in Verbindung stehende erste Steueröffnung 20 auf, die nierenförmig ausgebildet ist. Eine zweite, am Steuerspiegelkörper 9 ausgebildete Steueröffnung 21, die ebenfalls nierenförmig ausgebildet ist, steht mit dem Auslassanschluss in Verbindung.In the FIG. 2 the control mirror body 9 is shown in a plan view of the control surface 9a. The control mirror body 9 has a first control opening 20 which is connected to the inlet connection and which is kidney-shaped. A second, on the control mirror body 9 formed control opening 21, which is also designed kidney-shaped, communicates with the outlet port in connection.

Die Steueröffnungen 20, 21 sind hierbei auf unterschiedlichen Teilkreisen radial voneinander beabstandet angeordnet. Der mit dem Verdrängerraum in Verbindung stehende erste Verbindungskanal 8a steuert hierbei die erste Steueröffnung 20 an. Der zweite Verbindungskanal 8b steuert die zweite Steueröffnung 21 an.The control openings 20, 21 are arranged radially spaced from each other on different pitch circles. In this case, the first connection channel 8a, which is in communication with the displacement chamber, controls the first control opening 20. The second connection channel 8b drives the second control opening 21.

An dem ersten Verbindungskanal 8a sowie dem zweiten Verbindungskanal 8b sind jeweils Gleitringdichtungen 22a, 22b zur Abdichtung des Verbindungskanals 8a, 8b gegenüber den Steueröffnungen 20, 21 angeordnet.On the first connecting channel 8a and the second connecting channel 8b, respective sliding ring seals 22a, 22b for sealing the connecting channel 8a, 8b with respect to the control openings 20, 21 are arranged.

Zur Abdichtung der ersten Steueröffnung 20 gegenüber der zweiten Steueröffnung 21 ist eine Dichteinrichtung 25 vorgesehen, die von einer ringförmigen Gleitringdichtung 25a gebildet ist.For sealing the first control opening 20 relative to the second control opening 21, a sealing device 25 is provided, which is formed by an annular mechanical seal 25a.

Die erste Steueröffnung 20 ist mittels einer weiteren Dichteinrichtung 26 gegenüber dem Gehäuseinnenraum abgedichtet, die als ringförmige Gleitringdichtung 26a ausgebildet ist. Zur Abdichtung der zweiten Steueröffnung 21 gegenüber der Triebwelle 3 und somit dem Gehäuseinnenraum ist eine weitere Dichteinrichtung 27 vorgesehen, die als ringförmige Gleitringdichtung 27a ausgebildet ist.The first control opening 20 is sealed by means of a further sealing device 26 with respect to the housing interior, which is formed as an annular mechanical seal 26a. For sealing the second control opening 21 with respect to the drive shaft 3 and thus the housing interior, a further sealing device 27 is provided, which is designed as an annular mechanical seal 27a.

Zwischen der radial innen angeordneten Dichteinrichtung 27 und der radial mittig angeordneten Dichteinrichtung 25 ist ein Ringraum 28 ausgebildet, in den die zweite Steueröffnung 21 mündet. Der Ringraum 28 ist somit von dem an der zweiten Steueröffnung 21 anstehenden Druck beaufschlagt. Zwischen der radial außen angeordneten Dichteinrichtung 26 und der radial mittig angeordneten Dichteinrichtung 25 ist ein weiterer Ringraum 29 gebildet, in dem die erste Steueröffnung 20 mündet, wodurch der Ringraum 29 von dem an der Steueröffnung 20 anstehenden Druck beaufschlagt ist.Between the radially inner sealing device 27 and the radially centrally disposed sealing device 25, an annular space 28 is formed, in which the second control port 21 opens. The annular space 28 is thus acted upon by the pending at the second control port 21 pressure. Between the radially outer sealing device 26 and the radially centrally disposed sealing device 25, a further annular space 29 is formed, in which the first control port 20 opens, whereby the annular space 29 is acted upon by the pending at the control port 20 pressure.

Der Steuerspiegelkörper 9 steht mit einer Stelleinrichtung 50, die beispielsweise als Stellzylinder 51 ausgebildet ist, in Wirkverbindung, mittels der der Steuerspiegelkörper 9 bezüglich der Drehachse 4 verdrehbar ist.The control mirror body 9 is connected to an adjusting device 50, which is formed for example as a control cylinder 51, in operative connection, by means of which the control mirror body 9 with respect to the rotation axis 4 is rotatable.

Wie aus der Figur 3 ersichtlich ist, sind die Gleitringdichtungen 22a, 22b der Verbindungskanäle 8a, 8b als Gleitringbuchsen ausgebildet, die in jeweils einer bohrungsförmigen Ausnehmung 30a, 30b des Verbindungskanals 8a, 8b angeordnet sind. Die Gleitringdichtungen 22a, 22b sind mittels einer in der Ausnehmung 30a, 30b angeordneten Feder 31 a, 31 b in Richtung zum Steuerspiegelkörper 9 beaufschlagt. An der in der Figur 3 linken Stirnseite der Gleitringdichtungen 22a, 22b ist eine Steuerfläche 32a, 32b ausgebildet, die die Gleitringdichtungen 22a, 22b in Richtung des Steuerspiegelkörpers 9 beaufschlagt. Die Steuerfläche 32a, 32b ist hierbei von dem in dem Verbindungskanal 8a, 8b anstehenden Druck beaufschlagt. Mittels eines O-Rings 33a, 33b, der zwischen der Ausnehmung 30a, 30b und der Gleitringdichtungen 22a, 22b angeordnet ist, sind die Verbindungskanäle 8a, 8b gegenüber den Ringräumen 28, 29 abgedichtet.Like from the FIG. 3 it can be seen, the mechanical seals 22a, 22b of the connecting channels 8a, 8b are formed as Gleitringbuchsen, which are arranged in a respective bore-shaped recess 30a, 30b of the connecting channel 8a, 8b. The mechanical seals 22a, 22b are acted upon by means disposed in the recess 30a, 30b spring 31 a, 31 b in the direction of the control mirror body 9. At the in the FIG. 3 The left end face of the mechanical seals 22a, 22b, a control surface 32a, 32b is formed, which urges the sliding ring seals 22a, 22b in the direction of the control mirror body 9. In this case, the control surface 32a, 32b is acted upon by the pressure present in the connecting channel 8a, 8b. By means of an O-ring 33a, 33b, which is arranged between the recess 30a, 30b and the mechanical seals 22a, 22b, the connecting channels 8a, 8b are sealed against the annular spaces 28, 29.

Die Dichteinrichtungen 25, 26, 27 sind als ringförmige Gleitringdichtungen 25a, 26a, 27a ausgebildet, die in ringförmigen Aussparungen 35, 36, 37 des Steuerspiegelkörpers 9 angeordnet sind. Die Gleitringdichtungen 25a, 26a, 27a sind hierbei mittels jeweils einer Feder 38, 39, 40, die in der entsprechenden Aussparung 35, 36, 37 angeordnet sind, in Richtung der Zylindertrommel 5 beaufschlagt. An den in der Figur 3 rechten Stirnseiten der Gleitringdichtungen 25a, 26a, 27a sind in Richtung der Zylindertrommel 5 wirkende Steuerflächen 41, 42, 43 ausgebildet. Die an der Dichteinrichtung 25 ausgebildete Steuerfläche 41 und die an der Dichteinrichtung 27 ausgebildete Steuerfläche 43 sind hierbei von dem im Ringraum 28 und somit dem an der Steueröffnung 21 anstehenden Druck beaufschlagt. Die an der Dichteinrichtung 26 ausgebildete Steuerfläche 42 ist von dem im Ringraum 29 und somit dem in der Steueröffnung 20 anstehenden Druck beaufschlagt.The sealing means 25, 26, 27 are formed as annular sliding ring seals 25a, 26a, 27a, which are arranged in annular recesses 35, 36, 37 of the control mirror body 9. The mechanical seals 25a, 26a, 27a are in this case by means of a respective spring 38, 39, 40, which are arranged in the corresponding recess 35, 36, 37, acted upon in the direction of the cylinder drum 5. At the in the FIG. 3 right end faces of the mechanical seals 25a, 26a, 27a are in the direction of the cylinder drum 5 acting control surfaces 41, 42, 43 are formed. The control surface 41 formed on the sealing device 25 and the control surface 43 formed on the sealing device 27 are acted upon here by the pressure prevailing in the annular space 28 and thus at the control opening 21. The formed on the sealing device 26 control surface 42 is acted upon by the pressure in the annular space 29 and thus in the control port 20 pending.

Am radial äußeren Bereich der Dichteinrichtung 25 ist zwischen der Dichteinrichtung 25 und der Aussparung 35 ein O-Ring 45 angeordnet, mittels der der Ringraum 28 von dem Ringraum 29 abgedichtet ist.At the radially outer region of the sealing device 25, an O-ring 45 is arranged between the sealing device 25 and the recess 35, by means of which the annular space 28 is sealed by the annular space 29.

Ein weiterer O-Ring 46 ist am radial äußeren Bereich der Dichteinrichtung 26 zwischen der Dichteinrichtung 26 und der Aussparung 36 angeordnet. Mittels des O-Rings 46 ist der Ringraum 29 gegenüber dem Gehäuseinnenraum angedichtet.Another O-ring 46 is arranged on the radially outer region of the sealing device 26 between the sealing device 26 and the recess 36. By means of the O-ring 46, the annular space 29 is sealed against the housing interior.

Am radial inneren Bereich der Dichteinrichtung 27 ist zwischen der Aussparung 37 und der Dichteinrichtung 27 ein O-Ring 47 angeordnet, mittels der der Ringraum 28 gegenüber dem Gehäuseinnenraum im Bereich der Triebwelle abgedichtet ist.At the radially inner region of the sealing device 27, an O-ring 47 is arranged between the recess 37 and the sealing device 27, by means of which the annular space 28 is sealed relative to the housing interior in the region of the drive shaft.

Beim Betrieb der erfindungsgemäßen Verdrängereinheit 1 als Verdichter ist der Einlassanschluss 10 mit Niederdruck beaufschlagt. Der Auslassanschluss 11 ist von dem erzeugten Betriebsdruck beaufschlagt. Im Ringraum 29, der über die erste Steueröffnung 20 mit dem Einlassanschluss 10 verbunden ist, steht somit der Niederdruck an. Der Ringraum 28, der über die zweite Steueröffnung 21 mit dem Auslassanschluss 11 verbunden ist, ist von dem erzeugten Hochdruck beaufschlagt. Die Verbindung der ersten Steueröffnung 20 mit dem Verdrängerraum 6 ist über den Verbindungskanal 8a gesteuert, wobei über die Gleitringdichtung 22a eine Abdichtung erzielt wird. Die Verbindung der zweiten Steueröffnung 21 mit dem Verdrängerraum 6 erfolgt über den Verbindungskanal 8b, wobei mittels der Gleitringdichtung 22b eine Abdichtung erzielt wird. Die Gleitringdichtungen 22a, 22b sind hierbei zusätzlich zu den Federn 31a, 31b von dem im Verdrängerraum 6 anstehenden Druck in Richtung zum Steuerspiegelkörper 9 beaufschlagt. Die zweite Steueröffnung 21 ist hierbei derart bemessen, dass jeweils lediglich ein Verdrängerraum 6 mit der Steueröffnung 21 in Verbindung steht. Mittels der Gleitringdichtung 22b wird hierbei ein Leckagestrom von dem mit der Steueröffnung 21 in Verbindung stehenden Verdrängerraum 6 zu den benachbarten Verdrängerräumen vermieden.When operating the displacer unit 1 according to the invention as a compressor, the inlet port 10 is subjected to low pressure. The outlet port 11 is acted upon by the generated operating pressure. In the annular space 29, which is connected via the first control port 20 to the inlet port 10, so is the low pressure. The annular space 28, which is connected via the second control opening 21 with the outlet port 11, is acted upon by the generated high pressure. The connection of the first control opening 20 with the displacement chamber 6 is controlled via the connecting channel 8a, wherein a seal is achieved via the mechanical seal 22a. The connection of the second control opening 21 with the displacement chamber 6 via the connecting channel 8b, wherein by means of the mechanical seal 22b, a seal is achieved. The mechanical seals 22a, 22b are acted upon here in addition to the springs 31a, 31b by the pressure in the displacement chamber 6 in the direction of the control mirror body 9. The second control opening 21 is in this case dimensioned such that in each case only one displacement chamber 6 communicates with the control opening 21. By means of the mechanical seal 22b in this case a leakage flow is avoided by the displacer 6 communicating with the control opening 21 to the adjacent displacement chambers.

Ein Leckagestrom von der ersten Steuerfläche 20 zur zweiten Steuerfläche 21 wird durch die Dichteinrichtung 25 vermieden, die von der Feder 38 und dem an der Steuerfläche 41 anstehenden Betriebsdruck in Richtung zur Zylindertrommel 5 beaufschlagt ist.A leakage flow from the first control surface 20 to the second control surface 21 is avoided by the sealing device 25, which is acted upon by the spring 38 and the pending on the control surface 41 operating pressure in the direction of the cylinder barrel 5.

Der Leckagestrom von der zweiten Steuerfläche 21 zum Gehäuseinnenraum im Bereich der Triebwelle 3 wird durch die Dichteinrichtung 27 vermieden, die zusätzlich zur Feder 40 von dem an der Steuerfläche 43 anstehenden Betriebsdruck in Richtung zur Zylindertrommel 5 beaufschlagt ist.The leakage flow from the second control surface 21 to the housing interior in the region of the drive shaft 3 is avoided by the sealing device 27, which is acted upon in addition to the spring 40 by the pending on the control surface 43 operating pressure in the direction of the cylinder drum 5.

Der Leckagestrom von der ersten Steuerfläche 20 zum Gehäuseinnenraum wird durch die Dichteinrichtung 26 vermieden, die von der Feder 39 und dem Niederdruck, der an der Steuerfläche 42 ansteht, in Richtung zur Zylindertrommel 5 beaufschlagt ist.The leakage flow from the first control surface 20 to the housing interior is avoided by the sealing device 26, which is acted upon by the spring 39 and the low pressure, which is present at the control surface 42, in the direction of the cylinder drum 5.

Durch die Gleitringdichtungen 22a, 22b sowie die als Gleitringdichtungen 25a, 26a, 27a ausgebildeten Dichteinrichtungen 25, 26, 27 kann somit ein Leckagestrom zwischen den Verdrängerräumen 6 sowie ein Leckagestrom zwischen den Steueröffnungen 20, 21 sowie ein Leckagestrom von den Steueröffnungen 20, 21 zum Gehäuseinnenraum wirksam vermieden werden.As a result of the mechanical seals 22a, 22b and the sealing devices 25, 26, 27 designed as mechanical seals 25a, 26a, 27a, a leakage flow between the displacement chambers 6 and a leakage flow between the control openings 20, 21 and a leakage flow from the control openings 20, 21 to the housing interior effectively avoided.

Die erfindungsgemäße Verdrängereinheit 1 ist aufgrund der verringerten Leckageströme für eine Betrieb bei hohen maximalen Betriebsdrücken geeignet, insbesondere für Betriebsdrücke bis zu 1000 bar, wobei die als Verdichter betriebene Verdrängereinheit einen geringen Energiebedarf und einen hohen Wirkungsgrad aufweist. Hierdurch kann die als Verdichter betriebene erfindungsgemäße Verdrängereinheit zum Verdichten von gasförmigen Medien, insbesondere Wasserstoff, verwendet werden.Due to the reduced leakage flows, the displacer unit 1 according to the invention is suitable for operation at high maximum operating pressures, in particular for operating pressures of up to 1000 bar, the displacer unit operated as a compressor having a low energy requirement and high efficiency. As a result, the displacer unit according to the invention operated as a compressor can be used for compressing gaseous media, in particular hydrogen.

Claims (20)

  1. Displacer unit having at least one displacer space (6) which is arranged in a cylinder drum (5) rotating about an axis of rotation and which can be connected by means of a control face (9a) to an inlet connection (10) and to an outlet connection (11), the control face (9a) being formed on a valve plate body (9) which is provided with a first control port (20) connected to the inlet connection (10) and with a second control port (21) connected to the outlet connection (11), the first control port (20) and the second control port (21) being spaced apart radially, characterized in that the displacer space (6) can be connected to the first control port (20) by means of a first connecting duct (8a) and to the second control port (21) by means of a second connecting duct (8b), and the connecting ducts (8a; 8b) are provided in each case with a floating ring seal (22a; 22b) for sealing off with respect to the control port (20; 21).
  2. Displacer unit according to Claim 1, characterized in that the floating ring seal (22a; 22b) is designed as a floating ring bush.
  3. Displacer unit according to Claim 1 or 2, characterized in that the floating ring seal (22a; 22b) can be loaded in the direction of the valve plate body (9) by means of a spring (31a; 31b).
  4. Displacer unit according to one of Claims 1 to 3, characterized in that the floating ring seal (22a; 22b) is provided with a control face (32a; 32b) acting in the direction of the valve plate body (9).
  5. Displacer unit according to Claim 4, characterized in that the control face (32a; 32b) can be acted upon by the pressure prevailing in the connecting duct (8a; 8b).
  6. Displacer unit according to one of Claims 1 to 5, characterized in that the floating ring seal (22a; 22b) is arranged in a bore-shaped recess (30a; 30b) of the connecting duct (8a; 8b).
  7. Displacer unit according to Claim 6, characterized in that the floating ring seal (22a; 22b) is sealed off with respect to the recess (30a; 30b) by means of an 0-ring (33a; 33b).
  8. Displacer unit according to one of Claims 1 to 7, characterized in that a sealing device (25) for sealing off the first control port (20) with respect to the second control port (21) and/or a sealing device (26) for sealing off the first control port (20) with respect to a housing inner space and/or a sealing device (27) for sealing off the second control port (21) -with respect to the housing inner space are provided.
  9. Displacer unit according to Claim 8, characterized in that the sealing device (25; 26; 27) is designed as a floating ring seal (25a; 26a; 27a).
  10. Displacer unit according to Claim 8 or 9, characterized in that the sealing device (25; 26; 27) can be loaded in the direction of the cylinder drum (5) by means of a spring (38; 39; 40).
  11. Displacer unit according to one of Claims 8 to 10, characterized in that the sealing device (25; 26; 27) is provided with a control face (41; 42; 43) acting in the direction of the cylinder drum (5).
  12. Displacer unit according to Claim 11, characterized in that the control face (41) of the sealing device (25) sealing off the first control port (20) with respect to the second control port (21) and the control face (43) of the sealing device (27) sealing off the second control port (21) with respect to the housing inner space can be acted upon by the pressure prevailing in the second control port (21), and the control face (42) of the sealing device (26) sealing off the first control port (20) with respect to the housing inner space can be acted upon by the pressure prevailing in the first control port (20).
  13. Displacer unit according to one of Claims 8 to 12, characterized in that the sealing device (25; 26; 27) is arranged in an annular clearance (35; 36; 37) of the valve plate body (9).
  14. Displacer unit according to Claim 13, characterized in that the sealing device (25; 26; 27) is sealed off with respect to the clearance (35; 36; 37) by means of an 0-ring (45; 46; 47).
  15. Displacer unit according to one of the preceding claims, characterized in that the control ports (20; 21) are designed as kidney-shaped control ports.
  16. Displacer unit according to one of the preceding claims, characterized in that the valve plate body (9) can be rotated with respect to the axis of rotation (4) by means of an actuating device (50), in particular an actuating piston.
  17. Displacer unit according to one of the preceding claims, characterized by its design as a compressor.
  18. Displacer unit according to one of Claims 1 to 16, characterized by its design as a motor.
  19. Displacer unit according to one of the preceding claims, characterized by its operation with liquids.
  20. Displacer unit according to one of Claims 1 to 18, characterized by its operation with gaseous media, in particular hydrogen.
EP06762814A 2005-08-04 2006-07-25 Displacer unit with a valve plate body Not-in-force EP1910674B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005036773A DE102005036773A1 (en) 2005-08-04 2005-08-04 Displacer unit with a control mirror body
PCT/EP2006/007331 WO2007014675A1 (en) 2005-08-04 2006-07-25 Displacer unit with a valve plate body

Publications (2)

Publication Number Publication Date
EP1910674A1 EP1910674A1 (en) 2008-04-16
EP1910674B1 true EP1910674B1 (en) 2009-03-04

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EP06762814A Not-in-force EP1910674B1 (en) 2005-08-04 2006-07-25 Displacer unit with a valve plate body

Country Status (10)

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US (1) US7765914B2 (en)
EP (1) EP1910674B1 (en)
JP (2) JP4986177B2 (en)
KR (1) KR20080034974A (en)
CN (1) CN101238290B (en)
AT (1) ATE424509T1 (en)
AU (1) AU2006275139A1 (en)
CA (1) CA2617672A1 (en)
DE (2) DE102005036773A1 (en)
WO (1) WO2007014675A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3258101B1 (en) 2016-06-14 2019-09-11 Medaxis Ag Pump module and device for producing a fluid jet
DE102017105610A1 (en) * 2017-03-16 2018-09-20 Volkswagen Aktiengesellschaft Axial piston motor and cycle device
DE102018216271A1 (en) * 2018-09-25 2020-03-26 Robert Bosch Gmbh Housing block, method for producing a housing block and core

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH348322A (en) 1954-11-24 1960-08-15 Reiners Walter Dr Ing Multi-cylinder device representing an oil pump or an oil motor
JPS554954B2 (en) * 1973-08-31 1980-02-01
JPS5818074U (en) * 1981-07-28 1983-02-03 三菱重工業株式会社 Axial plunger pump or motor
GB8916883D0 (en) * 1989-07-24 1989-09-06 Metal Box Plc Pumps
US5085127A (en) * 1990-03-29 1992-02-04 Sundstrand Corporation Cavitation resistant hydraulic cylinder block porting faces
US5109754A (en) * 1990-06-13 1992-05-05 Shaw Edwin L High torque low speed motor
JPH0482375U (en) * 1990-11-29 1992-07-17
DE4138174C2 (en) * 1991-11-21 1997-04-10 Linde Ag Piston pump
KR100254182B1 (en) * 1992-01-15 2000-04-15 매리 제이 캘라한 An axial piston fluid translating unit with sealed barrel plate
CN2155446Y (en) * 1993-03-20 1994-02-09 赖致平 Gas-liquid pump
US5576843A (en) * 1993-10-29 1996-11-19 Time Warner Entertainment Co., L.P. System and method for controlling play of multiple dialog audio tracks of a software carrier
US5778136A (en) * 1995-06-15 1998-07-07 Kabushiki Kaishi Toshiba Multi-scene recording medium wherein related data segments of simultaneously proceeding scenes are recorded alternatingly and continuously thereon
GB9517789D0 (en) * 1995-08-31 1995-11-01 Philips Electronics Uk Ltd Interactive entertainment content control
KR100223207B1 (en) * 1996-09-25 1999-10-15 윤종용 Digital video disk player of outputting multi-video
JP2000018149A (en) * 1998-07-03 2000-01-18 Komatsu Ltd Hydraulic piston pump
WO2001066341A1 (en) * 2000-03-07 2001-09-13 Amada Company, Limited Ram moving method for hydraulic machine, ram movement controller, method for preventing trapping of axial plunger pump used for the machine, and the pump
JP3855797B2 (en) * 2002-02-26 2006-12-13 松下電器産業株式会社 Paste discharge device
CN1187531C (en) * 2003-06-02 2005-02-02 浙江大学 Hydraulic transformer
DE10347085B3 (en) * 2003-10-10 2005-06-16 Brueninghaus Hydromatik Gmbh Hydrostatic piston machine with two hydraulic circuits

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ATE424509T1 (en) 2009-03-15
JP5393815B2 (en) 2014-01-22
DE502006003020D1 (en) 2009-04-16
DE102005036773A1 (en) 2007-02-08
CA2617672A1 (en) 2007-02-08
JP2012112388A (en) 2012-06-14
JP4986177B2 (en) 2012-07-25
AU2006275139A1 (en) 2007-02-08
CN101238290B (en) 2010-07-14
US7765914B2 (en) 2010-08-03
EP1910674A1 (en) 2008-04-16
JP2009503346A (en) 2009-01-29
KR20080034974A (en) 2008-04-22
WO2007014675A1 (en) 2007-02-08
CN101238290A (en) 2008-08-06
US20080246222A1 (en) 2008-10-09

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