EP0124032A2 - Radial piston compressor - Google Patents

Radial piston compressor Download PDF

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Publication number
EP0124032A2
EP0124032A2 EP84104429A EP84104429A EP0124032A2 EP 0124032 A2 EP0124032 A2 EP 0124032A2 EP 84104429 A EP84104429 A EP 84104429A EP 84104429 A EP84104429 A EP 84104429A EP 0124032 A2 EP0124032 A2 EP 0124032A2
Authority
EP
European Patent Office
Prior art keywords
guide ring
piston
pistons
cylinder block
radial
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.)
Withdrawn
Application number
EP84104429A
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German (de)
French (fr)
Other versions
EP0124032A3 (en
Inventor
Rudolf Schöning
Siegfried Schönwald
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP0124032A2 publication Critical patent/EP0124032A2/en
Publication of EP0124032A3 publication Critical patent/EP0124032A3/en
Withdrawn legal-status Critical Current

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    • 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
    • F04B27/06—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B27/0606—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary having cylinders in star- or fan-arrangement, the connection of the pistons with an actuating element being at the outer ends of the cylinders
    • F04B27/0612—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary having cylinders in star- or fan-arrangement, the connection of the pistons with an actuating element being at the outer ends of the cylinders rotary cylinder block
    • F04B27/0619—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary having cylinders in star- or fan-arrangement, the connection of the pistons with an actuating element being at the outer ends of the cylinders rotary cylinder block cylinder block and actuating cam rotating together

Definitions

  • the invention relates to a radial piston compressor with a cylinder block rotatably mounted on a fixed axis, which has at least two piston chambers, in each of which a radially reciprocable piston is arranged, in which compressor the radial movement of the pistons by a guide ring arranged eccentrically to the axis of rotation of the cylinder block is controlled, on which the pistons are supported directly or via an intermediate part.
  • Such a compressor is known from DE-OS 31 20 812.
  • the pistons are supported on the guide ring by balls.
  • the guide ring is rotatably arranged, there is nevertheless a relative movement between the balls and the guide ring, which causes the guide ring to wear and fatigue accordingly.
  • the invention has for its object to develop a radial piston compressor of the type described above so that the life of the guide ring can be increased despite the wear and fatigue of the guide ring.
  • the object is achieved according to the invention in that the support points of the pistons or the intermediate parts on the guide ring lie on axially offset circumferential planes. Such an axial offset distributes the stress to different locations on the guide ring, so that the guide ring can be operated for a longer period of time without causing malfunctions due to wear and fatigue.
  • the axial offset of the support points is achieved in a particularly simple manner in that the piston spaces within the cylinder block are axially offset from one another.
  • the axial displacement of the piston chambers also ensures that the support forces always act vertically on the guide ring and thus no transverse components occur.
  • a further increase in the service life of radial piston compressors, in which the pistons are supported on the guide ring by balls, is possible in that several guide grooves are provided on the guide ring which are axially offset according to the axial displacement of the piston chambers. With such guide grooves, the osculation between the balls and the guide ring is improved and the load is thereby distributed over a larger area.
  • a cylinder block 2 is rotatably arranged on a fixed axis 1.
  • the cylinder block 2 has a plurality of cylindrical piston spaces 3 distributed uniformly over its circumference.
  • a freely movable piston 4 is arranged in each piston chamber 3 and is supported in each case on a guide ring 6 via a ball 5.
  • the guide ring 6 is in turn on a bell-shaped Carrying part 7 attached, which is rotatably mounted on an axis piece 8 offset on one side relative to the axis 1.
  • Arms 9 connected to the cylinder block 2 couple it to a drive motor.
  • the pistons 4 are moved back and forth in the piston chambers 3.
  • the medium to be compressed is sucked in via a suction line 10 formed in the axis extension 8 and in the axis 1 and is ejected via a pressure line 11 likewise formed in the axis extension 8 and in the axis 1.
  • the two piston spaces 3 shown in the drawing are axially offset from one another by the distance A.
  • the support points 12 and 13 of the two balls 5 on the guide ring 6 lie on different axially offset rotational levels.
  • the distance A is chosen so large that the deformation or stress fields of the individual raceways resulting from the pressure of the balls only touch or overlap with their weaker edge zones. This is the case when the distance A is about 4 to 10 of the ball diameter.
  • the tread 14 of the guide ring 6 is formed in a groove shape.
  • the balls 5 are thus with a larger area on the guide ring 6, so that this reduces the specific pressing forces.
  • the balls 5 rotating in each plane can also be assigned a separate guide groove.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)

Abstract

The compressor comprises a cylinder block (2), which is rotatably mounted on a fixed axis (1) and has at least two piston chambers (3), in each of which a radially reciprocating piston (4) is arranged. The radial movement of the pistons (4) is controlled in the compressor by a guide ring (6) arranged eccentrically with respect to the axis of rotation of the cylinder block (2). The pistons (4) are supported against the guide ring (6) either directly or via an intermediate part (5). An increase in the service life of the guide ring (6) is achieved by the support points (12 and 13) on the guide ring (6) lying on orbital planes offset axially with respect to each other. <IMAGE>

Description

Die Erfindung betrifft einen Radialkolbenverdichter mit einem auf einer feststehenden Achse drehbar gelagerten Zylinderblock, der mindestens zwei Kolbenräume aufweist, in denen jeweils ein radial hin- und herbewegbarer Kolben angeordnet ist, bei welchem Verdichter die Radialbewegung der Kolben durch einen exzentrisch zur Drehachse des Zylinderblockes angeordneten Führungsring gesteuert ist, an dem die Kolben direkt oder über ein Zwischenteil abgestützt sind.The invention relates to a radial piston compressor with a cylinder block rotatably mounted on a fixed axis, which has at least two piston chambers, in each of which a radially reciprocable piston is arranged, in which compressor the radial movement of the pistons by a guide ring arranged eccentrically to the axis of rotation of the cylinder block is controlled, on which the pistons are supported directly or via an intermediate part.

Ein solcher Verdichter ist durch die DE-OS 31 20 812 bekannt. Die Kolben sind bei diesem Verdichter über Kugeln an dem Führungsring abgestützt. Obwohl der Führungsring drehbar angeordnet ist, findet dennoch eine Relativbewegung zwischen den Kugeln und dem Führungsring statt, durch die eine entsprechende Abnutzung und Ermüdung des Führungsringes verursacht wird.Such a compressor is known from DE-OS 31 20 812. In this compressor, the pistons are supported on the guide ring by balls. Although the guide ring is rotatably arranged, there is nevertheless a relative movement between the balls and the guide ring, which causes the guide ring to wear and fatigue accordingly.

Der Erfindung liegt die Aufgabe zugrunde, einen Radialkolbenverdichter der eingangs beschriebenen Art so weiterzubilden, daß trotz der Abnutzung und Ermüdung des Führungsringes die Lebensdauer des Führungsringes erhöht werden kann.The invention has for its object to develop a radial piston compressor of the type described above so that the life of the guide ring can be increased despite the wear and fatigue of the guide ring.

Die Lösung der gestellten Aufgabe gelingt nach der Erfindung dadurch, daß die Abstützpunkte der Kolben bzw. der Zwischenteile an dem Führungsring auf axial gegeneinander versetzten Umlaufebenen liegen. Durch einen solchen axialen Versatz wird die Beanspruchung auf verschiedene Stellen des Führungsringes verteilt, so daß der Führungsring länger in Betrieb sein kann, ohne daß durch die Abnutzung und Ermüdung Störungen hervorgerufen werden.The object is achieved according to the invention in that the support points of the pistons or the intermediate parts on the guide ring lie on axially offset circumferential planes. Such an axial offset distributes the stress to different locations on the guide ring, so that the guide ring can be operated for a longer period of time without causing malfunctions due to wear and fatigue.

Der axiale Versatz der Abstützpunkte wird in besonders einfacher Weise dadurch erreicht, daß die Kolbenräume innerhalb des Zylinderblockes axial gegeneinander versetzt sind. Durch das axiale Versetzen der Kolbenräume wird außerdem erreicht, daß die Abstützkräfte stets senkrecht auf dem Führungsring angreifen und somit keine Querkomponenten auftreten.The axial offset of the support points is achieved in a particularly simple manner in that the piston spaces within the cylinder block are axially offset from one another. The axial displacement of the piston chambers also ensures that the support forces always act vertically on the guide ring and thus no transverse components occur.

Bei Radialkolbenverdichtern mit einer geraden Anzahl von Kolbenräumen, die größer als 2 ist, kann ein Ausgleich der freien Massenkräfte dadurch erzielt werden, daß jeweils diametral gegenüberliegende Kolbenräume in der gleichen Umlaufebene angeordnet sind. Dadurch können an dem Führungsring keine Kippmomente auftreten. Im übrigen können die Kippmomente der Massenkräfte auch durch an dem Zylinderblock angebrachte Ausgleichsgewichte ausgeglichen werden.In the case of radial piston compressors with an even number of piston chambers which is greater than 2, a compensation of the free mass forces can be achieved in that diametrically opposite piston chambers are arranged in the same revolving plane. As a result, no tilting moments can occur on the guide ring. In addition, the tilting moments of the mass forces can also be compensated for by counterweights attached to the cylinder block.

Eine weitere Erhöhung der Lebensdauer ist bei Radialkolbenverdichtern, bei denen die Kolben über Kugeln an dem Führungsring abgestützt sind, dadurch möglich, daß an dem Führungsring mehrere, dem axialen Versatz der Kolbenräume entsprechend axial versetzte Führungsrillen vorgesehen sind. Durch derartige Führungsrillen wird die Schmiegung zwischen den Kugeln und dem Führungsring verbessert und dadurch die Belastung auf eine größere Fläche verteilt.A further increase in the service life of radial piston compressors, in which the pistons are supported on the guide ring by balls, is possible in that several guide grooves are provided on the guide ring which are axially offset according to the axial displacement of the piston chambers. With such guide grooves, the osculation between the balls and the guide ring is improved and the load is thereby distributed over a larger area.

Anhand eines in der Zeichnung dargestellten Ausführungsbeispiels wird die Erfindung nachfolgend näher beschrieben.The invention is described in more detail below on the basis of an exemplary embodiment shown in the drawing.

Auf einer feststehenden Achse 1 ist ein Zylinderblock 2 drehbar angeordnet. Der Zylinderblock 2 weist mehrere gleichmäßig über dessen Umfang verteilte zylinderische Kolbenräume 3 auf. In jedem Kolbenraum 3 ist ein freibeweglicher Kolben 4 ängeordnet, der jeweils über eine Kugel 5 an einem Führungsring 6 abgestützt ist. Der Führungsring 6 ist seinerseits an einem glockenförmigen Tragteil 7 befestigt, welches auf einem gegenüber der Achse 1 einseitig versetzten Achsstück 8 drehbar gelagert ist.A cylinder block 2 is rotatably arranged on a fixed axis 1. The cylinder block 2 has a plurality of cylindrical piston spaces 3 distributed uniformly over its circumference. A freely movable piston 4 is arranged in each piston chamber 3 and is supported in each case on a guide ring 6 via a ball 5. The guide ring 6 is in turn on a bell-shaped Carrying part 7 attached, which is rotatably mounted on an axis piece 8 offset on one side relative to the axis 1.

Ober mit dem Zylinderblock 2 verbundene Arme 9 ist dieser mit einem Antriebsmotor gekuppelt. Infolge der exzentrischen Anordnung des Zylinderblockes 2 gegenüber dem Tragteil 7 werden die Kolben 4 in den Kolbenräumen 3 hin-und herbewegt. Dabei wird über eine in dem Achsansatz 8 und in der Achse 1 ausgebildete Ansaugleitung 10 das zu verdichtende Medium angesaugt und über eine ebenfalls in dem Achsansatz 8 und in der Achse 1 ausgebildete Druckleitung 11 ausgestoßen.Arms 9 connected to the cylinder block 2 couple it to a drive motor. As a result of the eccentric arrangement of the cylinder block 2 relative to the supporting part 7, the pistons 4 are moved back and forth in the piston chambers 3. In this case, the medium to be compressed is sucked in via a suction line 10 formed in the axis extension 8 and in the axis 1 and is ejected via a pressure line 11 likewise formed in the axis extension 8 and in the axis 1.

Die beiden in der Zeichnung dargestellten Kolbenräume 3 sind um den Abstand A axial gegeneinander versetzt. Dadurch liegen die Abstützpunkte 12 und 13 der beiden Kugeln 5 an dem Führungsring 6 auf verschiedenen axial gegeneinander versetzten Umlaufebenen. Der Abstand A ist so groß gewählt, daß die von dem Druck der Kugeln herrührenden Verformungs- bzw. Spannungsfelder der einzelnen Laufbahnen sich nur mit ihren schwächeren Randzonen berühren bzw. überdecken. Dies ist dann der Fall, wenn der Abstand A etwa 4 bis 10 des Kugeldurchmessers beträgt.The two piston spaces 3 shown in the drawing are axially offset from one another by the distance A. As a result, the support points 12 and 13 of the two balls 5 on the guide ring 6 lie on different axially offset rotational levels. The distance A is chosen so large that the deformation or stress fields of the individual raceways resulting from the pressure of the balls only touch or overlap with their weaker edge zones. This is the case when the distance A is about 4 to 10 of the ball diameter.

Um die Schmiegung zwischen den Kugeln 5 und dem Führungsring 6 zu verbessern, ist die Lauffläche 14 des Führungsringes 6 rillenförmig ausgebildet. Die Kugeln 5 liegen dadurch mit einer größeren Fläche an dem Führungsring 6 an, so daß hierdurch die spezifischen Andrückkräfte reduziert werden.In order to improve the osculation between the balls 5 and the guide ring 6, the tread 14 of the guide ring 6 is formed in a groove shape. The balls 5 are thus with a larger area on the guide ring 6, so that this reduces the specific pressing forces.

Infolge des axialen Versatzes der Kolbenräume 3 um den Abstand A wird die Anzahl der örtlichen Uberrollungen an dem Führungsring 6 je Umdrehung des Zylinderblockes 2 umgekehrt proportional zur Anzahl der Umlaufebenen herabgesetzt. Die Ermüdungslebensdauer des Führungsringes steigt damit praktisch proportional zu der Anzahl der Laufbahnen an.As a result of the axial offset of the piston chambers 3 by the distance A, the number of local rollovers on the guide ring 6 per revolution of the cylinder block 2 is reduced in inverse proportion to the number of revolving planes. The fatigue life of the guide ring increases practically in proportion to the number of raceways.

Bei einem Radialkolbenverdichter mit vier Kolbenräumen 3 je Zylinderblock 2 können alle vier Kolbenräume axial gegeneinander versetzt werden. Jedoch ist es zweckmäßig, jeweils zwei diametral gegenüberliegende Kolbenräume 3 in der gleichen Umlaufebene anzuordnen, da dann ohne weiteres ein Ausgleich der freien Massenkräfte erfolgt. Damit erhält man für einen solchen Radialkolbenverdichter zwei Laufbahnen der Kugeln 5 an dem Führungsring 6. Dies bedeutet, daß die Lebensdauer des Führungsringes 6 etwa verdoppelt ist.In a radial piston compressor with four piston chambers 3 per cylinder block 2, all four piston chambers can be axially offset from one another. However, it is expedient to arrange two diametrically opposite piston chambers 3 in the same circumferential plane, since the free mass forces are then easily compensated for. This results in two raceways of the balls 5 on the guide ring 6 for such a radial piston compressor. This means that the service life of the guide ring 6 is approximately doubled.

Anstelle einer gemeinsamen Bahn in dem Führungsring 6 für die in den verschiedenen Ebenen umlaufenden Kugeln 5 kann den jeweils in einer Ebene umlaufenden Kugeln 5 auch eine eigene Führungsrille zugeordnet werden.Instead of a common path in the guide ring 6 for the balls 5 rotating in the different planes, the balls 5 rotating in each plane can also be assigned a separate guide groove.

Claims (5)

1. Radialkolbenverdichter mit einem auf einer feststehenden Achse drehbar gelagerten Zylinderblock, der mindestens zwei Kolbenräume aufweist, in denen jeweils ein radial hin-und herbewegbarer Kolben angeordnet ist, bei welchem Verdichter die Radialbewegung der Kolben durch einen exzentrisch zur Drehachse des Zylinderblockes angeordneten Führungsring gesteuert ist, an dem die Kolben direkt oder über ein Zwischenteil abgestützt sind, dadurch gekennzeichnet, daß die Abstützpunkte (12 und 13) der Kolben (4) bzw. der Zwischenteile (5) an dem Führungsring (6) auf axial gegeneinander versetzten Umlaufebenen liegen.1. Radial piston compressor with a cylinder block rotatably mounted on a fixed axis, which has at least two piston chambers, in each of which a radially reciprocable piston is arranged, in which compressor the radial movement of the pistons is controlled by a guide ring arranged eccentrically to the axis of rotation of the cylinder block , on which the pistons are supported directly or via an intermediate part, characterized in that the support points (12 and 13) of the pistons (4) or the intermediate parts (5) lie on the guide ring (6) on axially offset circumferential planes. 2. Radialkolbenverdichter nach Anspruch 1, dadurch gekennzeichnet, daß die Kolbenräume (3) innerhalb des Zylinderblockes (2) axial gegeneinander versetzt sind.2. Radial piston compressor according to claim 1, characterized in that the piston chambers (3) within the cylinder block (2) are axially offset from one another. 3. Radialkolbenverdichter nach Anspruch 1 oder 2 mit einer geraden Anzahl von Kolbenräumen, die größer als zwei ist, dadurch gekennzeichnet, daß jeweils diametral gegenüberliegende Kolbenräume (3) in der gleichen Umlaufebene angeordnet sind.3. Radial piston compressor according to claim 1 or 2 with an even number of piston chambers, which is greater than two, characterized in that diametrically opposite piston chambers (3) are arranged in the same circulation plane. 4. Radialkolbenverdichter nach Anspruch 2 oder 3, bei dem die Kolben über Kugeln an dem Führungsring abgestützt sind, dadurch gekennzeichnet, daß an dem Führungsring (6) mehrere, dem axialen Versatz der Kolbenräume (3) entsprechend axial versetzte. Führungsrillen vorgesehen sind.4. A radial piston compressor according to claim 2 or 3, in which the pistons are supported on the guide ring by balls, characterized in that on the guide ring (6) a plurality of axially offset the axial displacement of the piston chambers (3) accordingly. Guide grooves are provided. 5. Radialkolbenverdichter nach Anspruch 4, dadurch gekennzeichnet, daß der axiale Versatz der Kolbenräume (3) und der Führungsrillen 4 bis 10 % des Kugeldurchmessers beträgt.5. Radial piston compressor according to claim 4, characterized in that the axial offset of the piston chambers (3) and the guide grooves is 4 to 10% of the ball diameter.
EP84104429A 1983-05-03 1984-04-18 Radial piston compressor Withdrawn EP0124032A3 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3316106 1983-05-03
DE19833316106 DE3316106A1 (en) 1983-05-03 1983-05-03 RADIAL PISTON COMPRESSORS

Publications (2)

Publication Number Publication Date
EP0124032A2 true EP0124032A2 (en) 1984-11-07
EP0124032A3 EP0124032A3 (en) 1984-12-05

Family

ID=6198021

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84104429A Withdrawn EP0124032A3 (en) 1983-05-03 1984-04-18 Radial piston compressor

Country Status (4)

Country Link
EP (1) EP0124032A3 (en)
JP (1) JPS59208178A (en)
DE (1) DE3316106A1 (en)
DK (1) DK86084A (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR566061A (en) * 1923-05-12 1924-02-08 Rotary compressors
US1939057A (en) * 1930-02-24 1933-12-12 Arthur J Kercher Compressor
US2504841A (en) * 1944-11-03 1950-04-18 U S Thermo Control Co Rotary compressor
DE3120812A1 (en) * 1981-05-25 1982-12-23 Siemens AG, 1000 Berlin und 8000 München RADIAL PISTON COMPRESSORS

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR566061A (en) * 1923-05-12 1924-02-08 Rotary compressors
US1939057A (en) * 1930-02-24 1933-12-12 Arthur J Kercher Compressor
US2504841A (en) * 1944-11-03 1950-04-18 U S Thermo Control Co Rotary compressor
DE3120812A1 (en) * 1981-05-25 1982-12-23 Siemens AG, 1000 Berlin und 8000 München RADIAL PISTON COMPRESSORS

Also Published As

Publication number Publication date
JPS59208178A (en) 1984-11-26
DK86084A (en) 1984-11-04
EP0124032A3 (en) 1984-12-05
DK86084D0 (en) 1984-02-22
DE3316106A1 (en) 1984-11-08

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