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EP0017100B1 - Verfahren und Einrichtung zur Schmiermittelzuführung an einer Kolben-Zylinderanordnung - Google Patents

Verfahren und Einrichtung zur Schmiermittelzuführung an einer Kolben-Zylinderanordnung Download PDF

Info

Publication number
EP0017100B1
EP0017100B1 EP80101491A EP80101491A EP0017100B1 EP 0017100 B1 EP0017100 B1 EP 0017100B1 EP 80101491 A EP80101491 A EP 80101491A EP 80101491 A EP80101491 A EP 80101491A EP 0017100 B1 EP0017100 B1 EP 0017100B1
Authority
EP
European Patent Office
Prior art keywords
lubricant
piston
cylinder
sealing element
pressure
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.)
Expired
Application number
EP80101491A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0017100A2 (de
EP0017100A3 (en
Inventor
Bernhard Frey
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.)
Hydrowatt Systems Ltd
Original Assignee
Hydrowatt Systems Ltd
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 Hydrowatt Systems Ltd filed Critical Hydrowatt Systems Ltd
Priority to AT80101491T priority Critical patent/ATE12044T1/de
Publication of EP0017100A2 publication Critical patent/EP0017100A2/de
Publication of EP0017100A3 publication Critical patent/EP0017100A3/de
Application granted granted Critical
Publication of EP0017100B1 publication Critical patent/EP0017100B1/de
Expired legal-status Critical Current

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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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members
    • F04B43/084—Machines, pumps, or pumping installations having flexible working members having tubular flexible members the tubular member being deformed by stretching or distortion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/16—Controlling lubricant pressure or quantity

Definitions

  • the invention relates to a method for supplying lubricant according to the preamble of claim 1 and to an associated device according to the preamble of claim 4.
  • a method and a device of the aforementioned type are known from DE-A-2 554 733.
  • the known support of a tubular sealing element via a lubricant on a cylindrical support surface is carried out with lubricant supply even during the pressure working strokes, ie. H. the strokes with decreasing working space volume when pump is operating or with increasing working space volume when motor is operating.
  • the supply takes place, for example, by pressing in a quantity flow that is more or less independent of the counter pressure and then leaves the lubricant chamber via a throttle point in a low pressure chamber.
  • working pressure irrespective of the fluctuations in the pressure in the working space (hereinafter referred to as "working pressure"), a balance can be achieved between this and the pressure in the lubricant space, thus avoiding direct contact or mixed friction between the sealing element and the support surface.
  • working pressure a pressure in the working space
  • a pump pressure which is in any case above the maximum values of the working pressure, as well as a suitable control or regulation of the supply volume flow. This is associated with a comparatively high outlay.
  • lubricant supply devices for arrangements without a soft-elastic sealing element at all or without such for sealing a working space of a piston-cylinder arrangement are known. These devices are furthermore the present invention as the aforementioned prior art.
  • the FR-A is only a mechanical lubrication without lubricant support of a flexible sealing element on a working area of a piston-cylinder arrangement. Accordingly, there is no basis for sizing the lubricant supply pressure with respect to a working pressure as in the invention.
  • the object of the invention is therefore to provide a method or a device for supplying lubricant to a piston-cylinder arrangement with a flexible sealing element of the type mentioned, which basically manages with a lower lubricant supply pressure with respect to the working pressure and does not control or regulate a constant flow rate in the Lubricant supply required.
  • the solution to this problem according to the invention is characterized in terms of the method and the device by the features specified in claim 1 and in claim 4.
  • a quantity of lubricant can be introduced into the lubricant space between the sealing element and the support surface with a comparatively low supply pressure in time intervals with a comparatively low working pressure, which, taking into account the throttled outflow, is sufficient for reliable support of the sealing element without contact or mixed friction on the support surface.
  • a backflow into the lower-pressure lubricant supply device is expediently prevented by a check valve arrangement, so that the required balance between the lubricant pressure and the working pressure on the sealing element can be established quickly.
  • the advantage of particular simplicity is that an at least approximately constant time profile of the lubricant supply pressure which is independent of the working strokes of the piston-cylinder arrangement can be provided.
  • this enables a common lubricant supply for a multiple-piston-cylinder arrangement with a corresponding plurality of sealing elements in a simple manner.
  • the lubricant supply pressure has a time course which is synchronous with respect to the periodic change in the working space of the piston-cylinder arrangement, with maximum values in working stroke ranges between the maximum values of the working pressure, i. H. at low working pressures.
  • Such an embodiment is particularly suitable for arrangements with only one sealing element or a small number of such elements, it being possible for a lubricant pump to be coupled to the drive of the piston-cylinder pair in question.
  • An essential formation of the device according to the invention is characterized in that the check valve arrangement has at least one valve member arranged in the area of the lubricant supply opening in the lubricant chamber.
  • This arrangement of the Ven valve member of the check valve arrangement results in a particularly low-inertia locking of the lubricant supply channel when the increase in working pressure begins.
  • very high working pressures which take into account the compressibility of the lubricant and the elastic resilience of the feed lines and other feed elements would require a significant relief of the entire feed device and avoid a reduction in the lubricant volume effective for the Ahstiit tion, thus securing the sealing element against contact with the unevenness of the lubricant feed opening and thus against damage .
  • a cylinder 1 as the first working member and a piston 2 as the second working member are connected to one another via a tubular sealing element 3, which is supported on a cylindrical support surface 4 of the first working member.
  • the support surface 4 forms a transition surface section 4a which is curved in a toroidal shape.
  • the connection area 3a is integrally connected, for example by vulcanization, to an intermediate ring 1a of the cylinder 1. In this connection area is the mouth of the lubricant supply, which is yet to be explained.
  • the sealing element is also cohesive, connected to a conical surface of the piston 2.
  • a helical compression spring 2a presses the shaft 2b, which is displaceably guided in the cylinder 1, downward against an oscillating drive member, so that the working space 5 formed within the sealing element is reduced during a movement according to arrow X.
  • the piston 2 assumes its lowest position with a maximum working volume.
  • the work space is connected by a cover 6 with feed and discharge line 6a to a valve arrangement (not shown) for a mode of operation of the device as a pump.
  • a gap-shaped lubricant chamber 3b of small radial thickness, the lubricant filling of which excludes contact between the sealing element and the support surface during the oscillating longitudinal expansion of the sealing element in accordance with the piston movement.
  • a motor unit 7 with a drive shaft 7a and cam 7b is provided, against which the piston shaft 2b is pressed against by the pressure unit 2a.
  • a lubricant supply device with a pump 8 is provided via a schematically indicated shaft 8a and a cam 8b coupled.
  • a check valve 8d can be inserted in the lubricant supply line 8c, but preferably the mouth 9 of the lubricant supply is provided with a low-inertia check valve member 15.
  • the lubricant supply mouth 9 is located on the underside of an annular body 10 provided with corresponding passage grooves, which forms the transition surface section 4a on its upper side.
  • the diagrams in FIG. 2 relate to an operation of the piston-cylinder arrangement as a pump, ie with a high working pressure with decreasing working space volume.
  • Diagram (a) shows the course of the stroke h A of the working piston 2 and the pump stroke h z of the lubricant supply pump over the time t. This method of operation corresponds to a synchronized lubricant supply in the working strokes with increasing work space volume.
  • the associated course of the lubricant supply pressure p z is indicated in curve B of diagram (b). This supply allows a comparatively low maximum supply pressure pzi.
  • the time course of the lubricant mass flow v z is indicated in curve B in diagram (c).
  • an asynchronous lubricant supply can be used, for example with an essentially constant supply pressure p zo according to line A in diagram (b).
  • p zo essentially constant supply pressure
  • FIG. 3a and 3b show the design of the lubricant supply mouth with check valve on the end face 10a of the ring body 10 in detail.
  • a radical channel 11 in the cylinder 1 a circumferential distributor groove 12 on the ring body 10 and a plurality of radial feed grooves 13 within the end face 10a are connected to the feed line 8c.
  • the radial feed grooves 13 open into an inner circumferential groove 14 between the ring body 10 and the cylinder 1, which acts as an end distributor for the lubricant supply into the gap 3b.
  • the mouth 9 itself is formed by a circumferential groove with a flat triangular cross section det, in which an annular, radially deformable valve member 15 is inserted.
  • the base side 15a of the ring cross section facing the sealing element 3 has a width b which is dimensioned substantially greater than the radial cross-sectional height d, so that rear side surfaces 15b of the ring are inclined at an acute angle to the cylindrical part of the support surface 4.
  • the annular valve member 15 is deformed radially inward, as is indicated by the broken line in FIG. 3a. This results in passage channels which open into the lubricant chamber 3b at an acute angle on the rear side surfaces 15b of the ring and which close again automatically when the working pressure is predominant and radially expand the ring outwards.
  • the annular valve member can optionally consist of a deformation-resistant but comparatively flexible material, in particular of a sliding-friendly plastic, so that small pressure differences are sufficient for rapid valve actuation and, in addition, only a slight stress on the surface of the sealing element occurs when it comes into contact with the valve member.
  • the low mass of the annular valve member also contributes to a low-inertia function.
  • annular extension 15c which extends in the circumferential direction and engages flush in the circumferential groove 14 and secures the valve member against axial displacement.
  • recesses 15d are provided in the annular extension 15c, which engage radially inwards in the region of the rear side surfaces 15b.
  • the lubricant can pass from the circumferential groove 14 into the passageways formed on the rear side surfaces 15b in the case of radial inward deformation when the radial inward deformation has only reached a small degree. This also contributes to a low-delay function of the check valve.
  • a circumferential distributor groove 22 as well as radical channels 23 and an end distributor groove 24 adjoin the feed line 8c and the radical channel 11 within the right end face of an annular body 20.
  • the transition surface section 4a is formed by an annular valve member 25, which is separated from the ring body 20 and is axially displaceable because of the deformability of the sealing element connecting region 3a and which closes the lubricant supply opening with its rear surface 25a when the working pressure exceeds the lubricant supply pressure.
  • the valve member 25 is axially displaced to the left in the sense of FIG. 4, the lower section of the rear surface 25a clears the passage into the lubricant chamber 3b.
  • the annular valve member 25 can also have a radial deformability instead of or possibly in addition to its axial displacement, which can be easily achieved by appropriate choice of material.
  • the cross section of the ring body can easily twist during the inward deformation in such a way that the inner edge region of the rear side surface 25a lifts off the cylinder, while the outer region of the ring continues to be supported. In this way, a slight deformation of the ring body is sufficient for the valve actuation.
  • an axially displaceable, annular valve member 35 is provided, which rests with its right end face 35a in the flowing state on a corresponding, flat end face of the cylinder 1 and is displaced to the left under the effect of the lubricant supply pressure for opening.
  • the valve member is fitted radially into a spacer ring 36, which has circumferential distributor grooves 32a and 32b on its right end face and radial channels 33 for the passage of the lubricant to the right end face of the valve member 35.
  • Such an embodiment is also particularly suitable for the use of non-deformable, wearable materials for the valve member 35.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Sealing Devices (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP80101491A 1979-04-06 1980-03-21 Verfahren und Einrichtung zur Schmiermittelzuführung an einer Kolben-Zylinderanordnung Expired EP0017100B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80101491T ATE12044T1 (de) 1979-04-06 1980-03-21 Verfahren und einrichtung zur schmiermittelzufuehrung an einer kolbenzylinderanordnung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH326279A CH642145A5 (de) 1979-04-06 1979-04-06 Verfahren und einrichtung zur schmiermittelzufuehrung an einer kolben-zylinderanordnung.
CH3262/79 1979-04-06

Publications (3)

Publication Number Publication Date
EP0017100A2 EP0017100A2 (de) 1980-10-15
EP0017100A3 EP0017100A3 (en) 1981-01-07
EP0017100B1 true EP0017100B1 (de) 1985-03-06

Family

ID=4252169

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80101491A Expired EP0017100B1 (de) 1979-04-06 1980-03-21 Verfahren und Einrichtung zur Schmiermittelzuführung an einer Kolben-Zylinderanordnung

Country Status (15)

Country Link
US (1) US4384510A (xx)
EP (1) EP0017100B1 (xx)
JP (1) JPS55139594A (xx)
AR (1) AR223868A1 (xx)
AT (1) ATE12044T1 (xx)
AU (1) AU540832B2 (xx)
BR (1) BR8002065A (xx)
CH (1) CH642145A5 (xx)
CS (1) CS258459B2 (xx)
DD (1) DD150102A5 (xx)
DE (1) DE3070250D1 (xx)
HU (1) HU182116B (xx)
MX (1) MX153130A (xx)
PL (1) PL130978B1 (xx)
ZA (1) ZA801966B (xx)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6022195B2 (ja) * 1982-01-22 1985-05-31 義一 山谷 高圧流体発生装置
DE102004027511A1 (de) * 2004-06-04 2005-12-22 Robert Bosch Gmbh Leckagefreie Kolbenpumpe
DE102013014930A1 (de) * 2013-09-11 2015-03-12 Man Truck & Bus Ag Steuerventil für eine Schmiermitteldüse

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB185815A (en) * 1921-06-06 1922-09-06 Haruo Hidaka Improvements relating to stuffing boxes for compressor piston rods and the like, and to oil pressure supply apparatus therefor
US2027979A (en) * 1934-07-14 1936-01-14 Kellogg M W Co Boot pump
US2191861A (en) * 1939-01-12 1940-02-27 Theodore R Rymal Pump
US3212447A (en) * 1962-10-23 1965-10-19 Laval Turbine Pumps
US3453995A (en) * 1965-06-11 1969-07-08 Mack Trucks Piston cooling and lubrication system
DE1912171A1 (de) * 1969-03-11 1970-11-12 Voegele Ag J Schmieranlage,insbesondere fuer die Hubtaktschmierung bei Kolbenmaschinen
NL6918558A (xx) * 1969-11-11 1971-05-13
US3685840A (en) * 1971-03-29 1972-08-22 Dresser Ind Packing for compressors, pumps or the like
US3769879A (en) * 1971-12-09 1973-11-06 A Lofquist Self-compensating diaphragm pump
US3902404A (en) * 1972-01-29 1975-09-02 Pumpenfabrik Urach Sealing sleeve arrangement
DE2621348C2 (de) * 1976-05-14 1984-05-30 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg Zylinder mit trockener dünnwandiger Zylinderlaufbuchse für Brennkraftmaschinen
DE2747843C3 (de) * 1977-10-26 1980-07-03 Woma Apparatebau Wolfgang Maasberg & Co Gmbh, 4100 Duisburg Kolbenpumpe, insbesondere Hochdruck-Kolbenpumpe in Liegendbauweise

Also Published As

Publication number Publication date
DD150102A5 (de) 1981-08-12
AU5717180A (en) 1980-10-09
PL130978B1 (en) 1984-09-29
CH642145A5 (de) 1984-03-30
AU540832B2 (en) 1984-12-06
ATE12044T1 (de) 1985-03-15
EP0017100A2 (de) 1980-10-15
JPS55139594A (en) 1980-10-31
PL223294A1 (xx) 1981-01-16
HU182116B (en) 1983-12-28
MX153130A (es) 1986-08-08
ZA801966B (en) 1981-04-29
US4384510A (en) 1983-05-24
EP0017100A3 (en) 1981-01-07
DE3070250D1 (en) 1985-04-11
BR8002065A (pt) 1980-11-25
AR223868A1 (es) 1981-09-30
CS258459B2 (en) 1988-08-16
JPS6365829B2 (xx) 1988-12-16

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