WO2015144137A1 - Dispositif de soupape et palier lisse - Google Patents

Dispositif de soupape et palier lisse Download PDF

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Publication number
WO2015144137A1
WO2015144137A1 PCT/DE2015/100122 DE2015100122W WO2015144137A1 WO 2015144137 A1 WO2015144137 A1 WO 2015144137A1 DE 2015100122 W DE2015100122 W DE 2015100122W WO 2015144137 A1 WO2015144137 A1 WO 2015144137A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
valve device
pressure
slide
valve
Prior art date
Application number
PCT/DE2015/100122
Other languages
German (de)
English (en)
Inventor
Markus Schneider
Dirk Wehner
Sabine Gold
Original Assignee
Technische Universität Dresden
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 Technische Universität Dresden filed Critical Technische Universität Dresden
Priority to DE112015001449.7T priority Critical patent/DE112015001449A5/de
Publication of WO2015144137A1 publication Critical patent/WO2015144137A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N23/00—Special adaptations of check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N27/00—Proportioning devices
    • F16N27/005—Proportioning devices using restrictions

Definitions

  • the invention relates to a valve device according to the preamble of patent claim 1 and a plain bearing.
  • hydrodynamic bearings are usually equipped with a lubricant supply device, with a pressure substantially lower than the average lubricating film pressure, the lubricant in transported the bearing gap.
  • a hydrodynamic lubricant device comprises at least one lubricant pump and connecting lines which connect the lubricant pump with the bearing pockets.
  • this device is protected by a pressure relief valve from destruction by excessive pressure, can drain over the excess lubricant quantities.
  • a separate distributor for distributing the lubricant to the bearing pockets is not required.
  • the lubricant flows on the path of least resistance in the bearing gap.
  • a disadvantage of the hydrodynamic plain bearing is that a rotation of the shaft is required to produce the required hydrodynamic pressure build-up in the bearing gap. When starting and at low speeds, it comes to solid contact between the shaft and bearing shell and thus short-term wear.
  • hydrostatic radial plain bearings have been developed.
  • the required lubricant pressure in the bearing gap is generated by at least one high pressure pump outside the camp.
  • Distributed over the circumference of the bearing several mostly large-area bearing pockets are arranged, which are connected to the lubricant supply device. Mainly acting in the bearing pockets hydrostatic pressure provides the counterforce against the bearing load, thus avoiding contact between the shaft and bearing shell.
  • Such a hydrostatic lubrication device has at least one high-pressure pump, a distributor for distributing the lubricant flows to the various bearing pockets and connecting lines.
  • hydrostatic radial plain bearing is that even with minimal rotational movements or even when the shaft is stationary, a lubricating film of finite thickness can be maintained and so contact between the shaft and bearing shell and thus wear in all operating conditions can be avoided.
  • a combination of a hydrodynamic bearing with a hydrostatic bearing is shown for example in DE 10 2009 012 398 B4.
  • a very common hydrostatic bearing provides to carry out a valve device in the form of a capillary valve, which acts as a static throttle.
  • the disadvantage is that the capillaries cause high flow rates in unloaded storage bags due to their constant resistance characteristics, resulting in large volume flow losses and a strong ⁇ lericarmung in the hydrostatic bearing.
  • a pressure supply and an oil cooling must be dimensioned accordingly consuming.
  • PM controller progressive-quantity regulator
  • a certain ratio between minimum and maximum volume flow is required, which still causes high volume flow losses in unloaded storage bags.
  • the maximum flow rate and thus the highest stiffness of the storage bag is only reached at pocket pressures that are almost as high as the supply pressure. However, this rigidity is preferred even with a low-loaded storage bag.
  • the resistance characteristic of the PM controller is set to a fixed supply pressure, a variation of the supply pressure affects the characteristics and thus the performance negatively.
  • the diaphragm valve allows continuous open and close control, but is due to its membrane construction relatively susceptible to interference and maintenance-intensive.
  • the object of the invention is to provide a valve device for volume flow metering, by means of which the volume flow is metered into a hydrostatic bearing pocket depending on the load of the storage bag. Furthermore, it is an object of the invention to provide a robust and low-maintenance slide bearing.
  • valve device having the features of patent claim 1 and by a plain bearing having the features of patent claim 9.
  • the element is designed as a slide which minimizes the flow cross section in a rest position and maximizes the flow cross section in a working position.
  • the slider is biased by at least one biasing member in the rest position and can be transferred via a switching pressure in the working position. The switching pressure is adjusted by means of a biasing force.
  • the valve device according to the invention is in its preferred embodiment, a mechanical slide valve for the flow control or flow control hydrostatic sliding bearings. It's almost a pressure balance in Form of a pressure-controlled slide valve with two discrete switching positions, which is set independently of its supply pressure.
  • a preferred biasing element is a spring and in particular a spiral spring.
  • a load of the sliding bearing causes a deflection of a bearing shaft, which results in an increase in pressure in each loaded bearing pocket.
  • the slide When unloaded storage bag, the slide is in its rest position and the valve device is virtually closed. The flow cross-section is minimized and only a small volume flow flows into the bearing pocket in order to reduce cavitation in the bearing gap.
  • the pocket pressure increases to the set switching pressure, then the slider moves against its biasing force or spring force from its rest position to its working position.
  • the valve device is opened and set the maximum flow cross-section. There is an increase in the volume flow in the bearing pocket, so that the required load capacity is safely established.
  • valve device By means of the valve device according to the invention, therefore, a volume flow can be metered into a hydrostatic bearing pocket depending on the load on the bearing pocket.
  • a loss volume flow in an unloaded storage bag is minimized by a high feed resistance.
  • the supply resistance is reduced, the volume flow increases and the stiffness of the bearing pocket is increased.
  • the slider has variable notches defining the flow area.
  • the notches are arranged on the outer circumference side and thus easy to produce in terms of production technology in the slide. "Variable” means that the notches are cross-sectionally extended from their beginning or beginning in the direction of their end.
  • the notches extend in the longitudinal direction or sliding direction of the slider, wherein a maximum slide stroke is limited to the notch lengths. As a result, a back pressure in the region of the notch beginnings can be prevented.
  • the at least one biasing element engages a slider via a spring plate, which is in operative connection with the slider via a roller bearing. Due to the roller bearing friction losses between the at least one em biasing element and the slider are minimized.
  • the spring plate is connected via a central ball with the slider in operative connection.
  • the spring plate can thereby be tilted relative to the slide, without affecting the functioning of the valve device.
  • the working position can be easily formed if it is limited by an emergence of the spring plate on a housing section.
  • a check valve which blocks when a blocking pressure which is greater than the switching pressure is exceeded in the direction of the supply connection.
  • the check valve prevents backflow of the lubricant from the respective bearing pocket during load peaks, which increases the rigidity of the bearing pockets at highly dynamic loads.
  • the check valve is biased in an open position, for example spring-biased, so that when the pressure drops below the backflow is ensured.
  • the check valve In the installed state of the valve device in a plain bearing, the check valve is thus positioned between the slide and the respective bearing pocket. The functioning of the quasi-pressure scale is not hindered by the check valve.
  • the valve device can be made compact with the check valve, who n the check valve is structurally integrated into this.
  • the check valve may be inserted into the working port, wherein it preferably limits the rest position of the slide.
  • a plain bearing according to the invention is provided with at least one valve device according to the invention.
  • Such sliding bearing for example, for the storage of ship propeller shafts, is characterized by a high load capacity, high robustness against load peaks, reduced maintenance, a compact design and low energy consumption.
  • FIG. 1 shows a schematic structure of a preferred plain bearing
  • Figure 2 is a first schematic detail of an inventive
  • FIG. 3 shows an integration of the valve device according to the invention in the
  • FIG. 4 is a detail view of the valve device according to the invention.
  • Figure 5 is a volume flow pressure diagram
  • FIG. 6 is an alternative schematic representation of the invention
  • Figure 1 shows a basic structure of a plain bearing 1 according to the invention, designed as a radial sliding bearing.
  • the sliding bearing 1 for supporting a shaft 2, for example a ship propeller shaft, in a bearing shell 4 has a hydrodynamic lubrication device 6 and a hydrostatic lubrication device 8.
  • the lubrication devices 6, 8 are in fluid communication with a multiplicity of bearing pockets 10 which are uniformly distributed over the circumference of the bearing Bearing shell 4 are introduced into this.
  • the hydrodynamic lubrication device 6 has a low-pressure pump 14 driven by an electric motor 12, with the aid of which a lubricant can be conveyed from a tank 16 via low-pressure lines 18, 20 to, for example, two opposite bearing pockets 10.
  • a check valve 22 is disposed in the low pressure lines 18, 20 respectively.
  • the low-pressure line 20 extends from the low-pressure line 18, wherein a spring-loaded pressure limiting valve 24 (see FIG. 2) is arranged in an unnumbered tank line between the low-pressure line 20 and the tank 16 to avoid overstressing the hydrodynamic lubrication device 6.
  • the pressure relief valve 24 is optionally piloted in this embodiment.
  • the hydrostatic lubrication device 8 has a high-pressure pump 28 driven by an electric motor 26, by means of which the lubricant can be conveyed from the tank 16 into the bearing pockets 10.
  • the high-pressure pump 28 is connected via a feed line 30 to a multiplicity of parallel supply lines 32, one of which extends to one of the bearing pockets 10.
  • a respective valve device 34 is arranged in the supply lines 32.
  • the valve device 34 has a quasi-pressure balance and in particular here, for example, a slide valve 36 for metering a volume flow of a lubricant with a check valve 38 arranged downstream in the direction of the volume flow.
  • a spring-loaded pressure relief valve 40 is arranged in an unnumbered tank line between the supply line 30 and the tank 16.
  • the pressure relief valve 40 is optionally piloted in this embodiment.
  • FIG. 2 shows a first schematic individual representation of the valve device 34 according to the invention.
  • the slide valve 36 has two discrete switch positions I, II, namely a spring-biased rest position I and a working position II.
  • the slide valve 36 has two ports A, V, namely a pump-side supply port V and a storage pocket side working port A.
  • the volume flow is minimized by the high-pressure pump 28 to the bearing pocket 10 via a throttle 42.
  • working position II the volume flow is maximized.
  • the valve device 34 has a control line 44, which picks up a control pressure downstream of the slide valve 36 and leads to this.
  • the check valve 38 Downstream of the slide valve 36 and also downstream of the control line 44, the check valve 38 is integrated into the valve device 34.
  • the check valve 38 has a closing body 46, which is spring-loaded counter to its blocking direction. For clarity, the spring element is not shown in the drawing.
  • a spring force of the spring element is dimensioned such that a load-dependent switching pressure to the working port A can be reported via the check valve 38 from the bearing pocket 10, with the aid of which the slide valve 36 in the working position II is transferred.
  • a barrier pressure is exceeded, for example, as a result of peak loads, however, the spring force is overcome and the check valve 38 closes, so that a return flow of the lubricant from the bearing pocket 10 is prevented.
  • the shaft 2 the tank 16, the high-pressure pump 28, the here pilot-operated and spring-biased pressure relief valve 24, and a bearing pocket 10 are shown and numbered.
  • valve means 34 is carried out in a cartridge and has a housing 48, by means of which it is inserted in the receptacle 47, preferably screwed, is.
  • these ports A, B, T are mutually sealed by outer peripheral seals 50, 52, 54.
  • the supply connection V and the tank connection T are designed, for example, as bore stars introduced into the housing 48.
  • the working port A is here a radial extension of a longitudinal bore introduced into the housing 48, in which (the extension) the check valve 38 is inserted, preferably screwed, is. About a non-numbered annular seal used in a front side groove of the check valve 38, a leakage flow on the outer peripheral side of the check valve 38 is prevented.
  • the longitudinal bore passes through the housing 48 in the longitudinal direction and has, in addition to the Häan gleich practiceen or front extension a rear radial extension 62 and a radially opposite to the extensions 62 tapered central portion 64.
  • the rear extension 62 forms a receiving space in the an insert 66 is provided for providing a biasing means for biasing a slider 68 into the rest position I, preferably screwed in.
  • the slider 68 is slidably guided in the middle portion in the longitudinal direction of the housing 48 between the biasing device and the check valve 38.
  • the insert 66 has a spring space 70, which is introduced into its front end face 72 and a spring 74 of the biasing device is inserted.
  • the spring chamber 70 is radially tapered in the region of its bottom 76. Their formed by the spring chamber 70 as an annular surface end face 72 forms a mechanical stop for a spring plate 78 of the biasing means and thus a Schieberhubbegrenzung or the working position 1 1 of the slider 68th
  • the insert 66 For discharging leaked oil that has penetrated into the spring chamber 70, the insert 66 is provided with a bore star 80, which in the mounted state is in overlap with the tank connection T. In order to prevent a leakage flow on the outer peripheral side along the insert 66, in an outer circumferential groove of the insert 66, a sealing ring 82 is used, which is sealingly in abutment with an opposite inner peripheral portion of the rear extension 62.
  • the biasing device is used for biasing the slider 68 in its rest position I.
  • the spring 74 is supported on the bottom of the spring chamber 70 and engages on the spring plate 78 on the slider 68 at.
  • To guide the spring 74 at its free end of the spring plate 78 has a rear projection 84 which is partially encompassed by the spring 74.
  • the projection 84 surrounding annular surface 86 is in the working position 1 1 on the end face 72 of the insert 66, whereby a slide stroke is limited from its rest position I.
  • the spring plate 78 is supported via a rolling bearing on the slider 68.
  • the roller bearing comprises in the embodiment shown here, a ball as a rolling element, which is positioned centrally on the longitudinal axis of the housing 48 and partially in each case a front-side recess 88, 90 of the spring plate 78 and the slider 68 is immersed.
  • the recesses 88, 90 are formed in the opposing end faces, that between the spring plate 78 and the slider 68, an axial gap 92 is formed, for example, allows relative tilting movements of the spring plate 78 to slide 68.
  • the slider 68 is a cylindrical member, in the outer circumference of which variable notches 94 are uniformly distributed.
  • the notches 94 in cooperation with a circumferential housing edge 96, the longitudinal direction of the slider 68 and open in the direction of the volume flow until they emerge frontally at the front end of the slider 68. So you are in the direction of the dosing Volume flow cross-section widened. They have an axial extent such that they begin in the rest position I of the slide 68 in the region of the supply connection V. In this case, the slide 68 is located at the front end, from which the notches 94 exit the front side, to the check valve 38 at. In the working position II, in which the slider 68 is lifted from the check valve 38, the notches 94 are provided with a correspondingly enlarged notch cross-section in the region of the supply connection V.
  • valve device 34 With reference to Figure 5, the operation of the valve device 34 according to the invention will be explained. It is expressly pointed out that the given diagram values are not limiting, but are only to be understood as examples.
  • the flow cross section in the direction of the bearing pockets 10 is minimized.
  • the slider 68 is thus in its rest position I, in which a minimum volume flow 98 is formed.
  • a switching pressure 100 of the spring 74 the slide 68 is transferred to its working position and the flow cross-section is maximized (maximum volume flow 102).
  • the slider 68 moves back to its rest position I and the flow cross section is again minimized.
  • a system pressure 104 of up to about 220 bar is possible before the check valve 38 blocks.
  • the spring force essentially determines the switching pressure 100, whereas the spring constant of the spring 74 substantially determines the curve between the minimum volume flow 98 and the maximum volume flow 102.
  • a metering of the volume flow Q 6 into the here hydrostatic bearing pocket 10 is dependent on the respective pocket load.
  • a loss volume flow (minimum volume flow 98) into an unloaded bearing pocket 10 is minimized by a high inlet resistance (throttle 42 or variable notches 94 with housing edge 96).
  • the inlet resistance is reduced (increased flow cross section of the notches 94).
  • the maximum volume flow 102 is formed and the rigidity of the bearing pockets 10 which are now loaded is increased.
  • the check valve 38 locks and a return flow of the lubricant from the bearing pocket 10 to the supply port V is prevented.
  • FIG. 6 shows an alternative schematic representation of the valve device 34 according to the invention. Essentially a difference from the illustration shown in FIG. 2, in FIG. 6, a throttle 42 of the valve device 34 is not symbol I but as a notch-housing edge combination 94, 96 shown. As a further significant difference, the spring 74 is clamped in the spring chamber between the bottom 76 of the spring chamber 70 and the slide 68, shown in its rest position I.
  • the other reference numerals used in Figure 6 correspond to the same structural elements as in Figures 2, 3 and 4, so that reference is made to avoid repetition to the explanations to these figures.
  • valve device for volume flow metering, which allows a load-dependent inlet resistance and two discrete switching positions, wherein a switching pressure for transferring a switching element of the valve device is adjustable from its rest position to its working position regardless of its supply pressure, and a sliding bearing with at least one such valve device.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Abstract

L'invention concerne un dispositif de soupape servant à réguler le débit volumique, qui offre une résistance au flux affluant selon la charge et qui présente deux positions de commutation discrètes. Une pression de commutation servant à amener un élément de commutation du dispositif de soupape depuis une position de repos dans sa position de travail peut être réglée indépendamment de sa pression d'alimentation. L'invention concerne également un palier lisse pourvu au moins d'un dispositif de soupape de ce type.
PCT/DE2015/100122 2014-03-24 2015-03-24 Dispositif de soupape et palier lisse WO2015144137A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112015001449.7T DE112015001449A5 (de) 2014-03-24 2015-03-24 Ventileinrichtung und Gleitlagerung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014004524.2A DE102014004524A1 (de) 2014-03-24 2014-03-24 Ventileinrichtung und Gleitlagerung
DE102014004524.2 2014-03-24

Publications (1)

Publication Number Publication Date
WO2015144137A1 true WO2015144137A1 (fr) 2015-10-01

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ID=53039137

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2015/100122 WO2015144137A1 (fr) 2014-03-24 2015-03-24 Dispositif de soupape et palier lisse

Country Status (2)

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DE (2) DE102014004524A1 (fr)
WO (1) WO2015144137A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE332873C (de) * 1921-02-12 Ludwig Glaser Dipl Ing Rueckschlagventil, insbesondere fuer OElschmierpressen
DE1073252B (de) * 1960-01-14 Loher S. Sohne GmbH, Ruhstorf/Rott Sicherungseinrichtung fur die Lager von Maschinen
JPS61141898U (fr) * 1985-02-25 1986-09-02
DE102009012398B4 (de) 2009-03-13 2013-11-28 Blohm + Voss Industries Gmbh Radialgleitlager und Verfahren für eine Schmiermittelversorgung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE332873C (de) * 1921-02-12 Ludwig Glaser Dipl Ing Rueckschlagventil, insbesondere fuer OElschmierpressen
DE1073252B (de) * 1960-01-14 Loher S. Sohne GmbH, Ruhstorf/Rott Sicherungseinrichtung fur die Lager von Maschinen
JPS61141898U (fr) * 1985-02-25 1986-09-02
DE102009012398B4 (de) 2009-03-13 2013-11-28 Blohm + Voss Industries Gmbh Radialgleitlager und Verfahren für eine Schmiermittelversorgung

Also Published As

Publication number Publication date
DE112015001449A5 (de) 2016-12-29
DE102014004524A1 (de) 2015-09-24

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