EP0613528A1 - Pumpe. - Google Patents
Pumpe.Info
- Publication number
- EP0613528A1 EP0613528A1 EP92923450A EP92923450A EP0613528A1 EP 0613528 A1 EP0613528 A1 EP 0613528A1 EP 92923450 A EP92923450 A EP 92923450A EP 92923450 A EP92923450 A EP 92923450A EP 0613528 A1 EP0613528 A1 EP 0613528A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- injector
- pump
- pump according
- fluid
- channel
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C15/062—Arrangements for supercharging the working space
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
- F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
- F04C11/006—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle having complementary function
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
-
- 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
- F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
- F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
- F04F5/46—Arrangements of nozzles
Definitions
- the invention relates to a pump according to the preamble of claim 1.
- Pumps of the type mentioned here are used, for example, in power steering systems and convey a special fluid or oil in order to support the steering forces to be applied to the steering wheel, for example of a motor vehicle.
- the pumps referred to here are preferably vane pumps which draw in oil from a supply provided outside the pump, for example from a tank.
- Such pumps are equipped with a valve called a flow control valve, via which oil from the high pressure area can be directed into the suction area of the pump. From a certain pump speed and with a fixed adjustable delivery rate, the valve opens an outflow hole into which oil under high pressure can escape. The oil enters the intake area of the conveyor.
- the pump is often not adequately filled with hydraulic oil. Moreover, in the oil-carrying channels due to cavitation damage.
- Tor by the Injek ⁇ which is on the one hand acted upon with an effluent from a high pressure region of fluid and the other oil-changed from the Zubowka ⁇ nal in the intake area of the conveyor för ⁇ ', is for all operating conditions a ausrei ⁇ sponding filling of the suction area. Damage due to cavitation is thus avoided due to the good supply of hydraulic oil to the intake area.
- An embodiment of the pump is preferred, in which the inlet region of the injector is arranged near the outlet of the control valve, which may allow fluid under high pressure to escape into an outflow bore.
- the high-energy fluid is thus collected by the injector, so that damage within the pump housing is avoided. Due to the fact that the mouth of the injector in the supply channel is immediately in front of the suction area of the conveyor. is arranged, an optimal introduction of the fluid is ensured, so that cavitations are avoided even at high pumping rates.
- an embodiment of the pump is preferred in which the base body of the injector is surrounded by an annular channel which is connected to the feed channel. Oil from an oil supply provided outside the pump, for example from a tank, is passed through the ring channel around the injector, so that a particularly good suction effect is ensured, the jet emerging from the injector being at its entire base or Mantle surface 'is used optimally.
- the base body of the injector is designed as an essentially tubular sleeve. Its inlet opening is assigned to the fluid emerging from a control valve, its outlet opening to the suction chamber of the conveying device. Both the oil emerging from the valve and the entrained fluid from the inlet channel are directed in a predetermined direction, namely into the suction area of the delivery device. This ensures good filling of the suction area, so that cavitation is reliably avoided.
- Figure 1 is a schematic longitudinal section through a first embodiment of a pump
- FIG. 2 shows an enlarged longitudinal section through the injector shown in FIG. 1;
- Figure 3 is a schematic longitudinal section through a further embodiment of a pump
- FIG. 4 shows a section through the injector of the pump shown in FIG. 3, made perpendicular to the section plane in FIG. 3.
- the pump 1 shown in the figure has a vane arrangement as a conveying device 3, which is arranged within the housing 5 of the pump.
- the pump 1 can be provided with a bearing flange 7 ⁇ of any configuration. It is therefore only outlined in dashed lines.
- the vanes are radially displaceably mounted in corresponding slots which are introduced into the rotor 19.
- the ends of the vanes 17 lie outside the rotor 19 against a ring 23, so that closed volumes are formed between the individual vanes.
- the inner surface of the ring 23 has different distances from the axis of rotation 25 of the pump 1 as seen over the circumference of the ring, so that the spaces enclosed between the vanes 17 become larger and smaller when the rotor rotates, so that fluid from a suction space 27 the pump 1 is conveyed into a pressure chamber 29.
- the fluid penetrates the pressure plate 15.
- the pressure plate carrier 11 and thus the pressure plate 15 are pressed against the ring 23 by the pressure spring 13, which in turn is pressed against the side plate 21.
- the fluid conveyed by the pump 1 is supplied by an external storage container, for example a tank, which is connected to a suction connection 31 provided at the top in the housing 5.
- the Suction port forms part of a supply channel 33 through which the oil reaches the suction chamber 27.
- the feed channel 33 has an area 35 which extends under an arc and leads to a channel section 37 which opens directly into the suction space 27.
- the central axis 39 of the channel section 37 is aligned with the central axis 41 of a bore 43 penetrating the wall of the housing 5. This means that the channel section 37 can be produced through a bore made in the housing 5.
- the bore 43 is closed in a pressure-tight manner by a cover 45.
- a control valve 47 referred to as a flow control valve, is arranged perpendicular to the image axis and can be displaced in the direction of its longitudinal axis, that is to say perpendicular to the image plane, within a valve bore 49.
- the displacement takes place as a function of the pressure prevailing in the pressure chamber 29 against the force of a compression spring (not shown here).
- the valve bore 49 is therefore connected to the pressure chamber 29 by suitable channels in the pump housing.
- the position of the valve changes depending on the pressure and the speed of the pump.
- the control valve opens from a fixed, predeterminable delivery rate of a certain pump speed, see above that a fluid jet under high pressure enters an outflow bore 51.
- This is chosen to be very short and flows directly into an injector 53 which has an elongated, essentially tubular base body 55.
- This is preferably made of erosion-resistant material.
- the cross section through the base body shows that the thickness of its wall decreases from the inlet opening 57 to the outlet opening 59, whereby on the one hand the outer surface of the base body can have the shape of a truncated cone shell, while that in the interior of the injector 53 current flow area 61 is approximately cylindrical or in turn is frustoconical.
- the central axis 63 of the injector 53 coincides here with the central axis 39 of the channel section 37 and also with the central axis 65 of the outflow bore 51.
- the injector 53 is surrounded by an annular channel 67, which is connected on the one hand to the curved area 35 of the supply channel 33 and on the other hand to the channel section 37.
- the housing 5 of the pump 1 is fastened to the bearing flange 7 in a suitable manner.
- a screw 69 for connecting the two parts is indicated here as an example.
- the interior of the housing 5 is designed such that the printing plate carrier 11 can be displaced in the direction of the axis of rotation 25. Between this and the housing 5 is a circumferential to separate the suction chamber 27 from the pressure chamber 29 Seal 69 'provided.
- the pressure chamber 29 is preferably circumferential.
- a bore 71 running through the pressure plate carrier 11, which penetrates the pressure plate 15 and opens in the foot region of the vanes 17 on the rotor 19, emanates from this. In this way, it is possible to pressurize the wings to facilitate the radial outward movement.
- the feed channel 33 can be led directly to the outflow jet entering the outflow bore 51.
- the outflow jet is caught by the injector 53 or by its base body 55, so that erosion of the housing 5 of the pump 1 is reliably avoided.
- the jet of the fluid passing through the injector is accelerated, so that the oil under low pressure is very well entrained. Due to the annular channel 57, the fluid in the supply channel is brought up to the entire peripheral region of the jet leaving the injector 53, so that its effect is particularly pronounced.
- the central axis 65 of the outflow bore 51, the central axis 63 of the injector 53 and the central axis 39 of the channel section 37 are aligned in a line.
- the injector 53 thus allows both the fluid coming from the valve bore 49 and the entrained oil to be guided, so that the suction area of the pump is optimally filled with the fluid to be conveyed even if the individual parts are arranged differently.
- the injector 53 shown here is characterized by a collar 71 surrounding its inlet opening 57, which leads to a reinforcement of the injector and enables this part to be pressed into the housing wall.
- the collar 71 can also be made larger for other types of mounting than shown in FIG. 2.
- both areas can be produced through a single bore in the material of the housing 5.
- the annular channel 67 which runs concentrically to the channel section 37, is preferably cast into the base body of the housing 5.
- an annular recess can be made in the base body of the housing through the bore 43.
- Housing 5 are introduced, which then serves to accommodate the collar 71.
- the outside diameter of the collar 71 is smaller than the inside diameter of the bore 43 but also of the channel section 37.
- the injector can therefore be inserted into the housing 5 from outside through the bore 43 and through the channel section 37. Automation is therefore also possible when introducing the injector into the housing 5 of the pump 1.
- the outflow bore 51 is in turn introduced with the aid of a drill which is guided through the bore 43 and thereby runs through the channel section 37. It can thus be seen that the installation of the injector 53 in the housing 5 is very simple, with the introduction of the fluid guide channels cooperating with the injector, that is to say the outflow bore 51, the channel section 37 and the annular channel 67, simple and therefore inexpensive to implement.
- the injector 53 can in turn be manufactured inexpensively, since its base body 55 can be realized as an essentially tubular sleeve.
- the space requirement of the injector is extremely low, so that the pump 1 is very compact.
- the flow control valve As shown in the sectional view, runs perpendicular to the axis of rotation 25 of the drive shaft 9. It is essential that the outflow jet is as close as possible to the control Valve 47 is picked up by the injector 53 and suction of the fluid to be brought in via the annular channel 67 is effected directly in this area.
- the annular channel ensures good utilization of the fluid jet penetrating the injector, since it completely surrounds the base body 55.
- the diameter of the ring channel and that of the outlet opening 59 of the injector 53 can be adapted as a function of the viscosity of the fluid used, the delivery rate of the pump and the flow rate of the fluid leaving the injector. In this way, an optimal filling of the suction space 27 is always to be ensured, so that cavitation-free operation of the pump is ensured with a wide variety of delivery rates.
- the height of the annular channel 67 surrounding the base body 55 of the injector 53 is matched to the length of the injector 53 in such a way that there is optimal suction of the fluid under low pressure.
- the effective length of the injector is approximately one and a half times the height of the ring channel.
- the diameter of the curved area 35 is selected such that the mouth of this area has a diameter which corresponds to the height of the annular channel corresponds.
- the outer diameter of the ring channel 67 is somewhat larger selected as the diameter of the channel section 37. This dimensioning of the ring channel allows a particularly good flow around the jacket of the injector 53, so that the suction effect of the jet leaving the injector 53 can be used particularly well.
- the sectional view also shows that a low-loss entry of the outflow jet into the injector 53 is made possible by the fact that the inside diameter of the outflow bore 51 is selected to be the same size as the diameter of the inlet opening 57.
- FIG. 2 which shows an enlarged longitudinal section through the injector 53, the size relationships in the area of the injector are to be shown more precisely.
- the basic condition for the function of the injector results, which is only guaranteed if a sufficiently large volume flow can be sucked in from the outside, that is, from the storage container. Only with that is one To prevent cavitation in the pump.
- the jet flowing out of the injector means that fluid must be sucked in from the tank (not shown here) via the suction connection 31, the feed channel 33, its curved region 35 and the ring channel 67.
- cavitation initially manifests itself only as a drop in the delivery rate of the pump, but finally, with increasing suction problems, the operating noises of the pump become louder and louder.
- the injector should be designed so that a slight reduction in the delivery rate is prevented.
- FIG. 3 differs from that shown in FIG. 1 only in that the injector 53 is held in the housing 5 of the pump 1 by a fastening sleeve 73 serving as a securing element.
- a fastening sleeve 73 serving as a securing element.
- the fastening sleeve 73 has an anchoring ring 75 arranged in the channel section 37, the outer diameter of which is adapted to the inner diameter of the channel section 37 in such a way that the fastening sleeve is held securely at all temperatures which can occur when the pump 1 is used .
- the height of the anchoring ring is selected such that it does not protrude, or practically does not protrude into the upstream ring channel 67, so that the medium conveyed by the pump can flow there unimpeded.
- the anchoring ring 75 likewise does not protrude or practically does not protrude into the suction space 27, so that it does not hinder the medium drawn in by the pump here either.
- the anchoring ring 75 is provided with at least one, preferably two diametrically opposite retaining webs, which extend upward through the ring channel 67 to the collar 71 of the injector 53.
- the holding webs 77 press against the underside of the collar 71 and thus hold the injector 53 securely in its assembly position.
- the collar 71 finds only little hold in the base body 5 of the pump 1, so that a high degree of functional reliability is obtained through the use of the fastening sleeve 73.
- the injector 53 is held securely at the desired mounting position over the entire temperature range of the use of the pump 1.
- fastening sleeve 73 it is possible to hold the fastening sleeve 73 in the channel section 73 by means of a press fit. It is also conceivable to achieve a positive fit between the fastening sleeve and the base body of the pump by means of corrugation on the inner surface of the channel section and suitable corrugation on the outer surface of the fastening sleeve or the anchoring ring 75. Finally, it is also conceivable to provide the channel section 37 on its inner surface with a thread which meshes with an external thread provided on the outside of the anchoring ring. This means that the fastening sleeve 73 can be screwed into the base body of the pump and thus hold the injector securely in its initial position.
- the medium flowing out of the suction connection 31 into the annular space 67 is practically not hindered by the holding webs 77; it can also get freely through the interior of the fastening sleeve, that is, through the interior of the anchoring ring 75 into the suction space 27, the medium emerging from the outlet opening 59 of the injector 53 (see FIG. 4) under high pressure in the channel section 37, related Medium present in the interior of the anchoring ring 75 is entrained, so that the suction space 27 is optimally filled.
- the fastening sleeve 73 is preferably arranged in such a way that the fluid passing from the bent region 35 into the annular channel 67 is not hindered by the retaining webs 77. This means that there are no retaining webs 77 in the mouth area between the curved area 35 and the ring channel 67.
- FIG. 4 shows particularly clearly that the fastening sleeve 73, as the designation as a sleeve already indicates, is hollow on the inside.
- the inner diameter of the fastening sleeve is selected such that the medium conveyed by the pump can pass unhindered from the annular channel 67 into the suction space 27.
- the outlet opening 57 of the injector 53 is located approximately halfway up the anchoring ring 75.
- the dimensions of the injector and the fastening sleeve 73 can be selected as was determined with reference to FIG. 2.
- the reference size b is to be used as the inner diameter of the anchoring ring 75 or the fastening sleeve 73.
- FIG. 4 clearly shows once again that the retaining webs 77 of the fastening sleeves 73 starting from the anchoring ring 75 extend through the annular channel 67 and end on the underside of the collar 71 of the injector 53.
- the collar 71 has a low height and thus a low holding force of the injector within the housing 5.
- This holding force is, as can be seen from the explanations for FIGS. 3 and 4, by the fastening sleeve 73 significantly increased, especially if, in addition to a normal pressing of the fastening sleeve 73 inside the housing 5, a positive connection between the sleeve and the housing is selected.
- the width of the holding webs 77 can be chosen to be relatively small, since they have a high degree of dimensional stability due to the curvature of the sleeve.
- the fastening sleeve 73 is formed overall as a hollow body, the inner and outer surfaces of which are circular-cylindrical. The holding webs 77 so domed that they are vertical
- the easy-to-manufacture fastening sleeve which is preferably made of metal, achieves a high level of functional reliability of the pump, since the injector is held securely at the installation site even with small installation sizes.
- the production costs of the pump do not increase practically, since the sleeve, like the injector 53, can easily be introduced through the bore 43 into the interior of the housing 5 of the pump 1 and anchored in the region of the channel section 37 .
- the fastening sleeve 73 since the fastening sleeve 73 only serves to secure the injector 53, it must not hinder the flow of the medium conveyed by the pump.
- the inside diameter of the sleeve is preferably selected so that the medium is optimally supplied to the outlet opening 59 of the injector 53 and is thus entrained by the medium emerging from the injector with a high degree of threading. In the area of the ring channel 67, the inflowing medium may be prevented as little as possible.
- the fastening sleeve is designed as a perforated plate in the area of the ring channel.
- narrow retaining webs 77 are preferably chosen, as shown particularly in FIG 3 are clearly visible in order to achieve a particularly low interference resistance.
- the retaining webs 77 it is also possible for the retaining webs 77 to be inclined somewhat in the direction of the injector 53 and to be supported on its outer surface, so that it is held securely in its assembly position. This requires a coordination of the inner diameter left free by the holding webs with the outer diameter of the injector in the area of the engagement of the holding webs on the outer surface of the injector.
- the cheapest way to implement the fastening sleeve 73 is if the holding webs 77 virtually form a continuation of the wall of the anchoring ring 75 and extend parallel to the central axis of the sleeve or the injector up to its collar 71 and hold it securely in the base body 5 of the pump 1 .
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Combustion & Propulsion (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Physics & Mathematics (AREA)
- Rotary Pumps (AREA)
- Fuel-Injection Apparatus (AREA)
- Details Of Reciprocating Pumps (AREA)
- External Artificial Organs (AREA)
- Reciprocating Pumps (AREA)
- Infusion, Injection, And Reservoir Apparatuses (AREA)
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4138516A DE4138516A1 (de) | 1991-11-23 | 1991-11-23 | Pumpe |
DE4138516 | 1991-11-23 | ||
PCT/EP1992/002584 WO1993010354A1 (de) | 1991-11-23 | 1992-11-11 | Pumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0613528A1 true EP0613528A1 (de) | 1994-09-07 |
EP0613528B1 EP0613528B1 (de) | 1996-03-20 |
Family
ID=6445403
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP92923450A Expired - Lifetime EP0613528B1 (de) | 1991-11-23 | 1992-11-11 | Pumpe |
Country Status (5)
Country | Link |
---|---|
US (1) | US5496152A (de) |
EP (1) | EP0613528B1 (de) |
JP (1) | JP3616808B2 (de) |
DE (2) | DE4138516A1 (de) |
WO (1) | WO1993010354A1 (de) |
Families Citing this family (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0763659B1 (de) * | 1995-09-14 | 2002-12-18 | LuK Fahrzeug-Hydraulik GmbH & Co. KG | Pumpe |
NL1009256C1 (nl) * | 1998-05-25 | 1999-06-25 | Scipio Pieter Sjoerd Beerlings | Cyclonale ejectiepomp. |
DE19836630A1 (de) * | 1998-08-13 | 2000-02-17 | Luk Fahrzeug Hydraulik | Pumpe |
DE19836628A1 (de) * | 1998-08-13 | 2000-02-17 | Luk Fahrzeug Hydraulik | Pumpe |
DE19836620C2 (de) * | 1998-08-13 | 2003-12-24 | Luk Fahrzeug Hydraulik | Pumpe |
US6413063B1 (en) | 1998-08-13 | 2002-07-02 | Luk Fahrzeug-Hydraulik Gmbh & Co. Kg | Pump |
JP2002522707A (ja) * | 1998-08-13 | 2002-07-23 | ルーク ファールチョイグ−ヒドラウリク ゲーエムベーハー アンド カンパニー カーゲー | ポンプ |
DE19952144B4 (de) * | 1998-11-17 | 2014-01-16 | Ixetic Bad Homburg Gmbh | Druckmittelfördereinrichtung mit einer Pumpeneinrichtung oberhalb einer Druckmittelvorratsmenge mit Verbindung zur zugehörigen Druckleitung |
JP2002021748A (ja) * | 2000-06-30 | 2002-01-23 | Showa Corp | ベーンポンプ |
EP1303701B1 (de) | 2000-07-27 | 2005-08-31 | LuK Fahrzeug-Hydraulik GmbH & Co. KG | Pumpe |
WO2002010592A1 (de) * | 2000-08-01 | 2002-02-07 | Luk Fahrzeug-Hydraulik Gmbh & Co. Kg | Pumpe mit stromregelventileinrichtung und injektoreinrichtung |
US20080273992A1 (en) * | 2007-05-03 | 2008-11-06 | Metaldyne Company Llc. | Cavitation-deterring energy-efficient fluid pump system and method of operation |
IN2009KO01235A (de) | 2008-10-20 | 2015-08-14 | Fmo Technology Gmbh | |
DE102011084405B4 (de) * | 2011-10-13 | 2021-05-27 | Zf Friedrichshafen Ag | Saugaufgeladene Pumpe zum Fördern einer Flüssigkeit |
DE102012100702A1 (de) * | 2012-01-30 | 2013-08-01 | Zf Lenksysteme Gmbh | Pumpe, insbesondere Flügelzellenpumpe für eine Hilfskraftlenkung |
DE102012010939B4 (de) * | 2012-06-04 | 2016-06-02 | Ibs Filtran Kunststoff- / Metallerzeugnisse Gmbh | Saugölfiltereinheit für Getriebe oder Verbrennungsmotoren |
DE102016102433B3 (de) * | 2016-02-11 | 2017-05-11 | Steyr Motors Gmbh | Gear Pump |
US11143208B2 (en) * | 2018-12-17 | 2021-10-12 | Goodrich Corporation | Aspirators for evacuation assemblies |
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US2724335A (en) * | 1951-12-14 | 1955-11-22 | Eaton Mfg Co | Pumping unit with flow director |
US2983226A (en) * | 1953-01-16 | 1961-05-09 | William T Livermore | Injection filled liquid pump |
US2985357A (en) * | 1959-03-19 | 1961-05-23 | Bendix Corp | Injectors |
US3207077A (en) * | 1963-05-27 | 1965-09-21 | Gen Motors Corp | Pump |
JPS504835B1 (de) * | 1968-08-14 | 1975-02-24 | ||
US3551073A (en) * | 1968-12-16 | 1970-12-29 | Chandler Evans Inc | Pumping system with improved jet inducer |
US3614266A (en) * | 1969-12-24 | 1971-10-19 | Ford Motor Co | Compact positive displacement pump |
US3922113A (en) * | 1972-01-06 | 1975-11-25 | Plessey Co Ltd | Metered supply of liquids |
SU690161A1 (ru) * | 1974-04-12 | 1979-10-05 | Panin Nikolaj M | Промывочный узел гидромониторного долота |
FR2443598A1 (fr) * | 1978-12-08 | 1980-07-04 | Renault | Dispositif d'alimentation a recuperation d'energie d'une pompe |
DE3210729A1 (de) * | 1982-03-24 | 1983-10-06 | Hoechst Ag | Verfahren zur herstellung von titandioxid-konzentraten |
EP0125328B1 (de) * | 1983-05-14 | 1987-03-04 | Vickers Systems GmbH | Flügelzellenpumpe, insbesondere zur Lenkhilfe |
US4712739A (en) * | 1986-10-03 | 1987-12-15 | Champion Spark Plug Company | Spray gun nozzle assembly retainer clip and spray gun nozzle assembly |
US4823550A (en) * | 1987-06-23 | 1989-04-25 | Templeton, Kenly & Co. | Rotary valve with jet pump aspirator |
GB2266342B (en) * | 1989-08-04 | 1994-01-26 | Ph Pool Services Ltd | Jet units for whirlpool-bath systems |
FR2666382B1 (fr) * | 1990-08-28 | 1992-10-16 | Cit Alcatel | Dispositif de pompage d'un gaz par une pompe a palettes et a joint d'huile et application aux detecteurs de fuites a helium. |
-
1991
- 1991-11-23 DE DE4138516A patent/DE4138516A1/de not_active Ceased
-
1992
- 1992-11-11 JP JP50895293A patent/JP3616808B2/ja not_active Expired - Fee Related
- 1992-11-11 DE DE59205785T patent/DE59205785D1/de not_active Expired - Lifetime
- 1992-11-11 WO PCT/EP1992/002584 patent/WO1993010354A1/de active IP Right Grant
- 1992-11-11 EP EP92923450A patent/EP0613528B1/de not_active Expired - Lifetime
- 1992-11-11 US US08/244,158 patent/US5496152A/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO9310354A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO1993010354A1 (de) | 1993-05-27 |
JPH07504245A (ja) | 1995-05-11 |
JP3616808B2 (ja) | 2005-02-02 |
DE59205785D1 (de) | 1996-04-25 |
DE4138516A1 (de) | 1993-05-27 |
EP0613528B1 (de) | 1996-03-20 |
US5496152A (en) | 1996-03-05 |
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