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
  • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
  • F04C15/0046—Internal leakage control
• • 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

Definitions

• the invention relates to a pump for conveying a fluid, in particular a vane pump, with a conveying device accommodated in a housing, an end-side housing cover and possibly a bearing flange adjoining the housing on the side opposite the housing cover, wherein between the housing and the housing cover and possibly a seal is arranged between the housing and the bearing flange and the seal is inserted into a groove formed in the housing cover and possibly in the bearing flange and / or in the respective end face of the housing, and a leakage path for the fluid extends between the pressure side and the suction side.
• the invention relates to a pump for conveying a fluid, in particular a vane pump, with a conveying device accommodated in a housing, a feed channel for the fluid which is formed in the housing and extends into the suction region of the conveying device, and an injector device which serves to convey the fluid Injector device injects high-pressure fluid into the fluid emerging from the supply channel into a blasting chamber upstream of the conveying device and thereby entrains or accelerates it.
• Pumps of the generic type are used, for example, in power steering systems and pump a special oil to support the steering force to be applied to the steering wheel of a motor vehicle.
• These are preferably vane pumps that draw oil from a reservoir provided outside the pump, for example from an external tank.
• Such pumps are usually equipped with a flow control valve, via which oil from the high pressure area - pressure side - into the suction area - suction side - of the pump can be directed. From a certain pump speed and with a fixed adjustable delivery rate, the flow control valve opens an outflow bore, through which oil under high pressure can escape. The oil enters the intake area of the conveyor.
• a generic pump which, in order to achieve operation that is as free of cavitation as possible, has a very special promotional measure for delivering the tank oil, namely an injector device that works similarly to a water jet pump.
• the injector device is acted upon by high-pressure fluid, which is supplied to the injector device from the high-pressure area.
• This high-pressure fluid is injected into the fluid from the supply channel by the injector device, specifically in the region of a blasting chamber upstream of the conveying device.
• the fluid coming out of the tank is entrained or accelerated and from there reaches the suction area of the delivery device via a further channel system.
• the present invention is based on the object of designing and developing a pump of the generic type in such a way that reliable discharge of the pressure-side leak oil while reducing the design or manufacturing measures is possible. Furthermore, a uniform charging of the cells of the conveyor is to be ensured. Damage due to cavitation should be effectively avoided.
• a pump of the type mentioned at the outset is characterized in that the leakage path on the inside of the seal - media side - runs parallel to the seal, at least in some areas.
• the leakage path can be designed to run parallel to the seal at least in some areas, the provision of the leakage path near the seal relieving the pressure on the seal.
• provision of the leakage path not only ensures that the fluid or leakage oil is safely removed, but at the same time relieves the pressure on the seal, which favors the sealing effect in the long term.
• the leakage path is provided wherever leakage oil has to be discharged on the pressure side.
• the leakage path extends at least in regions parallel to the seal, specifically on the inside of the seal or on the media side of the seal.
• the already provided groove for the seal serves as the leakage path.
• This groove is either formed in the housing cover or - if present - in the bearing flange or in the respective end face of the housing and is actually used for inserting or receiving the seal.
• the groove can, for example, be cast into the respective component.
• the groove is at least partially wider than the seal, namely towards the inside of the seal or the media side, see above that the groove on the inside of the seal - media side - forms the leakage path running parallel to the seal, directly adjacent to the seal.
• the seal is relieved directly on the inside of the seal and at the same time - on the inside of the seal - lubricated and, if necessary, cooled.
• the groove In the case of a wide configuration of the groove, it has a double function, namely on the one hand the reception of the seal and on the other hand the provision of a leakage path or leakage channel. Since the groove for receiving the seal is required anyway, the manufacturing effort is reduced considerably. In addition, this measure reduces the overall installation space required, so that this measure favors miniaturization of the pump.
• the groove is designed as a self-contained, circumferential annular groove, so that a sealing ring can be used as a seal.
• the groove can be widened over its entire length, so that the leakage path extends over the entire length of the seal - on the inside of the seal or the media side. It is also conceivable that the leakage path - as a widening of the groove - extends only partially over the length of the groove, namely wherever there is leakage oil to be discharged.
• the groove could be designed as a simple groove with a substantially widened groove base (at least wider than the usual groove for receiving the seal), so that the seal or the sealing ring can be positioned in the outer region of the groove against the outer groove wall. This results from the dimensioning of the groove on the one hand and the sealing ring on the other hand.
• the groove is stepped toward the bottom of the groove, the seal being arranged in the outer step of the groove.
• the outer groove area receiving the seal is advantageously formed deeper.
• the groove can be designed as a type of double groove, namely with a web extending between the groove regions and at least partially or largely separating the groove regions from one another.
• the seal or insert the sealing ring in the outer groove area, this groove area also advantageously being at least slightly larger than the seal.
• the inner groove area serves as a leakage path.
• the widened region of the groove - the leakage path running parallel to the seal - is fluidly connected to the suction side of the pump at at least one point, in order to effectively convey the leakage oil that accumulates in the leakage path out of the pressure side.
• the leak oil is fed directly to the suction side of the pump, where it is again mixed with the tank oil.
• the entire printed page i.e. the high pressure prevailing in the pump is sealed, at least very predominantly within the housing interior and / or directly adjacent to it.
• the high pressure is sealed within the bore formed for the rotary group of the vane pump, so that there is no “real” high pressure outside of this bore or far away from this bore and thus away from the interior of the housing horizontal seal no longer - as is the case in conventional pumps of the generic type - exposed to the "real" high pressure, so that the provision of the leakage path with the leakage path itself on the one hand and on the other hand with the seal adjacent there is favored.
• the other seals used to seal the pressure side act against the housing cover and possibly against the bearing flange.
• This can also be conventional sealing rings, which can also be equipped with a special leakage path - as an expanded groove in each case.
• a seal Form grooves each as a special leakage path, in order to be able to guarantee a particularly effective discharge with regard to the leakage oil.
• a pump of the type mentioned at the outset is characterized in that the feed channel opens into a blasting chamber on both sides of the conveying device, each with a subchannel, and that the injector device on both sides - each with jet nozzles - Blasting, so that at least one jet nozzle of the injector device is directed into each of the two blasting chambers.
• the injector device comprises injectors directed into each of the two jet chambers, i.e. two injectors in total, these injectors in turn emitting at least one jet nozzle.
• the injector device or its inlet is advantageously arranged essentially centrally above the conveying device.
• Such a central arrangement of the injector device has the advantage that the paths extending on both sides of the conveying device are roughly the same length on the one hand to accelerate the fluid coming from the tank and on the other hand the fluid under high pressure and used for injection. Accordingly, this is in the two-sided intake areas of the conveying devices reaching fluid under the same pressure, so that a uniform loading of the conveying device can take place on both sides.
• the jet nozzles are oriented such that the fluid injected via the jet nozzle under high pressure strikes the fluid to be accelerated in its direction of flow or at an acute angle to its direction of flow.
• the acceleration of the fluid coming from the tank is favored again, the fluid under high pressure already being split up between the two jet nozzles within the injector device, with a high kinetic energy of the fluid used for the injection.
• the jet nozzles it is advantageous if they have an approximately round nozzle shape, so that the fluid forms a type of jet jacket or a cylindrical / cone-shaped jet jacket when it emerges. Compared to a thin, fine jet, this creates a larger contact surface, which is double due to the two-sided radiation by means of the jet nozzles. Ultimately, the fluid reaches the jet nozzles of the injector device via outflow bores on both sides.
• the subchannels guiding the fluid coming from the tank of the feed channel divided on both sides of the conveying device are of approximately the same length, so that the same length distances are covered on the part of the fluid coming from the tank.
• the oil coming from the tank is acted upon and accelerated by the injected oil under high pressure and high kinetic energy, in a similar way to the case with a water jet pump.
• the subchannels of the feed channel divided on both sides of the conveying device are advantageously not only of approximately the same length, but also preferably have the same course, this course possibly being mirror-inverted on both sides.
• the generic pump has an end housing cover on one side of the housing and a bearing flange on the other side of the housing, if this is necessary. To this extent, it is possible that the blasting chamber formed on both sides of the conveying device is at least largely incorporated into the housing cover or into the bearing flange. It is also conceivable that the blasting chamber is assigned to the actual housing and is limited by the inner wall of the housing cover on the one hand and the bearing flange on the other hand. Both variants can be implemented.
• the fluid coming from the tank is divided in accordance with the invention on both sides of the conveying device, the fluid being accelerated by injection on these two sides of the conveying device in the respective blasting chamber.
• the jet nozzles are directed at a preferably acute angle that deviates from 90 °, or are inclined downward, toward the wall of the housing and / or the bearing flange opposite the outlet of the supply channel, so that the accelerated fluid impinges there with high energy and evades on both sides according to the contour of the wall of the housing and / or the bearing flange. Consequently, the fluid is again divided here, namely on both sides of the conveying device into another two separate flow paths, namely on both sides of the central bore provided in the housing for the conveying device or for the rotating group forming the conveying device.
• the wall of the housing and possibly the bearing flange is designed in such a way that it distributes the accelerated fluid impinging there approximately uniformly by lateral outflow and, in the sense of a guiding device, at least largely leads into suction channels formed on both sides, the suction channels leading into the immediate suction area the conveyor.
• the suction channels lead directly to the suction kidneys of the conveyor, on both sides of the conveyor on two separate flow paths, so that the suction kidneys of the conveyor are supplied at four mutually independent locations with the fluid under the same pressure and with the same volume of the fluid. This ensures uniform loading of the conveyor.
• the suction channels leading to the suction kidneys are at least largely of the same length, in order to avoid pressure losses in the fluid of different magnitudes.
• a pressure-limiting pilot which serves as overload protection to limit a maximum operating pressure on the high-pressure side.
• fluid is fed to the pressure pilot from the high pressure side, which is to be returned after passing through the pressure limiting pilot.
• the supply channel is flow-connected in a further advantageous manner to the pressure-limiting pilot for returning the pilot oil.
• This flow connection can be realized via a channel labyrinth which is preferably cast into the housing and / or into the housing cover and / or into the bearing flange. In any case, it is advantageous if this fluid is returned to the circuit together with the fluid coming from the tank, and specifically immediately before the area of action of the injector device.
• leakage oil channels or a corresponding channel labyrinth are provided, which leads the leakage oil into the supply channel from various collection points.
• FIG. 1 is a schematic side view, sectioned, an embodiment of a generic pump
• Fig. 2 shows the object of Fig. 1 in a front view with removed
• FIG. 3 shows a schematic interior view of the bearing flange with an incorporated groove, but without a seal
• FIG. 5 in a schematic side view, sectioned, another
• FIG. 6 in a schematic side view, in section, the object from FIG. 5 without a housing cover, without a bearing flange and without a conveyor device,
• Fig. 7 shows the object of Fig. 6 in a front view with removed
• Fig. 8 in a schematic interior view of the bearing flange, on the
• Fig. 1 shows a simplified representation of a generic pump in a sectional side view, which is specifically a vane pump with a rotation group 1 or conveyor not described here.
• a rotation group 1 or conveyor not described here.
• DE 39 28 029 A1 With regard to the special design of such a rotation group 1, reference is made to DE 39 28 029 A1 only by way of example.
• the pump shown here comprises - as essential components - a housing 2 and a conveying device accommodated in the housing 2, which is the rotation group 1 already mentioned.
• the front is on one side a housing cover 3 which closes the housing 2 and on the other side - on the side opposite the housing cover 3 - a bearing flange 4 adjoining the housing 2 is provided.
• an outwardly acting seal 5, 6 is arranged, the seal 5 acting against the housing cover 3 in a groove formed in the end face 7 of the housing 2 8 is inserted.
• the seal 6 is assigned to the bearing flange 4 or inserted into a groove 9 machined into the bearing flange 4.
• the groove 9 could also be worked into the end face 10 of the housing 2.
• the leakage path 13 is formed on the inside of the seal - media side - at least in regions parallel to the seal 5, 6.
• Fig. 2 shows particularly clearly that the groove 8 is formed wider than the seal 5 to form the leakage path 13, so that the leakage path 13 is formed on the inside of the seal 14 parallel to the seal 5. Likewise, the leakage path 13 is formed through the groove 9 in the bearing flange 4, the separate representation of the seal 6 being omitted in the representation of the bearing flange 4 according to FIG. 3.
• Figures 1 to 4 together show that the grooves 8, 9 are designed as self-contained ring grooves.
• the seals 5, 6 are designed as sealing rings, the leakage path 13 only extending over those areas of the grooves 8, 9 where leak oil occurs and must be removed or removed accordingly. Only there is the leakage path 13 designed as an integral part of the groove 8, 9, this being particularly clearly shown in FIG. 2 with regard to the groove 8 formed in the housing cover 3.
• Fig. 2 further shows that the widened area of the groove 8 forming the leakage path 13 is fluidly connected to the suction side 12 of the pump, namely via an integral leak oil channel 15.
• Fig. 2 it is also indicated how the leak oil 16 in the Leakage path 13 - parallel to the seal 5 -, ie into the groove 8, and how the leak oil 16 is fed from there via the leak oil channel 15 to the suction side 12 and thus to the tank oil.
• Fig. 1 the printing side 11, i.e. the high pressure is sealed, at least predominantly within the housing interior 17 or directly adjacent to it.
• seals 18, 19, 20, 21 are provided opposite the housing cover 3 and the bearing flange 4, these also being sealing rings and / or combination seals. Consequently, the first-mentioned seals 5, 6 are essentially exposed to a lower pressure close to the suction-side pressure or the tank pressure, which significantly improves the overall sealing effect of the pump.
• Fig. 4 shows three specific configurations of the groove, which can be both the groove 8 formed in the end face 7 of the housing 2 and the groove 9 formed in the bearing flange 4.
• Fig. 4 shows in the upper representation that the groove 8 or 9 to form the leakage path 13 is formed much wider than is necessary to accommodate the seal 5 or 6. Due to this wider configuration, the leakage path 13 is formed directly next to the seal 5 or 6, specifically on the inside of the pressure.
• the exemplary embodiment shown in FIG. 4 below - in the middle - shows a step-like configuration of the groove 8 or 9, the seal 5 or 6 being arranged in the lower-lying groove area.
• the leakage path 13 is at a somewhat higher level than the groove base of the lower groove area which receives the seal 5 or 6.
• the bottom illustration in FIG. 4 shows a two-part groove 8 or 9, the leakage path 13 being separated in the context of this exemplary embodiment by a web 22 from the region of the groove 8 or 9 receiving the seal 5 or 6, the web 22 being lower than the outer wall 23 of the groove 8 or 9 or the leakage path 13 is designed so that, with a sufficient amount of leakage oil, it can reach the seal 5 or 6 directly.
• a supply channel 113 extends for the fluid.
• an injector device 114 which serves to convey the fluid, is provided, which works similarly to a water jet pump. This injector device 114 injects fluid under high pressure into a blasting chamber 115 located upstream of the conveying devices 1, and there into the fluid emerging from the feed channel 113, thereby accelerating the fluid or thereby entraining the fluid.
• the feed channel 113 opens on both sides of the conveying device 1, each with a partial channel 116, into a - separate - blasting chamber 115, the injector device 114 emitting on both sides, so that a blasting nozzle 117 of the injector device 114 is directed into each of the two blasting chambers 115.
• FIG. 5 and 6 together show that the injector device 114 is arranged centrally above the conveyor device 1.
• the jet nozzles 117 are aligned in such a way that the fluid injected via the jet nozzle 117 under high pressure strikes the fluid to be accelerated approximately in its direction of flow, so that acceleration of the fluid coming from the tank is again favored.
• the fluid reaches the two jet nozzles 117 via the supply channel 113, the valve bore 125 and the outflow bores 126.
• FIG. 5 and 6 also show that the sub-channels 116 of the feed channel 113 divided on both sides of the conveyor 1 are approximately of the same length, since the feed channel 113 is also divided approximately centrally over the conveyor 1.
• Fig. 5 shows that the blasting chamber 115 formed on both sides of the conveyor 1 is largely incorporated into the housing cover 3 on one side and in the bearing flange 4 on the other side.
• the jet nozzles 117 are directed orthogonally to the wall 118 of the housing cover 3 opposite the outlet of the feed channel 113 on one side and to the wall 119 of the bearing flange 4 opposite the outlet of the feed channel 113.
• the wall 119 of the bearing flange 4 is designed in such a way that it approximately uniformly distributes the accelerated fluid impinging there by lateral discharge.
• the flow path of the fluid is identified by reference number 120.
• the walls 119, 120 guide the fluid in the manner of a guide device into suction channels 121 formed on both sides, so that the fluid is divided again.
• the suction channels 121 lead to suction kidneys (not shown in the figures) of the conveying device 1, these being arranged downstream of the immediate suction area 122 of the conveying device 1.
• FIG. 8 further clearly shows that the suction channels 121 leading to the suction kidneys or to the suction area 122 are of approximately the same length, so that the pressure conditions prevail on both sides in the same pressure conditions and an equal volume of fluid is made available.
• FIG. 7 only showing the housing 2 in an end view opposite the housing cover, the openings of the supply duct 113 or the sub-duct 116 and the injector device 114 or the jet nozzle there 117 are shown.
• a separate representation of the wall 118 of the housing cover 3 corresponding to the representation of the bearing flange 4 in FIG. 8 is omitted for the sake of simplicity.
• Fig. 7 further shows that the supply channel 113 is fluidly connected to a pressure limiting pilot (not shown in Fig. 7) for returning pilot oil, namely via a special pilot oil channel 123. Furthermore, a leak oil channel 124 opens into the supply channel 113, so that returned pilot oil and mix leakage oil within the supply channel 113 with the fluid coming from the tank. The resulting total amount of fluid is then released from the The supply channel 113 or the sub-channel 116 is acted upon by the fluid under high pressure and thereby accelerated via the injector device 114 or via the outflow bores 126 and via the jet nozzles 117.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Rotary Pumps (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)

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• 1999
  • 1999-08-13 US US09/762,789 patent/US6413064B1/en not_active Expired - Fee Related
  • 1999-08-13 JP JP2000565301A patent/JP2002522707A/ja active Pending
  • 1999-08-13 EP EP99952381A patent/EP1108144A1/de not_active Withdrawn
  • 1999-08-13 DE DE19981557.7T patent/DE19981557B4/de not_active Expired - Fee Related
  • 1999-08-13 WO PCT/DE1999/002529 patent/WO2000009888A2/de not_active Application Discontinuation
  • 1999-08-13 EP EP03005717A patent/EP1323926B1/de not_active Expired - Lifetime
• 2002
  • 2002-04-18 US US10/125,251 patent/US20020110459A1/en not_active Abandoned
• 2009
  • 2009-11-24 JP JP2009265895A patent/JP5140059B2/ja not_active Expired - Fee Related

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