Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C1/00—Rotary-piston machines or engines
  • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
  • F01C1/082—Details specially related to intermeshing engagement type machines or engines
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C19/00—Sealing arrangements in rotary-piston machines or engines
  • F01C19/10—Sealings for working fluids between radially and axially movable parts
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
  • F01C21/10—Outer members for co-operation with rotary pistons; Casings
  • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
  • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
• • 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
  • F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
  • F04C3/06—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees
  • F04C3/08—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
  • F04C3/085—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing the axes of cooperating members being on the same plane

Definitions

• the invention relates to a rotary piston engine, according to the preamble of the main claim.
• a rotary piston machine is known (DE-PS 4241320) as a pump, compressor or motor, in which run the combs of teeth, a rotating drive member for limiting work spaces on a cycloid surface of a likewise toothed driven part and this drive. Between the teeth of the driving part and the driven part, the said work spaces are formed, which are increased or reduced during the rotation of the parts for their work or to produce the conveying effect on a medium.
• Internal combustion engines for example, as a feed pump in diesel injection systems or as a feed pump or as a pressure and feed pump of gasoline injection systems, can serve.
• connection of the housing can be given in various ways, for example, as a screw connection between two "pots" on the one hand surround the pump and on the other hand the electric motor, or there may be a Verbörtelung between a cover part and a cup part, depending on how this for the Decisive for the invention is that in the motor housing, which are arranged part related to the electric motor, such as the magnets and the bearing of the rotor and that the pump housing are housed in the machine housing, including the Zu - And Abström vibration for the medium.
• the claimed bushing has been proposed earlier, but is not part of the prior art. However, it plays in conjunction with the individual features of claim 1 and their embodiments a significant role.
• Such an "electric pump” according to the invention is not restricted in its application as a fuel pump, but can be used depending on the size and performance of liquid or gaseous media, with much higher pressures can be generated than in the known Kraf stoffo pumps (from Robert Bosch GmbH odgl. ).
• the bearing bush is connected to a bottom bearing for the driven part, on which the driven part is supported on its side facing away from the drive part.
• bearing bush and bottom bearing on the same axis, perpendicular to the bearing surface stands, on which the output part is supported.
• the rotors run in an inner housing in which open to the rotors towards the suction channel and the pressure channel are arranged.
• This inner housing is rotatably and not floating within the rest of the machine housing and in particular against rotation of the bottom bearing.
• the inner housing may be arranged in an additional housing bushing and secured there against turning.
• This housing socket in turn, can be stored in the outer machine housing.
• the rotors run in a recess (of the inner housing), which is open and cylindrical to the driven side, and closed to the drive side and formed spherically.
• the drive part can be supported, while the driven part is held on the cylindrical side by the bearing bush and the bottom bearing in its working position.
• the drive part has an inner spherical region on which the drive part with a correspondingly shaped end face, or the bearing bush of the driven part can be supported.
• the driven part is axially loaded in the direction of the drive part.
• the output member is loaded by a spring force in the direction of the drive part.
• a spring force may be particularly advantageous in the starting phase of such a pump in order to achieve the required for the promotion of tightness between the working edges of the intermeshing teeth.
• the pressure channel of the machine is connected to a space between the driven part and the housing (bottom bearing) on the side facing away from the drive part. This ensures that when the medium has reached a certain pressure in the pressure channel, the driven part is pressed against the drive member so that thereby a better tightness between the flanks can be achieved.
• the rotor is mounted with its one shaft in a fixed bearing, which is supported by the inner housing and on which the drive member is axially supportable. It is thus a both as a radial bearing for the engine as a thrust bearing for the drive part, the latter particularly causes a reduction in the friction losses between the drive part and the inner housing.
• the transitions between the mutually facing the axial support serving spherical bearing surfaces and the work space delimiting tooth surfaces are rounded at the rotors.
• the radius of such rounding preferably has at least 1 mm. Basically, this radius depends on the size of the pump parts.
• short-circuit channels, or short-circuiting grooves are arranged in the bottom surface of the rotors, and in particular before the opening of a suction or pressure channel adjacent work spaces are connected to each other at To compensate for the changing volumes of the work spaces.
• the delivery chambers change between the parts, with the associated flanks of the teeth of one part to slide over the corresponding surfaces of the other part, so that the lying between the teeth spaces from which the actual work spaces arise, here act as harmful spaces. While an overpressure would be created in the one harmful room, a negative pressure would be created in the adjacent room.
• By the invention is a pressure equalization of the rooms, which benefits the pump efficiency.
• FIG. 1 A fuel delivery pump according to the invention in longitudinal section according to the arrow I in Figure 2;
• Fig. 2 is a longitudinal section through a part of the feed pump according to the line II-II in Figure 1;
• Fig. 3 The associated rotors of the pump in longitudinal section on an enlarged scale, and in exploded view;
• Fig. 4 The inner housing of the pump in longitudinal section;
• Fig. 5 The inner housing in the radial side view
• FIG. 6 shows the inner housing in the axial view according to the arrow VI in Fig. 4th
• the illustrated fuel delivery pump has a
• Rotary pump 1 and an electric motor 2 driving this which are arranged in a motor housing 3 and a housing cover 4 screwed thereon.
• the electric motor is greatly simplified represents with a rotor 5 and a magnet ring 6, and an axial closure part 7 of the motor housing 3, which is connected to the motor housing 3 and sealed to this.
• a pivot bearing 8 of the rotor 5, and the pressure port. 9 arranged for the fuel discharge.
• the fuel pump is designed as a submersible pump, in which via suction ports 10, which are only indicated here, the fuel passes into the pump to then leave the pump via the pressure port 9 again.
• the electric motor 5, 6 flows around the fuel within the motor housing 3.
• the second pivot bearing of the rotor 5 is formed as a fixed bearing 11, which is arranged in a corresponding bore on the end face of an inner housing 12 of the rotary lobe pump 1 and on which the drive member 17 can be supported axially.
• This inner housing 12 is arranged outside in a housing bushing 13, which in turn is sealed to the motor housing 3, partially clamped in this and partially within the housing cover 4.
• a recess 14 is provided in the inner housing 12, with a cylindrical section 15 and a spherical section 16.
• two pump rotors namely a drive part 17 and a driven part 18.
• the drive part 17 is driven by the shaft 20 of the electric motor 2 and transmits its rotary motion to the driven part 18.
• On the front sides of the drive part 17 and the abrasion part 18 are cycloidal gears provided, as can be seen in Figure 3, and have the corresponding facing work surfaces 19.
• 14 Pumparbeitsbank 21 are formed between the working surfaces 19 and the inner wall of the recess, as can be seen in Figure 2.
• the recess 14 is closed on the output side by a bottom bearing 22, which is arranged obliquely to the axis of the recess 14 in order to achieve the required conveying angle and which is sealed at 23 to the inner housing 12.
• a bearing pin 24 is arranged and perpendicular to the recess 14 facing end side of the bottom bearing 22, on which via a blind bore 25 ( Figure 3) the output member 18 is mounted.
• the output member 18 is also loaded in the direction of drive member 17 by a coil spring 26 and a ball 27, wherein the spring is disposed in a blind bore 28 of the journal 24 and the ball on the front side of the blind bore 25th supported.
• the output part 18 is supported via a spherical surface 29 facing the drive part 17 on a corresponding spherical recess 30 on the drive part 17 (FIG. 3).

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Applications Claiming Priority (2)

Publications (2)

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• 2004
  • 2004-09-10 WO PCT/DE2004/002034 patent/WO2005024237A1/fr active Application Filing
  • 2004-09-10 EP EP04786755A patent/EP1664541B1/fr active Active
  • 2004-09-10 JP JP2006525623A patent/JP5053637B2/ja active Active
  • 2004-09-10 DE DE102004044297A patent/DE102004044297A1/de not_active Ceased
  • 2004-09-10 CA CA2536279A patent/CA2536279C/fr not_active Expired - Fee Related
  • 2004-09-10 US US10/571,244 patent/US7390181B2/en active Active
  • 2004-09-10 BR BRPI0414231-4A patent/BRPI0414231B1/pt not_active IP Right Cessation
  • 2004-09-10 ES ES04786755T patent/ES2381002T3/es active Active
  • 2004-09-10 PL PL04786755T patent/PL1664541T3/pl unknown
  • 2004-09-10 AT AT04786755T patent/ATE549516T1/de active

Non-Patent Citations (1)

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