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
  • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
• • 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
  • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
  • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
  • F04C29/122—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
  • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
  • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
  • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
  • F04C18/123—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially or approximately radially from the rotor body extending tooth-like elements, co-operating with recesses in the other rotor, e.g. one tooth

Definitions

• the invention relates to a rotary piston machine with a chamber formed in a housing, in which three-bladed rotors rotate in opposite directions about parallel, mutually offset axes and mesh without contact and form separate cells with the peripheral wall of the chamber.
• Blower known.
• the inlet and outlet are aligned with each other on a line that is perpendicular to the axes of the rotors.
• the volume flow is conveyed through the interlocking wings in the chamber and pushed out at the outlet without internal compression.
• Such a rotary lobe machine is particularly suitable as a supercharger for relatively high volume flows.
• the invention provides a rotary lobe machine with three-bladed rotors, which works with internal compression and internal expansion and is also suitable for generating pressure and vacuum, even with relatively small volume flows.
• the claw-like wings of the rotors together with the chamber form a suction cell which increases their volume by the rotation of the rotors and a pressure cell which reduces their volume by the rotation of the rotors. Since the rotary lobe machine works with internal compression and at the same time with internal expansion, it is suitable for the simultaneous generation of pressure and negative pressure.
• the rotors with the chamber form two charging cells which are initially separate from one another in the course of the rotation of the rotors and which are combined with one another to form the pressure cell during the further rotation of the rotors.
• a media stream can be fed in via the charging cells, so that a corresponding - 2 -
• the charging cells are essentially isobar and isochoric in the pump chamber before they are combined; the medium in the charging cells experiences essentially no change in pressure and no volume when the charging cells are displaced.
• the geometry of the rotors is determined by the requirement to simultaneously separate the cells required for the generation of pressure and vacuum in the chamber. Since the rotors interact without contact with one another and also with the peripheral wall of the chamber, no wear occurs in the region of the chamber.
• the sealing gap between the rotors can be kept very small by optimizing their geometry; in practical versions it is only a fraction of a millimeter, so that good pressure and vacuum values are guaranteed. These values become even better with increasing operating time, since the deposits that form over time lead to a reduction in the size of the sealing gaps.
• the rotary piston machine according to the invention is particularly suitable for use as a pump for the simultaneous generation of compressed air and
• Vacuum In this application, it is particularly suitable for use in the paper processing industry, especially when no - separate provision or adjustment of compressed air and vacuum is required.
• Compressed air is e.g. needed to blow on a stack of paper to support sheet separation.
• the pulsating generation of compressed air by such a pump proves to be expedient here, since the edges of the paper can be separated more easily by compressed air which occurs intermittently. In such applications, vacuum is also required to suck up the top sheet of paper.
• FIG. 1 shows a longitudinal section of the rotary lobe machine according to the invention
• Figure 2 is a view along line II-II in Figure 1;
• Figure 3 is a view along line III-III in Figure 1;
• Figures 4a to 4h are schematic views of different rotor positions to explain the mode of operation.
• the rotary piston machine according to the invention is described below using the example of a pump for the simultaneous generation of compressed air and vacuum. However, the invention is not restricted to such an application.
• the single-stage pump for the simultaneous generation of compressed air and negative pressure has a housing which consists of a load-bearing central part 10, a housing cover 12 placed on one side of the central part 10, a housing ring 14 attached to the other side of the central part 10 and one on the housing ring 14 adjoining cover plate 16 there.
• a pump chamber 18 is formed between the middle part 10, the housing ring 14 and the cover plate 16.
• housing cover 12 and the central part 10, two shafts 20, 22 are mounted parallel to one another and offset from one another in floating ball bearings.
• a pinion 24, 26 is seated on each shaft 20, 22.
• the pinions 24, 26 are in meshing engagement with one another, so that the shafts 20, 22 rotate in opposite directions synchronously with one another.
• the lower shaft 22 is led out of the housing cover 12.
• Each of the rotors 30, 32 is adjustably attached to the associated shaft 20 and 22, respectively.
• each rotor 30, 32 has three blades 30a and 32a, respectively.
• the pump chamber 18 has a side view in the form of two intersecting circles, which are joined together in the form of an "8".
• the blades 30a of the rotor 30 have a shape that is different from the shape of the blades 32a of the rotor 32.
• the geometry of the wings 30a, 32a and the pump chamber 18 is determined so that at - 4 -
• the rotation of the rotors 30, 32 a plurality of separate cells are formed, as explained in more detail below with reference to FIGS. 4a to 4h, in that the vanes 30a, 32a contact-free with a sealing gap of a fraction of 1 mm one above the other and along the outer circumference of the pump chamber 18 slide.
• the cover plate 16 is provided with a series of cutouts, which are closed off from the outside by an attached closure plate 36.
• Two pipe sockets 42, 44 are screwed into the closure plate 36.
• the upper pipe socket 42 forms the suction connection and is connected to a recess 50 of the cover plate 16.
• the lower pipe socket 44 forms the pressure connection and is connected to a recess 52 in the cover plate 16.
• Two further cutouts 54a, 54b in the cover plate 16 are open to the outside and form charging ports.
• FIG. 4a shows the rotors 30, 32 in a rotational position in which their blades 30a, 32a form a closed cell 60, which is only connected to the recess 50, with the wall of the pump chamber 18. This cell 60 enlarges in the further
• This cell 60 is therefore a suction cell.
• FIG. 4c shows two cells 62a, 62b which are separate from one another and which arise immediately after the state shown in FIG. 4b in that the cell 60 has been separated into two sub-cells.
• the cell 62a assigned to the rotor 30 already borders the recess 54a, and the cell 62b assigned to the rotor 32 approaches the recess 54b.
• the cells 62a, 62b are connected to the recesses 54a and 54b leading to the atmosphere and are filled with air and charged to ambient pressure, so that the air mass flow is increased.
• the cells 62a, 62b are thus charging cells.
• the pressure cell 64 reduces its volume.
• Cell 64 compressed air is pushed out via the recess 52 to the pipe socket 44, as illustrated in FIGS. 4g and 4h.
• the pump chamber 18 is free of any lubricant, since the rotors 30, 32 operate without contact. To the drive side is the
• This arrangement also facilitates cooling.
• the housing can be equipped with cooling fins, and cooling air is guided from the cover plate 16 via the housing ring 14, the middle part 10 and the housing cover 12 by a cooling fan arranged on the side of the housing cover 12.
• a resonance damper which is matched to the operating frequency of the pump, is used to dampen the operating noise. Due to the three-wing design of the rotors, this frequency is three times the speed of the shafts 20, 22. The increased operating frequency makes it easier to accommodate the resonance damper, since its length is reduced accordingly.
• the described flying storage of the rotors is advantageous up to a volume flow of approximately 300 m3 / h. Pumps with larger
• Volume flow is preferably formed with rotors mounted on both sides. In this case, connections are left out in both scite plates.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Applications Or Details Of Rotary Compressors (AREA)
• Rotary Pumps (AREA)

Priority Applications (4)

Applications Claiming Priority (2)

Publications (1)

Family

ID=7866414

Family Applications (2)

Family Applications After (1)

Country Status (7)

Cited By (1)

Families Citing this family (21)

Citations (5)

Family Cites Families (27)

• 1998
  • 1998-04-30 DE DE19819538A patent/DE19819538C2/de not_active Revoked
• 1999
  • 1999-04-28 US US09/673,641 patent/US6439865B1/en not_active Expired - Fee Related
  • 1999-04-28 CN CN99805636A patent/CN1128935C/zh not_active Expired - Fee Related
  • 1999-04-28 EP EP99948559A patent/EP1076760B1/de not_active Expired - Lifetime
  • 1999-04-28 US US09/673,640 patent/US6364642B1/en not_active Expired - Fee Related
  • 1999-04-28 JP JP2000547347A patent/JP2002513880A/ja active Pending
  • 1999-04-28 EP EP99923485A patent/EP1075601B1/de not_active Expired - Lifetime
  • 1999-04-28 KR KR1020007011978A patent/KR100556077B1/ko not_active Expired - Fee Related
  • 1999-04-28 DE DE59902761T patent/DE59902761D1/de not_active Expired - Lifetime
  • 1999-04-28 KR KR1020007011977A patent/KR100608527B1/ko not_active Expired - Fee Related
  • 1999-04-28 DE DE59906193T patent/DE59906193D1/de not_active Expired - Lifetime
  • 1999-04-28 WO PCT/EP1999/002881 patent/WO1999057419A1/de not_active Ceased
  • 1999-04-28 CN CN99805637A patent/CN1105820C/zh not_active Expired - Fee Related
  • 1999-04-28 WO PCT/EP1999/002882 patent/WO1999057439A1/de not_active Ceased
  • 1999-04-28 JP JP2000547364A patent/JP2002513887A/ja not_active Ceased

Patent Citations (5)

Non-Patent Citations (1)

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