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
  • 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
• • 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
  • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
  • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
• • 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
  • F04C2240/00—Components
  • F04C2240/30—Casings or housings
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T137/00—Fluid handling
  • Y10T137/8593—Systems
  • Y10T137/85978—With pump

Definitions

• the invention relates to a delivery unit according to the preamble of the main claim. It is already a delivery unit known from DE 10 2004 026 048 Al, with a drive rotor and driven by the drive rotor output rotor, which are mounted in a housing, cooperating via a respective spur toothing mesh and suck in fluid via at least one inlet and express through an outlet , wherein the inlet and the outlet are separated by two dividers.
• a speed control or a bypass control or for gases suction suction can be done.
• a speed control is energetically efficient, but very expensive, since a variable speed electric motor must be used.
• the bypass control the fluid is conveyed from the outlet via a bypass back to the inlet, but this is energetically unfavorable and associated with hydraulic losses.
• the main claim has the advantage that the inlet side of the flow rate very easily and with little hydraulic losses controllable and outlet side in the case of conveying gases, the internal compression is controlled by at least one of the partitions at least one control port, the opening cross-section is controlled with a spool.
• the design according to the invention requires less space for the volume flow control compared to the prior art, is less expensive and more energy efficient.
• the volume increases in the region of the inlet in the direction of rotation and decreases their volume in the region of the outlet in the direction of rotation, wherein the maximum volume of the working chambers at a first transition point in the region of a first divider and the minimum volume at a second transition point is formed in the region of a second divider.
• At least one Steueröffhung connected to the inlet side is arranged in a region of the first divider, which lies in the direction of rotation behind the first transition point, since the respective working chambers in this way are fluidly connected to the inlet beyond the position of their maximum volume.
• At least one Steueröffhung connected to the outlet side is arranged in a region of the first separating web, which lies in the direction of rotation behind the first transition point, since in this way the internal compression of the delivery unit is controllable.
• FIG. 1 shows in section a delivery unit, in which the invention could be applied
• Figure 2 is a sectional view of a rotor housing according to the invention according to Figure 1 according to a first embodiment
• Figure 3 shows a three-dimensional view of the rotor housing according to Fig.l and Fig.2 and
• FIG. 4 shows a sectional view of a rotor housing according to the invention according to Figure 1 according to a second embodiment. Description of the embodiment
• FIG. 1 shows in section a delivery unit, to which the invention could be applied
• the delivery unit 1 has a drive rotor 2 and driven by the drive rotor 2 output rotor 3, both of which are mounted in a rotor housing 4.
• the drive rotor 2 is driven by a motor 5, for example an electric motor, via a drive shaft.
• the two rotors 2, 3 each have an end toothing 6, for example a cycloid front toothing, which interact in a combing manner and suck in fluid via at least one inlet 7 in the rotor housing 4 and express via an outlet 8 in the rotor housing 4 according to the positive displacement principle. Between the front teeth 6 of the rotors 2,3 working chambers 14 are formed.
• the axes of rotation of the two rotors 2, 3 are at an angle to one another, ie they enclose an angle that is not equal to 180 degrees, so that the volume of the working chambers 14 alternately increases and decreases during one revolution of the drive rotor 2.
• the volume of the chambers 14 increases in the direction of rotation and on
• the rotor housing 4 is surrounded by a pump housing 15.
• the inlet 7 and the outlet 8 of the rotor housing 4 are sealed within the pump housing 15 against each other, for example by means of dividing walls 16,17 or other sealing means.
• the dividing walls 16, 17 lie, for example, in the region of the partitions 9, 10.
• the working chambers 14 For conveying liquids, the working chambers 14 must be fluidly connected to either the inlet 7 or the outlet 8, so that no closed chambers 14 arise in which the incompressible liquid is compressed by the reduction in volume of the chambers 14 and an unacceptably high pressure is created, which the delivery unit could damage.
• the rotors 2, 3 are also mounted so that they are forced apart at a predetermined overpressure such that the overpressure is reduced by shorting the adjacent working chambers.
• closed working chambers 14 are permissible because gases are compressible and so-called internal compression within the closed chambers 14 is desired.
• FIG. 2 shows a sectional view of the rotor housing according to the invention according to Figure 1 according to a first embodiment. In the view of Figure 2 are opposite to the view - A -
• the inlet 7 and the outlet 8 are separated in the circumferential direction of the rotor housing 4 by two separating webs 9,10.
• At least one of the separating webs 9, 10 has at least one control opening 12 whose opening cross-section can be changed with a movably mounted control slide 13.
• a plurality of control openings 12 are arranged one behind the other in the direction of rotation of the rotors 2, 3.
• the control opening 12 is an example slot-shaped passage opening.
• the spool 13 is for example electrically, pneumatically or hydraulically adjustable and interacts with the at least one control opening 12 opening or closing together.
• a control opening 12, which is not fully covered by the spool valve 13, is connected to the inlet 7 or the outlet 8 and discharges into one of the working chambers 14 depending on the position of the rotors.
• the spool 13 can rotate in or against the direction of rotation of the rotors 2, 3 and /. or axially adjustable with respect to one of the axes of rotation.
• the maximum volume of the working chambers 14 is formed at a first transition point A in the region of the first separating web 9 and the minimum volume at a second transition point B in the region of the second separating web 10.
• the dividers 9,10 cover a predetermined angular range around the transition points A, B from around. As viewed in the direction of rotation from the first transition point A to the second transition point B, the volume of the chambers 14 decreases and from the second transition point B to the first transition point A.
• the at least one control opening 12 on the first separating web 9, viewed in the direction of rotation of the rotors 2, 3, is arranged in front of the dividing wall 16 in such a way that it is flow-connected to the inlet 7 in the opened state.
• the at least one control opening 12 is arranged, for example, such that it lies in a region of the first separating web 9, which is behind the first in the direction of rotation
• Transition point A is located.
• the respective working chambers 14 can be variably connected beyond the first transition point A via the control opening 12 to the inlet 7, so that, due to the reduction in volume of the respective working chamber 14, a part of the aspirated fluid of the working chamber again 14 is pushed back into the inlet 7.
• By the "late” Closing the inlet 7 decreases the required mass per revolution, whereby a simple and energy-efficient flow control on the inlet side is achieved.
• the at least one control opening 12 can alternatively also be formed in the direction of rotation of the rotors 2, 3 before the first transition point A on the first separating web 9.
• the volumetric flow control is accomplished by "early" closing of the working chambers 14 at the inlet 7, whereby the working chambers 14 are not completely filled and the hydraulic throttling losses are reduced compared to the "late” closing of the inlet 7.
• one or more control openings 12 in the direction of rotation may be provided in front of the first transition point A and one or more control openings 12 behind the first transition point A for this case.
• FIG. 3 shows a three-dimensional view of the rotor housing according to Fig.l and Fig.2.
• the parts which are identical or functionally identical to the view according to FIG. 1 and FIG. 2 are identified by the same reference numerals.
• FIG. 4 shows a sectional view of the rotor housing according to the invention according to Figure 1 according to a second embodiment.
• the parts which are identical or functionally identical to the view according to FIGS. 1 to 3 are identified by the same reference numerals.
• the at least one Steueröffhung 12 is also disposed on the first divider 9, but this is fluidly connected in the open state with the outlet 8 by being formed on the first divider 9 in the direction of rotation behind the partition wall 16.
• the inner compression is controlled by means of the Steueröffhungen 13 and thereby achieves an energetically optimal operation of the delivery unit. Due to the internal compression, the second version is only suitable for the delivery of gases.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Rotary Pumps (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)

Priority Applications (4)

Applications Claiming Priority (2)

Publications (2)

Family

ID=41794756

Family Applications (1)

Country Status (6)

Citations (3)

Family Cites Families (7)

• 2008
  • 2008-10-02 DE DE200810042564 patent/DE102008042564A1/de not_active Withdrawn
• 2009
  • 2009-09-10 US US13/121,699 patent/US20110186158A1/en not_active Abandoned
  • 2009-09-10 EP EP09782859A patent/EP2331822A2/de not_active Withdrawn
  • 2009-09-10 WO PCT/EP2009/061739 patent/WO2010037620A2/de active Application Filing
  • 2009-09-10 CN CN200980139231.8A patent/CN102171457B/zh not_active Expired - Fee Related
  • 2009-09-10 BR BRPI0920534A patent/BRPI0920534A2/pt not_active IP Right Cessation

Patent Citations (3)

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