Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D13/00—Pumping installations or systems
  • F04D13/02—Units comprising pumps and their driving means
  • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
  • F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
  • F04D13/086—Units comprising pumps and their driving means the pump being electrically driven for submerged use the pump and drive motor are both submerged
• • 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
  • F04C11/008—Enclosed motor pump units
• • 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
  • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
  • F04C13/008—Pumps for submersible use, i.e. down-hole pumping
• • 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
  • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
  • F04C15/008—Prime movers
• • 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
  • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
  • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
• • 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
  • F04C2270/00—Control; Monitoring or safety arrangements
  • F04C2270/70—Safety, emergency conditions or requirements
  • F04C2270/701—Cold start

Definitions

• the invention relates to a drive unit for a sub-oil pump according to the preamble of claim 1, and a pump, in particular sub-oil pump according to the preamble of claim 10.
• Drive units are used to drive so-called sub-pumps, which serve the promotion of oil, such as gear oil.
• the pump with the preferably integrated drive unit is completely or partially immersed in a reservoir with the oil to be delivered.
• Known drive units have a housing which encloses an engine compartment. In this a rotor is arranged. This ultimately serves the rotary drive of a pump unit by being connected via a drive shaft with the same.
• a first fluid path from a sub-oil environment of the housing into the engine compartment is provided.
• the pump Since the pump is completely or partially immersed in the oil to be pumped by it, the environment of the housing has oil, which can penetrate via the first fluid path into the engine compartment and so cool the drive unit.
• a disadvantage of known drive units is that they in particular run during shutdown phases over the first fluid path with oil, so that a significant part of or even the entire engine compartment is flooded with oil. When restarting the pump and during operation, so-called churning losses occur because the rotor must rotate in the oil which is present in the engine compartment, with a drag torque acting on it.
• the invention is therefore based on the object to provide a drive unit and a pump, which do not have the disadvantages mentioned.
• Claim 1 is created. This is characterized by at least a second fluid path from the engine compartment to an air environment of the housing, the one Pushing oil from the engine compartment through the rotor allows.
• the air environment is located above an oil level below which the pump is at least partially located.
• the second fluid path is provided on the drive unit in such a way that accelerated oil is expelled from the engine compartment when it starts up due to its rotational movement.
• oil which adheres to the rotor is accelerated accordingly and ultimately ejected.
• oil, which does not adhere directly to the rotor, but is arranged in its surroundings, can be entrained, accelerated and ejected. In this way, a significant portion of the oil is carried out of the engine compartment, so that churning losses are minimized.
• a drive unit is preferred in which the second fluid path comprises a Ausschieböff- opening provided in a peripheral wall of the housing.
• the second fluid path may preferably include a snorkel when the Ausschiebö réelle is disposed below the oil level. The snorkel juts out over the oil level into the air environment.
• the Ausschiebö réelle has a passage surface which is arranged substantially perpendicular to an imaginary circumferential line of a rotational direction of the rotor.
• the oil which is accelerated by the rotor has a main speed component which is oriented tangentially to the direction of rotation of the rotor. If the passage surface of the ejection opening is oriented substantially perpendicular to an imaginary circumferential line of the rotational direction of the rotor, the main speed component is essentially perpendicular to the passage surface. This means that the accelerated oil can emerge particularly resistant, with it being pushed out almost directly by the rotor.
• a drive unit in which the Ausschiebö réelle by a - seen in the radial direction - back or projecting portion of the circumference Forming of the housing is formed.
• These are structurally particularly simple forms to form the Ausschiebö réelle, at the same time the oil can be pushed in the direction of its main speed component.
• a drive unit in which at least one third fluid path is provided from the air environment of the housing to the engine compartment.
• this ambient air can flow into the engine compartment when the pump is partially submerged and in particular the at least one third fluid path is in fluid communication with the ambient air.
• an oil-air mixture eventually sets in the engine compartment. This significantly less churning occur as when the engine compartment is filled with oil.
• a drive unit which is characterized in that the third fluid path comprises an opening in the peripheral wall of the housing.
• the third fluid path may also preferably include a snorkel when the pump with the opening encompassed by the third fluid path is arranged below the oil level. The snorkel protrudes beyond the oil level into the air environment.
• a drive unit is also preferred, which is characterized in that the first fluid path extends via a bearing of a drive shaft and a bypass opening, via which the engine compartment is in fluid communication with a space encompassing the drive shaft.
• oil delivered by the pump can reach the engine compartment via a bearing of the drive shaft and the bypass opening, whereby no separate fluid connection has to be provided for this purpose. So it is quasi leakage oil, which occurs anyway in the field of storage, advantageously used for cooling and lubrication of the drive unit.
• a drive unit is preferred, which is designed as an electric motor. This includes a stator. The stator cooperates in a known manner with the rotor.
• a drive unit which is characterized in that the rotor engages around the stator as an external rotor.
• This has the advantage that the rotor - viewed in the radial direction - is provided as far as possible outside and as close as possible to a circumferential wall of the housing, so that it can push out the oil directly over the at least one second fluid path.
• a pump in particular a sub-oil pump is provided, which has the features of claim 10.
• This is characterized by a drive unit according to one of claims 1 to 9. Characterized in that in the drive unit of the pump at least a second fluid path is provided, which leads from the engine compartment to the air environment of the housing and allows expulsion of oil from the engine compartment through the rotor, churning losses of the engine can be significantly reduced.
• Figure 1 is a schematic longitudinal sectional view of an embodiment of a
• Figure 2a is a schematic detail view in cross section of the drive unit
• Figure 2b is a schematic detail view in cross section for another
• Figure 1 shows a schematic view of an embodiment of a pump 1 in longitudinal section.
• This comprises a drive unit 3 and a pump unit 5.
• the drive unit 3 and the pump unit 5 are preferably integrally formed. This is indicates that they form a structural unit, so that the pump 1 represents an assembly.
• the drive unit 3 comprises a housing 7. This is in the illustrated
• Embodiment pot-shaped It encloses an engine compartment 9. An open side of the cup-shaped housing 7 is closed by a carrier 1 1, which carries the pump unit 5. He is here designed as a lid, which closes the housing 7 tight.
• a rotor 13 is arranged in the engine compartment 9, a rotor 13 is arranged. This is connected to a drive shaft 15, which in turn is connected to the pump unit 5. In this way, during operation of the pump 1, the rotor 13 causes a rotational movement of the rotatable parts of the pump unit 5 about a longitudinal axis of the drive shaft 15.
• a radial direction refers to a direction that is perpendicular to this.
• the pump 1 is designed here as gerotor pump.
• the pump unit 5 includes an internal gear 17 which meshes with an external gear 19.
• the pump unit 5 has a cover plate 21. It also closes off the intake area 23 and an outlet area 25, whereby oil can pass into an actual suction area via the intake area 23, which is formed by the internal gearwheel 17 and the external gearwheel 19 , Over a pressure range formed by the gears, oil is expelled over the outlet area 25. In this way, the pump unit 5 conveys oil from the suction region 23 to the outlet region 25.
• the principle of a gerotor pump is known, so that will not be discussed further.
• the pump is not as
• Gerotor pump is formed. It may for example be designed as a vane pump, radial piston pump or in any other suitable manner.
• the drive shaft 15 is connected to the internal gear 17 so that it is driven by the rotor 13.
• the drive shaft 15 is mounted in a first bearing 27 and preferably in a second bearing 29.
• the first bearing 27 is designed as a sliding bearing.
• the second bearing 29 is preferably designed as a ball bearing, particularly preferably as a deep groove ball bearing.
• the drive unit 3 is designed as an electric motor which comprises a stator 31.
• the drive unit 3 is designed as a synchronous motor, particularly preferably as a brushless DC motor (BLDC motor), very particularly preferably as a sensorless BLDC motor.
• the rotor 13 is designed as a permanent magnet, or it comprises areas which comprise permanent magnetic material. The principle of an electric motor, in particular a synchronous or BLDC motor is known, so it will not be discussed further here.
• the stator and the rotor are positioned and / or formed so that the bearing 29 is biased.
• a force is exerted on the bearing 29, which acts in the axial direction, and biases it.
• the bearing is designed as an axial ball bearing.
• a first fluid path 35 leads from a sub-oil environment 37 of the housing 7 into the engine compartment 9.
• the sub-oil environment is arranged below an oil level S, with the pump partially submerged below the oil level S in the exemplary embodiment shown.
• the fluid path 35 leads via the first bearing 27, which - depending on the viscosity of the oil - has a certain leakage rate, in a space 39. In the illustrated embodiment, this surrounds the drive shaft. He is also - as seen in the axial direction - limited by the first bearing 27 and preferably the second bearing 29.
• the space 39 forms an annular space around the drive shaft 15.
• a bypass opening 41 is provided, via which the engine compartment 9 is in fluid communication with the space 39.
• the bypass opening 41 may preferably be formed as a bore.
• the first fluid path 35 thus comprises the intake region 23, the
• the rate of passage of the oil along the first fluid path depends on the viscosity of the oil and thus in particular also on its temperature. If the oil heats up, for example due to the waste heat of the drive unit 3, its viscosity decreases and more oil per unit of time can pass through the fluid path.
• the drive unit 3 or the engine compartment 9 is thus supplied more oil when the oil is warmer. This causes in an advantageous manner that the drive unit 3 is cooled depending on temperature. The warmer it gets, the more oil is supplied via the first fluid path 35 for cooling and thus can carry away more heat.
• the pump 1 when the pump 1 is at least partially submerged in the oil, the engine may, during a standstill, overflow the first fluid path 35 and possibly also further bores in the housing 7. When the pump is restarted, the rotor 13 then rotates in the engine compartment 9, which is completely filled with oil, and the drag torque of the oil causes considerable losses, so-called churning losses.
• At least one second fluid path 43 is provided in the present drive unit, which leads from the engine compartment 9 to an air environment 38. This is arranged above the oil level S.
• the second fluid path 43 is formed and / or arranged so that the rotor 13 can push oil out of the engine compartment. In this case, the rotor 13 accelerates oil adhering to it during its rotation, which oil is expelled via the second fluid path 43.
• the second fluid path 43 is provided in regions in a peripheral wall 47 of the housing 7.
• the centrifugal force which is accelerated in particular in the radial direction and is entrained in the tangential direction due to the centrifugal force imparted by the rotating rotor 13, is then ejected particularly efficiently via the second fluid path 43.
• the second fluid path 43 comprises a Ausschiebö réelle 45, which is provided in the peripheral wall 47 of the housing 7.
• more than a second fluid path 43 is provided. It is possible that - seen in the circumferential direction - in the peripheral wall 47 at least two, preferably more Ausschiebö Maschinenen 45 are arranged.
• the Ausschiebö Maschinenen are either disposed above the oil level S, or they are connected to at least one snorkel, which projects beyond the oil level S, so that the second
• the passage cross-section of a second fluid path 43, or the cumulative passage cross-section of the various second Fluid paths is greater than the passage cross-section of the first fluid path 35.
• a motor that has run full at standstill empties quickly when restarting, so that splashing losses are limited to a short time after starting.
• the passage cross section of the first fluid path 35 only has to be large enough to be able to conduct a sufficient amount of oil for the cooling of the drive unit 3 into the engine compartment 9.
• gear oil typically contains a large amount of air or air bubbles dissolved in oil, so in this case, when the oil is expelled, air is released, even without ambient air flowing in. Even then there is an oil-air mixture - if necessary under negative pressure - before.
• the pump when the pump is partially immersed in deep oil, preferably at least one third fluid path 49 is provided, which leads from the air environment 38, particularly preferably via a snorkel in the engine compartment 9.
• the third fluid path 49 By means of this third fluid path 49, ambient air can then flow into the engine compartment 9 when the oil is expelled via the second fluid path 43.
• the third fluid path is preferably in fluid communication with the air environment 38.
• the corresponding area of the pump 1, which has the third fluid path 49 not be immersed in the oil.
• the third fluid path 49 includes a snorkel, which projects beyond the oil level S, when the pump 1 is completely or at least partially immersed.
• the third fluid path 49 comprises an opening 51 in the
• Circumferential wall 47 Air can flow over these, preferably when the pump protrudes with the opening 51 from the oil, or when a snorkel is provided in or at the opening 51, which protrudes from the oil.
• the rotor 13 surrounds the stator 31 as an external rotor. This is particularly advantageous because the oil adhering to the rotor 13 is thus accelerated at a large radius and in the immediate vicinity of the discharge opening 45, so that it can be easily pushed out.
• a dashed line 53 is still shown, which extends in the radial direction and is perpendicular to the peripheral wall 47 and the sectional area for the sectional views in Figure 2 indicates.
• FIG. 2 a shows a detailed view of the pump 1, namely a detail from a cross-sectional view, wherein the sectional plane in FIG. 1 is arranged at the level of the line 53.
• Identical and functionally identical elements are provided with the same reference numerals, so that reference is made to the preceding statements. Shown are in particular the rotor 13 and the housing 7 with its peripheral wall 47.
• the Ausschiebö réelle 45 has a special shape: It has a passage surface 55, which is arranged substantially perpendicular - here exactly perpendicular - to an imaginary circumferential line of rotation of the rotor 13. This is indicated in Figure 2a by the arrow P.
• the rotation of the rotor 13 is concentric with the longitudinal axis of the drive shaft 15. It is thus possible to construct peripheral lines which run concentrically to the longitudinal axis of the drive shaft 15 and thus represent quasi circumferential lines of rotation of the rotor 13.
• the passage surface 55 extends substantially at least in its point of intersection with at least one such circumferential line - here exactly - perpendicular to this.
• Oil adhering to the rotor 13 contains ne main speed component, which is oriented substantially tangential to the rotational direction of the rotor 13 and a corresponding circumferential line.
• the passage area 55 being arranged substantially perpendicular to an imaginary circumferential line of the rotational direction of the rotor 13, the oil can exit in the direction of its main speed component unhindered through the ejection opening 45. This is thus arranged or shaped so that oil can be pushed out of the rotor 13 very efficiently.
• the Ausschiebö réelle 45 is formed by a portion 57 of the peripheral wall 47, which - seen in the radial direction - springs back. Together with a region 59 of the peripheral wall 47, which, viewed in the opposite direction to the direction of rotation of the rotor 13, adjoins the recessed region 57 and does not spring back, the Ausschiebö réelle 45 is formed in a structurally simple manner. It can for example be stamped into the housing.
• the rotor 13 has an outer diameter which is only slightly smaller than an inner diameter of the housing 7.
• only a relatively small volume of oil between the rotor 13 and the peripheral wall 47 is arranged, which almost completely by the rotor 13 can be accelerated.
• the recessed region 57 then jumps back so far - seen in the radial direction - that the passage surface 55 occupies a large part of the available area between the circumferential wall 47 and the rotor 13.
• a considerable amount of the oil arranged between the rotor 13 and the peripheral wall 47 can be pushed out over the passage surface 55.
• Figure 2b shows a schematic detail view in cross section for another
• the Ausschiebö réelle 45 is formed here by a portion 57 of the peripheral wall 47, which - seen in the radial direction - protrudes. Together with a region 59 of the peripheral wall 47, which adjoins the projecting region 57 and does not project itself, the Ausschiebö réelle 45 is formed in a structurally simple manner. For example, it can also be stamped into the housing.
• Ausschiebö réelle 45 seen in the circumferential direction - in the region of the peripheral wall 47 is arranged. They are arranged either above the oil level S, or connected to at least one snorkel, which projects beyond the oil level S.
• the present drive unit and the present pump due to the second fluid path, which allows a pushing out of oil from the engine compartment 9 through the rotor 13, significantly reduced churning losses and thus have a significantly increased efficiency. This also reduces the recorded drive power, so that the drive unit and the pump are particularly economical.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Rotary Pumps (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• Motor Or Generator Frames (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=46017740

Family Applications (1)

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• 2012
  • 2012-03-13 JP JP2014501442A patent/JP2014515073A/ja active Pending
  • 2012-03-13 WO PCT/DE2012/100064 patent/WO2012130225A2/de active Application Filing
  • 2012-03-13 EP EP12717160.1A patent/EP2691651A2/de not_active Withdrawn
  • 2012-03-13 DE DE112012001476T patent/DE112012001476A5/de active Pending
  • 2012-03-13 US US14/004,061 patent/US9587638B2/en active Active
  • 2012-03-13 CN CN201280015058.2A patent/CN103443460B/zh active Active

Non-Patent Citations (1)

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