Drive unit for a submersible oil pump, with a fluid passage allowing the fluid in the motor housing to be discharged to the ambient enviroment

Abstract

A drive unit (3) for a submersible oil pump, including a housing (7), a motor compartment (9) that is surrounded by the housing (7), and a rotor (13) arranged in the motor compartment (9), whereby a first fluid path (35) leading from a submerged oil environment (37) of the housing (7) to the motor compartment (9) is provided so as to allow oil to flow from the submerged oil environment (37) into the motor compartment (9).

Claims

1. A drive unit for a submersible oil pump, comprising a housing surrounding a motor compartment; a rotor arranged in the motor compartment, a first fluid path leading from a submerged oil environment of the housing to the motor compartment so as to allow oil to flow from the submerged oil environment into the motor compartment; at least one second fluid path leading from the motor compartment to an air environment of the housing and allowing oil to be discharged to the air environment from the motor compartment by the rotor; and at least one third fluid path leading from the air environment of the housing to the motor compartment, whereby ambient air can flow through the third fluid path into the motor compartment when oil is expelled via the second fluid path.

2. The drive unit as recited in claim 1 wherein the second fluid path comprises a discharge opening arranged in a circumferential wall of the housing.

3. The drive unit as recited in claim 2 wherein the discharge opening has a passage surface arranged perpendicular to an imaginary circumferential line in the direction of rotation of the rotor.

4. The drive unit as recited in claim 2 wherein the discharge opening is formedas seen in the radial directionby a recessed or projecting area of the circumferential wall of the housing.

5. The drive unit as recited in claim 1 wherein the third fluid path has an opening in the circumferential wall of the housing.

6. The drive unit as recited in claim 1 wherein the first fluid path runs via a bearing of a drive shaft and via a bypass opening via which the motor compartment is in fluid connection with a space surrounding the drive shaft.

7. The drive unit as recited in claim 1 further comprising a stator so as to define an electric motor.

8. The drive unit as recited in claim 7 wherein the rotor surrounds the stator as an external rotor.

9. A pump comprising the drive unit as recited in claim 1.

10. A submersible oil pump comprising the pump as recited in claim 9.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The invention will be explained in greater detail below on the basis of the drawing. The following is shown:

(2) FIG. 1 a schematic longitudinal section of an embodiment of a pump with a drive unit;

(3) FIG. 2a a schematic detailed view of a cross section of the drive unit according to FIG. 1; and

(4) FIG. 2b a schematic detailed view of a cross section of another embodiment of a discharge opening.

DETAILED DESCRIPTION

(5) FIG. 1 shows a schematic view of a longitudinal section of an embodiment of a pump 1. This pump comprises a drive unit 3 and a pump unit 5. The drive unit 3 and the pump unit 5 are preferably configured integrally. This means that they form a structural unit, as a result of which the pump 1 constitutes a module.

(6) The drive unit 3 comprises a housing 7 which, in the embodiment shown, is configured so as to be pot-shaped. It surrounds a motor compartment 9. An open side of the pot-shaped housing 7 is closed by a support 11 that supports the pump unit 5. Here, it is depicted with a lid that tightly seals the housing 7.

(7) A rotor 13 is arranged in the motor compartment 9. The rotor 13 is joined to a drive shaft 15 which, in turn, is joined to the pump unit 5. In this manner, the rotor 13 brings about a rotational movement of the rotatable parts of the pump unit 5 around a longitudinal axis of the drive shaft 15 during operation of the pump 1. Whenever the term axial direction is employed, this always refers to the direction of the longitudinal axis of the drive unit 15. The radial direction refers to the direction that is perpendicular thereto.

(8) The pump 1 is configured here as a gerotor pump. Consequently, in the embodiment shown, the pump unit 5 comprises an inner gearwheel 17 that meshes with an outer gearwheel 19. Moreover, the pump unit 5 has a closure lid 21. This lid 21 closes the actual pump area with the inner gearwheel 17 and the outer gearwheel 19. It also has an inlet area 23 and an outlet area 25, whereby, via the inlet area 23, oil can get into the actual suction area that is formed by the inner gearwheel 17 and the outer gearwheel 19. Oil is expelled through the outlet area 25 via a pressure area that is formed by the gearwheels. In this manner, the pump unit 5 conveys oil from the inlet area 23 to the outlet area 25. The principle of a gerotor pump is well known, so that this will not be elaborated upon here.

(9) In other embodiments, it is possible for the pump not to be configured as a gerotor pump. It can be configured for instance, as a rotary vane pump, a radial piston pump or else in some other suitable manner.

(10) The drive shaft 15 is joined to the inner gearwheel 17, so that it is driven by the rotor 13. In this context, the drive shaft 15 is mounted in a first bearing 27 and preferably in a second bearing 29. Preferably, the first bearing 27 is configured as a sliding bearing. The second bearing 29 is preferably configured as a ball bearing, especially preferably as a deep-groove ball bearing.

(11) In the embodiment shown, the drive unit 3 is configured as an electric motor that comprises a stator 31. In particular, FIG. 1 depicts the stator windings 33, 33. Preferably, the drive unit 3 is configured as a synchronous electric motor, especially preferably as a brushless direct-current electric motor (BLDC motor), very particularly preferably as a sensorless BLDC motor. In this case, the rotor 13 is configured as a permanent magnet, or else it has sections that comprise permanent-magnetic material. The principle of an electric motor, especially of a synchronous or BLDC motor, is familiar, so that this will not be elaborated upon here.

(12) Especially preferably, the stator and the rotor are positioned and/or configured in such a way that the bearing 29 is pretensioned. In particular, between the stator 31 and the rotor 13, there is preferably a magnetic that forces the rotor 13 towards the left in FIG. 1, as a result of which the drive shaft 15 is also forced to the left. In this manner, a force is exerted onto the bearing 29 that acts in the axial direction and pretensions it. This is especially advantageous if the bearing is configured as an axial ball bearing. The pretensioning translates into a high level of stiffness, quiet running, a more precise guidance of the drive shaft 15 as well as a compensation for wear and settling processes in the bearing 29. Altogether, this accounts for a longer service life for the bearing 29.

(13) A first fluid path 35 leads from a submerged-oil environment 37 of the housing 7 to the motor compartment 9. The submerged-oil environment is located below the oil surface S, whereby, in the embodiment shown, the pump is partially submerged below the oil surface. The fluid path 35 leads through the first bearing 27which, depending on the viscosity of the oil, has a certain rate of leakageinto a space 39. In the embodiment shown, it surrounds the drive shaft. Moreover, as seen in the axial direction, it is delimited by the first bearing 27 and preferably by the second bearing 29. Altogether, the space 39 here forms an annular space around the drive shaft 15. The support 11 has a bypass opening 41 via which the motor compartment 9 is in fluid connection with the space 39. The bypass opening 41 can preferably be configured as a drilled hole. Finally, the oil leaves the submerged-oil environment 37 of the pump 1 or of the housing 7 via the inlet area 23 and via the suction area formed by the inner gearwheel 17 and the outer gearwheel 19 and, via the first bearing 27, the oil reaches the space 39 and from there, goes to the motor compartment 9 via the bypass opening 41. From the suction area that is formed by the gearwheels 17, 19, the oil inside the pump reaches the pressure area that is in fluid connection with the outlet area 25. The pressure area of the pump is likewise adjacent to the first bearing 27. It is precisely from the pressure area of the gearwheels 17, 19 where the oil is under an elevated pressure, that the oil, as leakage oil, reaches the space 39 through the bearing 27.

(14) Therefore, all in all, the first fluid path 35 comprises the inlet area 23, the suction area and especially also the pressure area of the gearwheels 17, 19, the leakage path through the bearing 27, the space 39 as well as the bypass opening 41. Thus, during operation and when the pump 1 is at a standstill, oil from the submerged-oil environment 37 reaches the motor compartment 9 via the first fluid path 35, where it is available to cool the drive unit 3.

(15) The flow rate of the oil along the first fluid path depends on the viscosity of the oil and thus especially on its temperature. If the oil heats up, for example, due to exhaust heat from the drive unit 3, the viscosity drops and more oil per unit of time can pass through the fluid path. In other words, more oil will be conveyed to the drive unit 3 or to the motor compartment 9 if the oil is hotter. This advantageously causes the drive unit 3 to be cooled as a function of the temperature. The hotter it becomes, the more oil is conveyed via the first fluid path 35 for cooling purposes, so that more heat can thus be dissipated.

(16) However, when the pump 1 is at least partially submerged into the oil, during a standstill, the motor can fill up with oil via the first fluid path 35 and, if applicable, also via additional holes drilled into the housing 7. When the pump is started up again, the rotor 13 then rotates inside the motor compartment 9 that is completely filled with oil, a process in which the drag torque of the oil causes considerable losses, so-called splash losses, to occur.

(17) In order to prevent this, the drive unit in question here is provided with at least one second fluid path 43 leading from the motor compartment 9 to an air environment 38 that is situated above the oil surface S. The second fluid path 43 is configured and/or arranged in such a way that the rotor 13 can expel oil from the motor compartment. In this process, as the rotor 13 turns, it accelerates the oil adhering to it, which is then expelled via the second fluid path 43.

(18) Preferably, the second fluid path 43 is provided in certain areas of a circumferential wall 47 of the housing 7. The centrifugal force exerted by the rotating rotor 13 accelerates the oil especially in the radial direction and oil that has been picked up in the tangential direction is expelled very efficiently via the second fluid path 43.

(19) Preferably, the second fluid path 43 comprises a discharge opening 45 that is provided in the circumferential wall 47 of the housing 7.

(20) Preferably, more than one second fluid path 43 is provided. It is possible thatas seen in the circumferential directionat least two, preferably more, discharge openings 45 are provided in the circumferential wall 47. In this context, the discharge openings 45 are situated either above the oil surface S, or else they are connected to at least one snorkel that protrudes above the oil surface S, so that the second fluid path 43 leads to the air environment 38 in any case.

(21) Preferably, it is provided that the passage cross section of the one 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. In this case, more oil is expelled per unit of time by the rotor 13 than can be replenished via the first fluid path 35. Consequently, a motor that has filled up while at a standstill empties out quickly when it is started up again, so that splash losses are limited to a brief period of time after the start-up. Here, the passage cross section of the first fluid path 35 only has to be large enough that it can convey into the motor compartment 9 a sufficient quantity of oil to cool the drive unit 3.

(22) Depending on whether air can continue to flow into the motor compartment 9, an oil-oil vapor mixture or an oil-air mixture is present in said motor compartment 9. However, especially transmission oil typically contains a large quantity of air or air bubbles dissolved in the oil, so that in this case, air is released when the oil is being expelled, even if no ambient air is being replenished. Then, too, an oil-air mixture, if applicable at a negative pressure, is present.

(23) Especially when parts of the pump are submerged deep into the oil, preferably at least one third fluid path 49 is provided that leads from the air environment 38 to the motor compartment 9, especially preferably through a snorkel. Additional ambient air can then flow into the motor compartment 9 via this third fluid path when the oil is expelled via the second fluid path 43. For this purpose, the third fluid path is preferably in fluid connection with the air environment 38. Towards this end, as already mentioned, it is possible for the appertaining area of the pump 1 that has the third fluid path 49 not to be submerged in the oil. However, it is likewise possible for the third fluid path 49 to have a snorkel that protrudes above the oil surface S if the pump 1 is completely submerged or when at least parts of the pump are submerged deep into the oil.

(24) Especially preferably, the third fluid path 49 has an opening 51 in the circumferential wall 47. Preferably, additional air can then flow in if the pump with the opening 51 is protruding out of the oil, or if a snorkel that protrudes out of the oil is provided in or at the opening 51.

(25) In the present embodiment, the rotor 13 surrounds the stator 31 as an external rotor. This is particularly advantageous since, in this way, oil adhering to the rotor 13 is accelerated over a large radius and in the direct vicinity of the discharge opening 45, so that it can easily be expelled.

(26) FIG. 1 shows a broken line 53 that runs in the radial direction and that is perpendicular to the circumferential wall 47 and that indicates the intersection area of the sectional views in FIG. 2.

(27) FIG. 2a shows a detailed view of the pump 1, namely, a section from a cross-sectional view, whereby the intersection plane in FIG. 1 is arranged at the height of line 53. Identical and functionally equivalent elements are provided with the same reference numerals, so that reference is hereby made to the preceding embodiments. Particularly the rotor 13 as well as the housing 7 with its circumferential wall 47 are shown.

(28) An embodiment of the discharge opening 45 in the second fluid path 43 is described on the basis of FIG. 2a. In particular, FIG. 2a shows how the discharge opening 45 can be configured in order to allow an efficient discharge of oil from the motor compartment 9 by the rotor 13, preferably at a high discharge speed.

(29) In the embodiment shown, the discharge opening 45 has a special shape: it has a passage surface 55 that is arranged essentially perpendicularhere precisely perpendicularto an imaginary circumferential line in the direction of rotation of the rotor 13. This is indicated in FIG. 2a by the arrow P. The rotation of the rotor 13 is concentric to the longitudinal axis of the drive shaft 15. Therefore, it is possible to construct circumferential lines that run concentrically to the longitudinal axis of the drive shaft 15 and thus, so to speak, represent circumferential lines of the rotational direction of the rotor 13. At its intersection point with at least one such circumferential line, the passage surface 55 runs essentiallyhere preciselyperpendicular thereto. Oil adhering to the rotor 13 is imparted by the rotor with a main velocity component that is oriented essentially tangentially to the rotational direction of the rotor 13 or to a corresponding circumferential line. Owing to the fact that the passage surface 55 is arranged essentially perpendicular to an imaginary circumferential line in the direction of rotation of the rotor 13, the oil can exit from the discharge opening 45 in the direction of its main velocity component without being hindered. In other words, the passage surface 55 is arranged or shaped in such a way that oil can be expelled by the rotor 13 very efficiently.

(30) Especially preferably, the discharge opening 45 is formed by a section 57 of the circumferential wall 47 which is recessed as seen in the radial direction. Together with a section 59 of the circumferential wall 47 whichas seen in the direction opposite from the rotational direction of the rotor 13adjoins the recessed section 57 and itself is not recessed, the discharge opening 45 is easy to create. For instance, it can be stamped into the housing.

(31) It is particularly advantageous for the rotor 13 to have an outer diameter that is only slightly smaller than the inner diameter of the housing 7. In this case, only a relatively small volume of oil is situated between the rotor 13 and the circumferential wall 47, and this oil volume can be accelerated by the rotor 13 virtually in its entirety. Especially preferably, the recessed section 57 is recessed to such an extentas seen in the radial directionthat the passage surface 55 takes up a large portion of the surface area available between the circumferential wall 47 and the rotor 13. In this case, a considerable amount of the oil situated between the rotor 13 and the circumferential wall 47 can be expelled via the passage surface 55. In this context, the closer the recessed section 57as seen in the radial directionis to the rotor 13, the more it can scrape off oil that is in effect adhering to the rotor 13, so that said oil is then expelled.

(32) FIG. 2b shows a schematic detailed view of the cross section of another embodiment of a discharge opening 45. Identical and functionally equivalent elements are provided with the same reference numerals, so that reference is hereby made to the preceding elaborations. The discharge opening 45 here is formed by a section 57 of the circumferential wall 47 which protrudes as seen in the radial direction. Together with a section 57 of the circumferential wall 47 which adjoins the recessed section 57 and itself does not protrude, the discharge opening 45 is easy to create. For instance, it likewise can be stamped into the housing.

(33) As already mentioned, preferably more than one discharge opening 45as seen in the circumferential directionis arranged in the vicinity of the circumferential wall 47. In this context, they are either situated above the oil surface S or they are at least connected to a snorkel that protrudes above the oil surface S.

(34) Altogether, it can be seen that, with the present drive unit and the present pump, considerable less splash loss occurs and thus a considerable better efficiency is achieved due to the second fluid path that allows oil to be expelled from the motor compartment 9 by the rotor 13. This reduces the drive power consumed, so that the drive unit and the pump are quite economical.

LIST OF REFERENCE NUMERALS

(35) 1 pump 3 drive unit 5 pump unit 7 housing 9 motor compartment 11 support 13 rotor 15 drive shaft 17 internal gearwheel 19 external gearwheel 21 closure lid 23 inlet area 25 outlet 27 sliding bearing 29 ball bearing 31 stator 33 stator winding 35 fluid path 37 submerged-oil environment 38 air environment 39 space 41 bypass 43 fluid path 45 discharge opening 47 circumferential wall 49 fluid path 51 opening 53 line 55 passage surface 57 section 59 section 33 stator winding P arrow S oil surface