EP3628866B1 - Lubricant holder for a refrigerant compressor - Google Patents

Lubricant holder for a refrigerant compressor Download PDF

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Publication number
EP3628866B1
EP3628866B1 EP18197570.7A EP18197570A EP3628866B1 EP 3628866 B1 EP3628866 B1 EP 3628866B1 EP 18197570 A EP18197570 A EP 18197570A EP 3628866 B1 EP3628866 B1 EP 3628866B1
Authority
EP
European Patent Office
Prior art keywords
lubricant
inner element
crankshaft
sleeve element
sleeve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP18197570.7A
Other languages
German (de)
French (fr)
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EP3628866A1 (en
Inventor
Andreas Tramposch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Secop GmbH
Original Assignee
Secop GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Secop GmbH filed Critical Secop GmbH
Priority to EP18197570.7A priority Critical patent/EP3628866B1/en
Priority to PCT/EP2019/076159 priority patent/WO2020064998A1/en
Priority to CN201980063273.1A priority patent/CN112752904B/en
Priority to US17/276,532 priority patent/US11225957B2/en
Publication of EP3628866A1 publication Critical patent/EP3628866A1/en
Application granted granted Critical
Publication of EP3628866B1 publication Critical patent/EP3628866B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0261—Hermetic compressors with an auxiliary oil pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F04B39/0253—Hermetic compressors with oil distribution channels in the rotating shaft using centrifugal force for transporting the oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
    • F01M2001/0238—Rotary pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0253—Pressure lubrication using lubricating pumps characterised by the pump driving means
    • F01M2001/0269—Pressure lubrication using lubricating pumps characterised by the pump driving means driven by the crankshaft

Definitions

  • an electric drive unit arranged in the interior of the compressor housing, comprising a rotor and a stator, a crankshaft non-rotatably connected to the rotor, and with a piston-cylinder unit arranged in the interior of the housing, which has a movable in a Cylinder of the piston-cylinder unit comprises pistons mounted, which can be driven by the crankshaft for compressing refrigerant, ensuring adequate lubrication of all moving components is of particular importance.
  • lubricant which collects in a lubricant sump covering a bottom area of the compressor housing is conveyed via the crankshaft in the direction of the cylinder.
  • a sleeve-shaped lubricant receptacle is often provided, which is connected to the crankshaft in a rotationally fixed manner and is arranged coaxially with it and protrudes with an end section into the lubricant sump.
  • Lubricant that has penetrated through an inlet opening from the lubricant sump into a cylindrical receiving section of the lubricant receiver is forced into a paraboloid shape due to the rotation of the lubricant receiver - which is caused by rotation of the crankshaft - with the paraboloid moving along the inner wall of the lubricant receiver and along the Forms the inner wall of the crankshaft—hollow or provided with a bore.
  • Such a lubricant recording is for example from the AT 15828 U1 famous.
  • a maximum rise to which the lubricant located in the receiving section of the lubricant receptacle can be raised in this way is in the range of the clear inner diameter of the crankshaft or the bore and depends on the square of the rotational speed of the lubricant holder and the square of the clear inner radius of the crankshaft or the lubricant holder.
  • the lubricant can then escape from the crankshaft to points to be lubricated via at least one outlet bore.
  • compressors with variable speeds are increasingly being used - in contrast to conventional compressors with a fixed speed, which only have two states, namely zero speed and a working speed of typically 3000 rpm .
  • very low speeds are regularly achieved in practice - typically a minimum of 800 rpm. Since, as explained above, the height of rise depends squarely on the rotational speed or the speed, low speeds pose a major problem for reliable lubrication.
  • the cylindrical receiving section is open at the bottom and the likewise cylindrical inner element is arranged in the receiving section, so that a Gap between a lateral surface of the inner element and the inner wall of the receiving portion results.
  • the inner element is essentially fixed in position, typically by being connected to the stator.
  • the inner element typically has a spiral-shaped groove running from bottom to top on its outer surface, which promotes the delivery of the lubricant.
  • the inner element must have a sufficiently large radius so that the rotational speed or tangential speed and thus the achievable centrifugal force acting on the lubricant in the area of the outer surface is large enough to achieve good pumping capacity even at low speeds.
  • the width of the gap between the inner member and the inner wall of the female portion is critical. In principle, a smaller gap would tend to result in better conveying capacity. Due to the viscosity of the lubricant, however, the gap cannot be made too small, otherwise friction losses would reduce efficiency. This means that the selection of the gap width must be made from these points of view as the best possible compromise. In practice, however, it has been found that depending on the exact operating parameters of the refrigerant compressor and the thermal expansion of the lubricant on the one hand and the lubricant holder including the inner element on the other hand, the gap width (like the viscosity of the lubricant) is not stable but changes. It comes in sequence too undesired strong fluctuations in the flow rate, which, especially at low speeds, carries the risk of too low a flow rate and the associated consequential damage.
  • an oil pump for a refrigeration compressor comprising a sleeve having an inner surface, an upper portion fixed to a crankshaft and a rotor, whereby the sleeve is rotationally driven, and a lower portion, the lower end of which is immersed in lubricating oil.
  • the oil pump further includes an elongate pump body disposed within the inner surface of the sleeve, the sleeve and pump body each having a conical profile and tapering from bottom to top.
  • the inner surface of the sleeve has a helical groove. The relative movement between the sleeve and the pump body causes oil to flow upwards.
  • the inner element can, for example, be connected to the crankshaft in a rotationally fixed manner and the sleeve element can be rotationally fixed—apart from a negligible, minor angle of rotation.
  • the crankshaft rotates and, accordingly, the inner element rotates, whereas the sleeve element does not rotate.
  • the sleeve element can be connected to the crankshaft in a rotationally fixed manner and the inner element can be rotationally fixed except for a negligible, minor angle of rotation.
  • a non-rotatable connection between the inner element or sleeve element and the crankshaft can in principle be direct or indirect, ie with the interposition of at least one other element such as a seal, a fastener, etc., take place.
  • the sleeve element can be connected to the crankshaft, in particular in the region of its upper end. It would be conceivable, for example, for the sleeve element to be slid onto the crankshaft with its clear cross-section in the region of the upper end and to be held thereon, for example by means of a press fit. For this purpose, it can be provided that the clear cross section in the region of the upper end compared to the im Recording segment existing taper extended again to accommodate the crankshaft.
  • the sleeve element is itself a part or section of a larger element.
  • the clear section extends over this part or section, i.e. over the sleeve element.
  • the sleeve element and the inner element are designed in such a way that in the operating state the inner element is arranged with its lateral surface at least in sections within the clear cross section of the sleeve element. I.e. the inner element is at least partially accommodated in the receiving segment.
  • the sleeve element and the inner element are designed in such a way that in the operating state viewed in the direction from the lower end to the upper end of the sleeve element, the lower end of the lateral surface is arranged in front of the upper end thereof.
  • the receiving segment of the clear cross section and the inner element, in particular its lateral surface are oriented at least approximately the same.
  • the result when used in an operating refrigerant compressor, the result is that the lower ends of the sleeve element and the shell surface are arranged in the vertical direction below the upper ends of the sleeve element and the shell surface.
  • the cross section of the inner element or the geometry of the inner element with its outer surface is preferably adapted to the clear cross section or at least to the receiving segment.
  • the clear cross section or the receiving segment it would be conceivable for the clear cross section or the receiving segment to have a certain sequence of, preferably fine, steps for the purpose of narrowing, and for the lateral surface to have a corresponding sequence of steps.
  • the sleeve element and the inner element are designed such that in the operating state the inner element and the sleeve element can be rotated relative to one another about the longitudinal axis of the sleeve element and/or the longitudinal axis of the inner element.
  • the at least partial arrangement of the inner element in the receiving segment is such that a gap with a certain gap width is created between the lateral surface and the inner wall, which delimits the clear cross section and thus in particular the receiving segment.
  • lubricant from a lubricant sump of the refrigerant compressor can enter this gap if the inner element and the sleeve element protrude at least in sections into the lubricant sump.
  • the sleeve element projects into the lubricant sump, in particular in the area of its lower end, and the inner element in particular in the area of the lower end of its lateral surface.
  • the lubricant can in particular be an oil that is customary when used in refrigerant compressors.
  • the rotation of the crankshaft causes the sleeve element and the inner element to rotate relative to one another, in particular when the sleeve element is connected in a rotationally fixed manner to the crankshaft.
  • the inner element preferably does not rotate relative to the stator, or only rotates through a limited angular range, whereas the sleeve element rotates completely.
  • a reverse design is also possible, in which the inner element rotates completely and the sleeve element does not rotate relative to the stator, or only rotates through a limited angular range.
  • the tapering of the inner element or the receiving segment can ensure that in the region of the upper end of the lateral surface there is a substantially continuous transition, ie a transition without an abrupt drop in pressure, for the lubricant from the gap into a bore of the crankshaft. Accordingly, an adverse reduction in the flow of the lubricant can be avoided.
  • the inner wall and/or the lateral surface has at least one groove running in a spiral shape. I.e. the inner wall and/or the lateral surface can also have several grooves.
  • the at least one groove provides an additional delivery volume for the lubricant that is independent of the gap width. Due to the centrifugal forces acting on the lubricant, the lubricant is forced into and through the at least one groove.
  • the lateral surface preferably has the at least one spiral-shaped groove which runs in the direction from the lower end to the upper end of the lateral surface.
  • the at least one groove can extend from the lower end to the upper end of the lateral surface. You can theoretically, for example, start only in the area of the lower end and/or stop in the area of the upper end, so that a certain overhang of the lateral surface over the groove in the area of the lower and/or upper end is given.
  • Seen in the direction of the longitudinal axis of the inner element the at least one groove runs spirally around this longitudinal axis, it being possible for the groove to theoretically also end on the longitudinal axis.
  • the course of the groove is of course also given in the opposite direction, ie from the upper end to the lower end of the lateral surface.
  • the invention provides that the at least one groove has a varying pitch angle, which preferably increases from the lower end to the upper end of the lateral surface.
  • the clear cross section of the sleeve element is designed in the shape of a truncated cone, at least in its receptacle segment.
  • this proves to be favorable in terms of production technology.
  • this also has a favorable effect on the flow behavior of the lubricant or oil, since there is a correspondingly smooth inner wall at least in the receiving segment.
  • the inner wall has the at least one groove, what is said above naturally means that the clear cross-section of the sleeve element is designed in the shape of a truncated cone, at least in its receiving segment, apart from the at least one groove.
  • the lateral surface of the inner element is designed as the lateral surface of a truncated cone.
  • this again proves to be favorable in terms of manufacturing technology.
  • this also has a favorable effect on the flow behavior of the lubricant or oil, since there is a smooth lateral surface.
  • the lateral surface has the at least one groove, what is said above naturally means that the lateral surface, apart from the at least one groove, is designed as the lateral surface of a truncated cone.
  • the truncated cone shape of the receptacle segment of the clear cross section is based on a cone with a first opening angle
  • that the truncated cone shape according to which the lateral surface is formed is based on a cone with a second opening angle
  • the absolute difference between the first opening angle and the second opening angle is less than or equal to 10°, preferably less than or equal to 5°, particularly preferably equal to 0°.
  • the absolute difference is to be understood as the absolute value of the difference between the two opening angles.
  • the inner element has at least one protruding wing and/or a fastening element, preferably an eyelet, for a fixing means in the region of the lower end of the lateral surface.
  • a protruding wing and/or a fastening element preferably an eyelet
  • This configuration serves to ensure that the inner element does not rotate or only rotates by a certain angular amount when the crankshaft rotates, whereas the sleeve element rotates with the crankshaft.
  • the wing which dips into the lubricant sump, is sufficient due to the viscosity of the lubricant, ie the lubricant causes a sufficiently large resistance to rotation of the inner element.
  • the area of the wing can be made correspondingly larger.
  • the at least one wing does not protrude from the lateral surface, but from a kind of base surface of the Inner member that is substantially normal to the longitudinal axis of the inner member.
  • the at least one wing extends at least in sections parallel—and normal—to the longitudinal axis and points away from the upper end of the lateral surface.
  • a fixing means for example in the form of a bracket or a bracket, can be provided, which is fastened to the fastening element on the one hand and is supported on an essentially immovable element, e.g. on the stator, on the other hand or is rigidly connected to it.
  • the fixing means can also serve to mount the inner element in a fixed or movable manner in relation to the longitudinal axis, ie with a directional component parallel to the longitudinal axis, of the sleeve element.
  • the buoyancy experienced by the inner element when immersed in the lubricant sump can be used for the purpose of such a bearing.
  • the inner element can be designed in such a way that it floats on the lubricant (ie does not sink completely), which represents a particularly cost-effective mounting of the inner element.
  • the inner element is made of a material, preferably a plastic, whose density is lower than the density of the lubricant. It would also be conceivable to manufacture the inner element from a light metal or a light metal alloy, in particular an aluminum alloy, to achieve the desired density.
  • a refrigerant compressor with a hermetically encapsulated compressor housing, an electric drive unit arranged in the interior of the compressor housing, comprising a rotor and a stator, a crankshaft non-rotatably connected to the rotor, and a piston-cylinder arranged in the interior of the housing -Unit, which comprises a piston which is movably mounted in a cylinder of the piston-cylinder unit and which can be driven by the crankshaft to compress refrigerant, according to the invention that the refrigerant compressor has a lubricant receptacle according to the invention which is in the operating state, in order to collect lubricant from one in one To promote bottom area of the compressor housing trained lubricant sump over the crankshaft.
  • the inner member or the sleeve member can be non-rotatably connected to the crankshaft. Accordingly, in a preferred embodiment of the refrigerant compressor according to the invention, it is provided that the sleeve element of the lubricant receptacle is connected to the crankshaft in a rotationally fixed manner.
  • the crankshaft has a bore, preferably at least partially oblique to an axis of rotation of the crankshaft, which is in fluid communication with the clear cross section of the sleeve element, with the inner element protruding into the bore.
  • This arrangement is possible due to the narrowing of the inner element and ensures a particularly good transition for the lubricant from the gap into the bore of the crankshaft.
  • the lubricant can then escape from the crankshaft—more precisely, from the bore of the crankshaft—to points to be lubricated via at least one outlet bore.
  • the inner element is movable in relation to the longitudinal axis of the sleeve element.
  • the gap width is changed by a corresponding movement of the inner element parallel to the longitudinal axis of the sleeve element. Accordingly, the gap width can be adjusted to operating parameters such as the temperature and/or the viscosity of the lubricant and/or the speed in order to enable an optimal flow of the lubricant. For example, with a lubricant that is becoming thinner, the gap width can be reduced in order to bring about increased delivery.
  • a preferred embodiment of the refrigerant compressor according to the invention provides that a fixing means designed as a spring element, preferably in the form of a resilient wire clip, is provided, with which the inner element is essentially non-rotatably connected to the stator or other components of the refrigerant compressor.
  • a fixing means designed as a spring element preferably in the form of a resilient wire clip, is provided, with which the inner element is essentially non-rotatably connected to the stator or other components of the refrigerant compressor.
  • connection to the stator or other - essentially immobile - components of the refrigerant compressor can be direct or indirect, i.e. with the interposition of other elements.
  • the spring element ensures a certain mobility of the inner element parallel to the longitudinal axis of the sleeve element.
  • the spring element causes that the inner member is pushed towards the receiving segment to some degree, which tends to reduce the gap width. This is counteracted by a certain pressure of the lubricant in the gap, which pressure depends on various factors. For example, the inner element is pressed away from the inner wall of the receiving segment against the spring force of the spring element, the stronger the thicker the lubricant is or the higher the speed, and the larger the gap width remains the inner element is pressed less strongly away from the inner wall of the receiving segment by the lubricant flowing in the gap against the spring force of the spring element, and the gap width decreases accordingly.
  • the adjustment can also take place—at least roughly—using the above-described utilization of the buoyancy of the inner element in the lubricant, in which case the fixing means can also be dispensed with entirely if the at least one wing is present.
  • the inner element Due to the buoyancy, the inner element is basically pressed in the direction of the receiving segment, which tends to lead to a reduction in the gap width—similar to the embodiment with the spring element described above. This is counteracted by the pressure of the lubricant in the gap, which pressure depends on various factors. For example, the more viscous the lubricant or the higher the speed, the greater the gap width. If the lubricant becomes thinner or the speed decreases, the gap width decreases accordingly.
  • FIG. 1 shows an axonometric view of an inner element 9 of a lubricant receptacle 1 according to the invention.
  • the latter is in an operating state and is attached to a crankshaft 2 of a refrigerant compressor 3 according to the invention in 2 shown in a sectional view.
  • the lubricant holder 1 is used for the vertical promotion of lubricant, in particular oil 15, from one in one Lubricant sump 26 formed in the bottom area 25 of a compressor housing 18 of the refrigerant compressor 3, see the sectional view of FIG 3 , via the crankshaft 2.
  • the crankshaft 2 has a 2 easily recognizable bore 27, from which the oil 15 can escape via outlet bores 28 to points to be lubricated.
  • the bore 27 can be designed to run obliquely to an axis of rotation 29 of the crankshaft 2, as shown in FIG 2 shown.
  • An electric drive unit 19 with a rotor 20 and a stator 21 is also arranged in the compressor housing 18 , the crankshaft 2 being connected to the rotor 20 in a rotationally fixed manner. Also located in the compressor housing 18 is a piston-cylinder unit 22 which includes a piston 23 which is movably mounted in a cylinder 24 of the piston-cylinder unit 22 and can be driven by the crankshaft 2 to compress refrigerant.
  • the lubricant holder 1 comprises a sleeve element 4 with a clear cross section 5 delimited by an inner wall 34 which extends along a longitudinal axis 6 of the sleeve element 4 from an upper end 7 to a lower end 8 of the sleeve element 4 .
  • the clear cross section 5 at the upper end 7 can serve to accommodate the crankshaft 2 in order to produce a non-rotatable connection between the sleeve element 4 and thus the lubricant receptacle 1 and the crankshaft 2, for example by means of a press fit.
  • lubricant receptacles 1 according to the invention are also possible in which the lubricant receptacle 1 is non-rotatably connected to the crankshaft 2 via a non-rotatably connected connection between the inner element 9 and the crankshaft 2 .
  • the lubricant receptacle 1 comprises the inner element 9, which has an outer surface 10 which extends along a longitudinal axis 11 of the inner element 9 from a lower end 12 to an upper end 13 and has a groove 14 in the exemplary embodiment shown.
  • This groove 14 runs spirally in the direction from the lower end 12 to the upper end 13 and extends from the lower end 12 to the upper end 13 of the lateral surface 10.
  • the inner wall 34 has no groove in the illustrated embodiment, although this is possible in principle.
  • the inner element 9 is arranged with its lateral surface 10 at least in sections - essentially completely in the exemplary embodiment shown - within the clear cross section 5 of the sleeve element 4, more precisely in a receiving segment 33 of the clear cross section 5 provided for receiving.
  • the lower end 12 of the lateral surface 10 is arranged in front of its upper end 13, ie the sleeve element 4 and the inner element 9 are to a certain extent oriented or aligned in the same way.
  • the sleeve element 4 and the inner element 9 are also designed such that the inner element 9 and the sleeve element 4 can be rotated relative to one another about the longitudinal axis 6 of the sleeve element 4 and/or the longitudinal axis 11 of the inner element 9 .
  • this rotation is mediated or generated by the non-rotatable connection of the lubricant receptacle 1 to the crankshaft 2 .
  • only the relative rotation between the sleeve element 4 and the inner element 9 is important, ie it would be conceivable for the inner element 9 to be driven in rotation and for the sleeve element 4 to be essentially fixed in terms of rotation.
  • the sleeve element 4 is driven in rotation when the crankshaft 2 rotates, but the inner element 9 does not.
  • the inner element 9 can be connected to the stator 21 by means of a fixing means, for example.
  • the inner element 9 can be used, as in 1 shown, have a fastening element in the form of an eyelet 16 with which the fixing means can be brought into engagement.
  • the Oil 15 upon rotation of the sleeve member 4 a corresponding centrifugal force. This presses the oil 15 in the gap 30 and in particular in the at least one groove 14 in the direction from the lower end 12 to the upper end 13 of the lateral surface 10 and thus in the direction of the crankshaft 2.
  • the oil 15 can flow particularly well in the direction of the crankshaft 4 via the groove 14 - regardless of the exact gap width 31.
  • the bore 27 of the crankshaft 2 with the clear cross section 5 and thus in particular also with the groove 14 is in more fluid Connection so that the oil 15 can get into the bore 27.
  • the clear cross section 5 tapers at least in the receiving segment 33 in the direction from the lower end 8 to the upper end 7 .
  • the inner element 9 tapers in the area of the lateral surface 10 in the direction from the lower end 12 to the upper end 13 of the lateral surface 10 . Due to the narrowing of the inner element 9 or the receiving segment 33, this can have a large diameter in the area of the lower end 12 of the lateral surface 10, whereby sufficiently large tangential speeds or centrifugal forces (in the gap 30) can be realized even at low speeds in order to ensure reliable delivery of the oil 15 to ensure.
  • the tapering of the inner element 9 or the receiving segment 33 can ensure that in the area of the upper end 13 of the lateral surface 10 there is a substantially continuous transition, i.e. a transition without an abrupt pressure drop, for the oil 15 from the gap 30 into the bore 27 the crankshaft 2 takes place.
  • this continuous transition is further improved in that the inner element 9 is designed with its taper in such a way that the inner element 9 protrudes into the bore 27, cf. 2 . Accordingly, a disadvantageous reduction in the flow of lubricant can be avoided almost completely.
  • the shape of the narrowing of the clear cross-section 5 in the receiving segment 33 on the one hand and the shape of the narrowing of the inner element 9 in the area of the lateral surface 10 on the other hand are matched to one another in the exemplary embodiment shown in order to enable an optimal arrangement of the inner element 9 in the sleeve element 4 in the operating state.
  • the clear cross section 5 of the sleeve element 4 is frustoconical, at least in its receiving segment 33 formed, this truncated cone shape being based on a cone with a first opening angle ⁇ 1.
  • the lateral surface 10 of the inner element 9 apart from the at least one groove 14 is designed as the lateral surface of a truncated cone, this truncated cone shape being based on a cone with a second opening angle ⁇ 2.
  • the above-mentioned matching is further optimized in that the absolute amount of the difference between the first opening angle ⁇ 1 and the second opening angle ⁇ 2 is less than or equal to 10°, preferably less than or equal to 5°, particularly preferably equal to 0°.
  • the inner element 9 is movably mounted in relation to the longitudinal axis 6 of the sleeve element 4, i.e. with a directional portion parallel to the longitudinal axis 6.
  • the gap width 31 can be adjusted in principle, in particular to adapt to operating parameters such as the temperature and/or the viscosity of the oil 15 and/or the speed, in order to achieve an optimal lubricant flow to allow.
  • the gap width 31 could be reduced in order to bring about increased delivery.
  • the possibility of adjustment is particularly precise in the exemplary embodiment shown due to the above-mentioned truncated cone shapes.
  • the fixing means is designed as a spring element in the form of a resilient wire clip 32, with which the inner element 9 is essentially non-rotatably connected to the stator 21. Slight twisting angles of the inner element 9, which due to the elasticity of the springy wire clip 32 may arise can be tolerated.
  • the resilient wire clip 32 causes the inner element 9 to be pressed to a certain extent in the direction of the receiving segment 33 , which tends to lead to a reduction in the gap width 31 . This is counteracted by a certain pressure of the oil 15 in the gap 30, which pressure depends on various factors.
  • the inner element 9 is pushed away from the inner wall 34 of the receiving segment 33 against the spring force of the resilient wire bracket 32, the stronger the more viscous the oil 15 is or the higher the speed, and the larger the gap width 31 remains. If the oil 15 becomes thinner or if the speed drops, the inner element 9 is pressed away less strongly from the inner wall of the receiving segment 33 against the spring force of the resilient wire clip 32 by the oil 15 flowing in the gap 30, and the gap width 31 is reduced accordingly.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Description

Die vorliegende Erfindung betrifft eine Schmiermittelaufnahme zur vertikalen Förderung von Schmiermittel mittels einer Kurbelwelle eines Kältemittelkompressors gemäß Anspruch 1, umfassend ein Hülsenelement mit einem von einer Innenwand begrenzten lichten Querschnitt, der sich entlang einer Längsachse des Hülsenelements von einem oberen Ende bis zu einem unteren Ende des Hülsenelements erstreckt, die Schmiermittelaufnahme weiters umfassend ein Innenelement, das eine Mantelfläche aufweist, die sich entlang einer Längsachse des Innenelements von einem unteren Ende bis zu einem oberen Ende erstreckt, wobei in einem Betriebszustand der Schmiermittelaufnahme

  • das Innenelement mit seiner Mantelfläche zumindest abschnittsweise innerhalb des lichten Querschnitts des Hülsenelements angeordnet ist,
  • in Richtung vom unteren Ende zum oberen Ende des Hülsenelements gesehen das untere Ende der Mantelfläche vor dessen oberen Ende angeordnet ist und
  • das Innenelement und das Hülsenelement relativ zueinander um die Längsachse des Hülsenelements und/oder die Längsachse des Innenelements verdrehbar sind, wobei sich der lichte Querschnitt vom unteren Ende zum oberen Ende des Hülsenelements hin zumindest in einem zur Aufnahme des Innenelements vorgesehenen Aufnahmesegment verjüngt und wobei sich das Innenelement im Bereich der Mantelfläche vom unteren Ende zum oberen Ende der Mantelfläche hin verjüngt und wobei die Innenwand und/oder die Mantelfläche mindestens eine spiralförmig verlaufende Rille aufweist.
The present invention relates to a lubricant receptacle for the vertical conveyance of lubricant by means of a crankshaft of a refrigerant compressor according to claim 1, comprising a sleeve element with a clear cross section delimited by an inner wall, which extends along a longitudinal axis of the sleeve element from an upper end to a lower end of the sleeve element extends, the lubricant receptacle further comprising an inner element having an outer surface that extends along a longitudinal axis of the inner element from a lower end to an upper end, wherein in an operating state of the lubricant receptacle
  • the inner element is arranged with its lateral surface at least in sections within the clear cross section of the sleeve element,
  • viewed in the direction from the lower end to the upper end of the sleeve element, the lower end of the lateral surface is arranged in front of the upper end thereof and
  • the inner element and the sleeve element can be rotated relative to one another about the longitudinal axis of the sleeve element and/or the longitudinal axis of the inner element, with the clear cross-section tapering from the lower end to the upper end of the sleeve element at least in a receiving segment provided for receiving the inner element and with the Inner element in the area of the lateral surface tapers from the lower end to the upper end of the lateral surface and wherein the inner wall and/or the lateral surface has at least one spirally running groove.

STAND DER TECHNIKSTATE OF THE ART

Bei Kältemittelkompressoren mit einem hermetisch kapselbaren Kompressorgehäuse, einer in einem Gehäuseinneren des Kompressorgehäuses angeordneten elektrischen Antriebseinheit, umfassend einen Rotor und einen Stator, einer mit dem Rotor drehfest verbundenen Kurbelwelle sowie mit einer in dem Gehäuseinneren angeordneten Kolben-Zylinder-Einheit, welche einen beweglich in einem Zylinder der Kolben-Zylinder-Einheit gelagerten Kolben umfasst, welcher zur Verdichtung von Kältemittel von der Kurbelwelle antreibbar ist, ist die Sicherstellung einer ausreichenden Schmierung sämtlicher beweglicher Bauteile von besonderer Bedeutung. Zu diesem Zweck kann es vorgesehen sein, dass Schmiermittel, welches sich in einem einen Bodenbereich des Kompressorgehäuses bedeckenden Schmiermittelsumpf sammelt, über die Kurbelwelle in Richtung des Zylinders gefördert wird.In refrigerant compressors with a hermetically encapsulated compressor housing, an electric drive unit arranged in the interior of the compressor housing, comprising a rotor and a stator, a crankshaft non-rotatably connected to the rotor, and with a piston-cylinder unit arranged in the interior of the housing, which has a movable in a Cylinder of the piston-cylinder unit comprises pistons mounted, which can be driven by the crankshaft for compressing refrigerant, ensuring adequate lubrication of all moving components is of particular importance. For this purpose it can be provided that lubricant which collects in a lubricant sump covering a bottom area of the compressor housing is conveyed via the crankshaft in the direction of the cylinder.

Dazu ist oftmals eine hülsenförmige Schmiermittelaufnahme vorgesehen, welche drehfest mit der Kurbelwelle verbunden und koaxial mit dieser angeordnet ist und mit einem Endabschnitt in den Schmiermittelsumpf hinein ragt. Schmiermittel, welches durch eine Eintrittsöffnung aus dem Schmiermittelsumpf in einen zylindrischen Aufnahmeabschnitt der Schmiermittelaufnahme eingedrungen ist, wird aufgrund der Rotation der Schmiermittelaufnahme - welche durch Rotation der Kurbelwelle hervorgerufen wird - in eine Paraboloidform gezwungen, wobei sich das Paraboloid entlang der Innenwand der Schmiermittelaufnahme und entlang der Innenwand der - hohl ausgeführten oder mit einer Bohrung versehenen - Kurbelwelle ausbildet. Eine solche Schmiermittelaufnahme ist z.B. aus der AT 15828 U1 bekannt.For this purpose, a sleeve-shaped lubricant receptacle is often provided, which is connected to the crankshaft in a rotationally fixed manner and is arranged coaxially with it and protrudes with an end section into the lubricant sump. Lubricant that has penetrated through an inlet opening from the lubricant sump into a cylindrical receiving section of the lubricant receiver is forced into a paraboloid shape due to the rotation of the lubricant receiver - which is caused by rotation of the crankshaft - with the paraboloid moving along the inner wall of the lubricant receiver and along the Forms the inner wall of the crankshaft—hollow or provided with a bore. Such a lubricant recording is for example from the AT 15828 U1 famous.

Eine maximale Steighöhe, auf die das sich im Aufnahmeabschnitt der Schmiermittelaufnahme befindende Schmiermittel auf diese Weise angehoben werden kann, wird im Bereich des lichten Innendurchmessers der Kurbelwelle bzw. der Bohrung erreicht und hängt vom Quadrat der Rotationsgeschwindigkeit der Schmiermittelaufnahme sowie vom Quadrat des lichten Innenradius der Kurbelwelle bzw. der Schmiermittelaufnahme ab. Über mindestens eine Austrittsbohrung kann das Schmiermittel sodann aus der Kurbelwelle zu zu schmierenden Stellen austreten.A maximum rise to which the lubricant located in the receiving section of the lubricant receptacle can be raised in this way is in the range of the clear inner diameter of the crankshaft or the bore and depends on the square of the rotational speed of the lubricant holder and the square of the clear inner radius of the crankshaft or the lubricant holder. The lubricant can then escape from the crankshaft to points to be lubricated via at least one outlet bore.

Bei entsprechender Wahl der Fertigungsparameter (beispielsweise lichter Innenradius der Kurbelwelle, Höhe der Austrittsbohrungen) und Prozessparameter (beispielsweise Rotationsgeschwindigkeit der Kurbelwelle, Viskosität des Schmiermittels) ist es somit möglich, das Schmiermittel vom Boden des Kompressorgehäuses mittels der Schmiermittelaufnahme über die Kurbelwelle des Kompressors zu den Auflagestellen des Hauptlagers der Kurbelwelle, dem Kurbelzapfen und der Pleuelstange des Kältemittelkompressors zu fördern.With an appropriate selection of the production parameters (e.g. inside radius of the crankshaft, height of the outlet bores) and process parameters (e.g. rotational speed of the crankshaft, viscosity of the lubricant), it is thus possible to transport the lubricant from the bottom of the compressor housing via the compressor crankshaft to the bearing points by means of the lubricant intake of the main bearing of the crankshaft, the crank pin and the connecting rod of the refrigerant compressor.

In der Praxis kommen heutzutage vermehrt Kompressoren mit variabler Drehzahl zum Einsatz - im Gegensatz zu konventionellen Kompressoren mit fixer Drehzahl, die lediglich zwei Zustände, nämlich Drehzahl null und eine Arbeitsdrehzahl von typischerweise 3000 min-1, aufweisen. Bei Kompressoren mit variabler Drehzahl werden in Abhängigkeit einer geforderten Kühlleistung in der Praxis regelmäßig sehr niedrige Drehzahlen - minimal typischerweise 800 min-1 - erzielt. Da, wie oben ausgeführt, die Steighöhe quadratisch von der Rotationsgeschwindigkeit bzw. von der Drehzahl abhängt, stellen geringe Drehzahlen ein großes Problem für eine zuverlässige Schmierung dar.In practice, compressors with variable speeds are increasingly being used - in contrast to conventional compressors with a fixed speed, which only have two states, namely zero speed and a working speed of typically 3000 rpm . In the case of compressors with variable speeds, depending on the required cooling capacity, very low speeds are regularly achieved in practice - typically a minimum of 800 rpm. Since, as explained above, the height of rise depends squarely on the rotational speed or the speed, low speeds pose a major problem for reliable lubrication.

Versuche, die Förderleistung mittels eines Innenelements zu verbessern, haben sich bislang als nicht zufriedenstellend erwiesen. Hierbei ist der zylindrische Aufnahmeabschnitt unten offen ausgeführt und das ebenfalls zylindrisch ausgeführte Innenelement im Aufnahmeabschnitt angeordnet, sodass sich ein Spalt zwischen einer Mantelfläche des Innenelements und der Innenwand des Aufnahmeabschnitts ergibt. Das Innenelement ist dabei im Wesentlichen lagefixiert, typischerweise durch Anbindung an den Stator. Das Innenelement weist typischerweise eine von unten nach oben laufende, spiralförmige Rille an seiner Mantelfläche auf, die die Förderung des Schmiermittels begünstigt. Das Innenelement muss einen hinreichend großen Radius haben, damit die Drehgeschwindigkeit bzw. Tangentialgeschwindigkeit und damit die erzielbare, auf das Schmiermittel wirkende Zentrifugalkraft im Bereich der Mantelfläche groß genug ist, um auch bei niedrigen Drehzahlen eine gute Förderleistung zu erzielen. Andererseits haben derart große Radien einen abrupten strukturellen Übergang und damit einen hohen abrupten Druckabfall zwischen dem Innenelement und der Bohrung in der Kurbelwelle zur Folge, was den Schmiermittelfluss nachteilig reduziert. Geringere Durchmesser des Innenelements vermindern zwar den Druckabfall, erzeugen aber bei niedrigen Drehzahlen keine hinreichend großen Zentrifugalkräfte.Attempts to improve pumping performance by means of an inner element have so far proved unsatisfactory. In this case, the cylindrical receiving section is open at the bottom and the likewise cylindrical inner element is arranged in the receiving section, so that a Gap between a lateral surface of the inner element and the inner wall of the receiving portion results. The inner element is essentially fixed in position, typically by being connected to the stator. The inner element typically has a spiral-shaped groove running from bottom to top on its outer surface, which promotes the delivery of the lubricant. The inner element must have a sufficiently large radius so that the rotational speed or tangential speed and thus the achievable centrifugal force acting on the lubricant in the area of the outer surface is large enough to achieve good pumping capacity even at low speeds. On the other hand, such large radii result in an abrupt structural transition and hence a high abrupt pressure drop between the inner member and the bore in the crankshaft, which disadvantageously reduces lubricant flow. Although smaller diameters of the inner element reduce the pressure drop, they do not generate sufficiently large centrifugal forces at low speeds.

Ein weiterer Nachteil bekannter Lösungsversuche mit Innenelementen ist, dass die Breite des Spalts zwischen dem Innenelement und der Innenwand des Aufnahmeabschnitts kritisch ist. Grundsätzlich würde ein kleinerer Spalt tendenziell eine bessere Förderleistung ergeben. Aufgrund der Viskosität des Schmiermittels kann der Spalt aber nicht zu klein gemacht werden, da sonst Reibungsverluste den Wirkungsgrad verringern würden. D.h. die Wahl der Spaltbreite muss unter diesen Gesichtspunkten als möglichst guter Kompromiss erfolgen. In der Praxis zeigt es sich jedoch, dass in Abhängigkeit der genauen Betriebsparameter des Kältemittelkompressors sowie der thermischen Ausdehnung des Schmiermittels einerseits und der Schmiermittelaufnahme samt Innenelement andererseits die Spaltbreite (ebenso wie die Viskosität des Schmiermittels) nicht stabil ist, sondern sich ändert. Es kommt in Folge zu unerwünschten starken Schwankungen der Förderleistung, was insbesondere bei niedrigen Drehzahlen die Gefahr einer zu geringen Förderleistung und damit einhergehenden Folgeschäden birgt.Another disadvantage of known inner member approaches is that the width of the gap between the inner member and the inner wall of the female portion is critical. In principle, a smaller gap would tend to result in better conveying capacity. Due to the viscosity of the lubricant, however, the gap cannot be made too small, otherwise friction losses would reduce efficiency. This means that the selection of the gap width must be made from these points of view as the best possible compromise. In practice, however, it has been found that depending on the exact operating parameters of the refrigerant compressor and the thermal expansion of the lubricant on the one hand and the lubricant holder including the inner element on the other hand, the gap width (like the viscosity of the lubricant) is not stable but changes. It comes in sequence too undesired strong fluctuations in the flow rate, which, especially at low speeds, carries the risk of too low a flow rate and the associated consequential damage.

Aus der US 2010/074771 A1 ist eine Ölpumpe für einen Kühlkompressor bekannt, umfassend eine eine Innenfläche aufweisende Hülse mit einem oberen Abschnitt, der an einer Kurbelwelle und an einem Rotor befestigt ist, wodurch die Hülse drehend angetrieben wird, und einem unteren Abschnitt, dessen unteres Ende in Schmieröl eintaucht. Ferner umfasst die Ölpumpe einen länglichen Pumpenkörper, der innerhalb der Innenfläche der Hülse angeordnet ist, wobei die Hülse und der Pumpenkörper jeweils ein konisches Profil aufweisen und sich von unten nach oben verjüngen. Die Innenfläche der Hülse weist eine schraubenförmige Nut auf. Die Relativbewegung zwischen der Hülse und dem Pumpenkörper lässt Öl nach oben strömen.From the U.S. 2010/074771 A1 discloses an oil pump for a refrigeration compressor, comprising a sleeve having an inner surface, an upper portion fixed to a crankshaft and a rotor, whereby the sleeve is rotationally driven, and a lower portion, the lower end of which is immersed in lubricating oil. The oil pump further includes an elongate pump body disposed within the inner surface of the sleeve, the sleeve and pump body each having a conical profile and tapering from bottom to top. The inner surface of the sleeve has a helical groove. The relative movement between the sleeve and the pump body causes oil to flow upwards.

AUFGABE DER ERFINDUNGOBJECT OF THE INVENTION

Es ist daher Aufgabe der vorliegenden Erfindung, eine Schmiermittelaufnahme zur Verfügung zu stellen, die die oben geschilderten Nachteile vermeidet und eine zuverlässige Schmierung auch bei niedrigen Drehzahlen, wie sie insbesondere bei Kompressoren mit variabler Drehzahl in der Praxis regelmäßig vorkommen, gewährleistet.It is therefore the object of the present invention to provide a lubricant receptacle which avoids the disadvantages described above and ensures reliable lubrication even at low speeds, as is regularly the case in practice, particularly in compressors with variable speeds.

DARSTELLUNG DER ERFINDUNGPRESENTATION OF THE INVENTION

Zur Lösung der oben genannten Aufgabe ist es bei einer Schmiermittelaufnahme zur vertikalen Förderung von Schmiermittel mittels einer Kurbelwelle eines Kältemittelkompressors, umfassend ein Hülsenelement mit einem von einer Innenwand begrenzten lichten Querschnitt, der sich entlang einer Längsachse des Hülsenelements von einem oberen Ende bis zu einem unteren Ende des Hülsenelements erstreckt, die Schmiermittelaufnahme weiters umfassend ein Innenelement, das eine Mantelfläche aufweist, die sich entlang einer Längsachse des Innenelements von einem unteren Ende bis zu einem oberen Ende erstreckt, wobei in einem Betriebszustand der Schmiermittelaufnahme

  • das Innenelement mit seiner Mantelfläche zumindest abschnittsweise innerhalb des lichten Querschnitts des Hülsenelements angeordnet ist,
  • in Richtung vom unteren Ende zum oberen Ende des Hülsenelements gesehen das untere Ende der Mantelfläche vor dessen oberen Ende angeordnet ist und
  • das Innenelement und das Hülsenelement relativ zueinander um die Längsachse des Hülsenelements und/oder die Längsachse des Innenelements verdrehbar sind, vorgesehen, dass sich der lichte Querschnitt vom unteren Ende zum oberen Ende des Hülsenelements hin zumindest in einem zur Aufnahme des Innenelements vorgesehenen Aufnahmesegment verjüngt und dass sich das Innenelement im Bereich der Mantelfläche vom unteren Ende zum oberen Ende der Mantelfläche hin verjüngt.
In order to achieve the above object, a lubricant receptacle for the vertical conveyance of lubricant by means of a crankshaft of a refrigerant compressor comprises a sleeve element with a clear cross section delimited by an inner wall, which extends along a longitudinal axis of the sleeve element from an upper end to a lower end of the sleeve member, the lubricant receptacle further comprising an inner member having an outer surface extending along a longitudinal axis of the inner member from a lower end to an upper end, wherein in an operative state of the lubricant receptacle
  • the inner element is arranged with its lateral surface at least in sections within the clear cross section of the sleeve element,
  • viewed in the direction from the lower end to the upper end of the sleeve element, the lower end of the lateral surface is arranged in front of the upper end thereof and
  • the inner element and the sleeve element can be rotated relative to one another about the longitudinal axis of the sleeve element and/or the longitudinal axis of the inner element, provided that the clear cross section tapers from the lower end to the upper end of the sleeve element at least in a receiving segment provided for receiving the inner element and that the inner element in the region of the lateral surface tapers from the lower end to the upper end of the lateral surface.

Da es nur auf die relative Drehung des Hülsenelements und des Innenelements zueinander ankommt, kann beispielsweise das Innenelement drehfest mit der Kurbelwelle verbunden und das Hülsenelement rotatorisch - bis auf vernachlässigbare geringfügige Verdrehwinkel - fixiert sein. Beim Betrieb des Kompressors dreht sich die Kurbelwelle und entsprechend dann auch das Innenelement, wohingegen das Hülsenelement nicht rotiert.Since only the relative rotation of the sleeve element and the inner element to one another is important, the inner element can, for example, be connected to the crankshaft in a rotationally fixed manner and the sleeve element can be rotationally fixed—apart from a negligible, minor angle of rotation. During operation of the compressor, the crankshaft rotates and, accordingly, the inner element rotates, whereas the sleeve element does not rotate.

Oder es kann das Hülsenelement drehfest mit der Kurbelwelle verbunden und das Innenelement rotatorisch- bis auf vernachlässigbare geringfügige Verdrehwinkel - fixiert sein.Or the sleeve element can be connected to the crankshaft in a rotationally fixed manner and the inner element can be rotationally fixed except for a negligible, minor angle of rotation.

Eine drehfeste Verbindung zwischen dem Innenelement bzw. Hülsenelement und der Kurbelwelle kann grundsätzlich direkt oder indirekt, d.h. unter Zwischenschaltung mindestens eines weiteren Elements wie z.B. einer Dichtung, eines Befestigungselements etc., erfolgen.A non-rotatable connection between the inner element or sleeve element and the crankshaft can in principle be direct or indirect, ie with the interposition of at least one other element such as a seal, a fastener, etc., take place.

Das Hülsenelement kann insbesondere im Bereich seines oberen Endes mit der Kurbelwelle verbunden sein. Denkbar wäre etwa, dass das Hülsenelement mit seinem lichten Querschnitt im Bereich des oberen Endes auf die Kurbelwelle aufgeschoben und auf dieser z.B. mittels eines Presssitzes gehalten ist. Hierfür kann es vorgesehen sein, dass sich der lichte Querschnitt im Bereich des oberen Endes gegenüber der im Aufnahmesegment vorhandenen Verjüngung wieder erweitert, um die Kurbelwelle aufnehmen zu können.The sleeve element can be connected to the crankshaft, in particular in the region of its upper end. It would be conceivable, for example, for the sleeve element to be slid onto the crankshaft with its clear cross-section in the region of the upper end and to be held thereon, for example by means of a press fit. For this purpose, it can be provided that the clear cross section in the region of the upper end compared to the im Recording segment existing taper extended again to accommodate the crankshaft.

Der guten Ordnung halber wird festgehalten, dass es nicht ausgeschlossen ist, dass das Hülsenelement seinerseits ein Teil oder Abschnitt eines größeren Elements ist. Der lichte Abschnitt erstreckt sich aber jedenfalls über diesen Teil oder Abschnitt, d.h. über das Hülsenelement.For the sake of good order, it is noted that it is not excluded that the sleeve element is itself a part or section of a larger element. In any case, the clear section extends over this part or section, i.e. over the sleeve element.

Gemäß dem oben Gesagten sind das Hülsenelement und das Innenelement derart ausgelegt, dass im Betriebszustand das Innenelement mit seiner Mantelfläche zumindest abschnittsweise innerhalb des lichten Querschnitts des Hülsenelements angeordnet ist. D.h. das Innenelement ist zumindest abschnittsweise im Aufnahmesegment aufgenommen.According to what was said above, the sleeve element and the inner element are designed in such a way that in the operating state the inner element is arranged with its lateral surface at least in sections within the clear cross section of the sleeve element. I.e. the inner element is at least partially accommodated in the receiving segment.

Gemäß dem oben Gesagten sind das Hülsenelement und das Innenelement derart ausgelegt, dass im Betriebszustand in Richtung vom unteren Ende zum oberen Ende des Hülsenelements gesehen das untere Ende der Mantelfläche vor dessen oberen Ende angeordnet ist. D.h. das Aufnahmesegment des lichten Querschnitts und das Innenelement, insbesondere dessen Mantelfläche, sind zumindest annähernd gleich orientiert. In der Praxis beim Einsatz in einem in Betrieb befindlichen Kältemittelkompressor ergibt sich dabei, dass die unteren Enden des Hülsenelements und der Mantelfläche in vertikaler Richtung unter den oberen Enden des Hülsenelements und der Mantelfläche angeordnet sind.According to what has been said above, the sleeve element and the inner element are designed in such a way that in the operating state viewed in the direction from the lower end to the upper end of the sleeve element, the lower end of the lateral surface is arranged in front of the upper end thereof. This means that the receiving segment of the clear cross section and the inner element, in particular its lateral surface, are oriented at least approximately the same. In practice, when used in an operating refrigerant compressor, the result is that the lower ends of the sleeve element and the shell surface are arranged in the vertical direction below the upper ends of the sleeve element and the shell surface.

Vorzugsweise ist dabei der Querschnitt des Innenelements bzw. die Geometrie des Innenelements mit seiner Mantelfläche an den lichten Querschnitt bzw. zumindest an das Aufnahmesegment angepasst. Beispielsweise wäre es denkbar, dass der lichte Querschnitt bzw. das Aufnahmesegment zur Verjüngung eine gewisse Abfolge von, vorzugsweise feinen, Stufen aufweist und dass die Mantelfläche eine dazu korrespondierende Abfolge von Stufen aufweist.The cross section of the inner element or the geometry of the inner element with its outer surface is preferably adapted to the clear cross section or at least to the receiving segment. For example, it would be conceivable for the clear cross section or the receiving segment to have a certain sequence of, preferably fine, steps for the purpose of narrowing, and for the lateral surface to have a corresponding sequence of steps.

Gemäß dem oben Gesagten sind das Hülsenelement und das Innenelement derart ausgelegt, dass im Betriebszustand das Innenelement und das Hülsenelement relativ zueinander um die Längsachse des Hülsenelements und/oder die Längsachse des Innenelements verdrehbar sind. Hiermit geht einher, dass die zumindest abschnittsweise Anordnung des Innenelements im Aufnahmesegment so ist, dass sich ein Spalt mit einer gewissen Spaltbreite zwischen der Mantelfläche und der Innenwand, die den lichten Querschnitt und damit insbesondere das Aufnahmesegment begrenzt, einstellt. Entsprechend kann in diesen Spalt Schmiermittel aus einem Schmiermittelsumpf des Kältemittelkompressors eintreten, wenn das Innenelement und das Hülsenelement zumindest abschnittsweise in den Schmiermittelsumpf ragen. Dabei ragt das Hülsenelement insbesondere im Bereich seines unteren Endes in den Schmiermittelsumpf und das Innenelement insbesondere im Bereich des unteren Endes seiner Mantelfläche.According to the above, the sleeve element and the inner element are designed such that in the operating state the inner element and the sleeve element can be rotated relative to one another about the longitudinal axis of the sleeve element and/or the longitudinal axis of the inner element. This means that the at least partial arrangement of the inner element in the receiving segment is such that a gap with a certain gap width is created between the lateral surface and the inner wall, which delimits the clear cross section and thus in particular the receiving segment. Accordingly, lubricant from a lubricant sump of the refrigerant compressor can enter this gap if the inner element and the sleeve element protrude at least in sections into the lubricant sump. The sleeve element projects into the lubricant sump, in particular in the area of its lower end, and the inner element in particular in the area of the lower end of its lateral surface.

Bei dem Schmiermittel kann es sich insbesondere um ein bei der Verwendung in Kältemittelkompressoren übliches Öl handeln.The lubricant can in particular be an oil that is customary when used in refrigerant compressors.

Durch Drehung der Kurbelwelle wird, insbesondere bei einer drehfesten Verbindung des Hülsenelements mit der Kurbelwelle, das relative Drehen des Hülsenelements und des Innenelements zueinander bewirkt. Vorzugsweise verdreht sich dabei das Innenelement gegenüber dem Stator nicht oder nur um einen beschränkten Winkelbereich, wohingegen das Hülsenelement vollständig rotiert. Wie oben bereits festgehalten, ist aber auch eine umgekehrte Auslegung möglich, bei der das Innenelement vollständig rotiert und das Hülsenelement gegenüber dem Stator nicht oder nur um einen beschränkten Winkelbereich.The rotation of the crankshaft causes the sleeve element and the inner element to rotate relative to one another, in particular when the sleeve element is connected in a rotationally fixed manner to the crankshaft. In this case, the inner element preferably does not rotate relative to the stator, or only rotates through a limited angular range, whereas the sleeve element rotates completely. As already stated above, however, a reverse design is also possible, in which the inner element rotates completely and the sleeve element does not rotate relative to the stator, or only rotates through a limited angular range.

Aufgrund der Viskosität des Schmiermittels bzw. der Reibung zwischen Schmiermittel und Hülsenelement bzw. Innenelement wirkt auf das Schmiermittel eine entsprechende Zentrifugalkraft. Diese drückt das Schmiermittel im Spalt in Richtung vom unteren Ende zum oberen Ende der Mantelfläche und damit in Richtung Kurbelwelle. Durch die Verjüngung des Innenelements bzw. des Aufnahmesegments kann dieses im Bereich des unteren Endes der Mantelfläche einen großen Durchmesser aufweisen, wodurch auch bei niedrigen Drehzahlen hinreichend große Tangentialgeschwindigkeiten bzw. Zentrifugalkräfte realisiert werden, um eine zuverlässige Schmiermittelförderung zu gewährleisten. Andererseits kann durch die Verjüngung des Innenelements bzw. des Aufnahmesegments sichergestellt werden, dass im Bereich des oberen Endes der Mantelfläche ein im Wesentlichen kontinuierlicher Übergang, d.h. ein Übergang ohne abrupten Druckabfall, für das Schmiermittel vom Spalt in eine Bohrung der Kurbelwelle erfolgt. Entsprechend kann eine nachteilige Reduktion des Schmiermittelflusses vermieden werden.Due to the viscosity of the lubricant or the friction between the lubricant and the sleeve element or the inner element, a corresponding centrifugal force. This pushes the lubricant in the gap in the direction from the lower end to the upper end of the lateral surface and thus in the direction of the crankshaft. Due to the narrowing of the inner element or the receiving segment, it can have a large diameter in the area of the lower end of the outer surface, whereby sufficiently high tangential speeds or centrifugal forces can be realized even at low speeds to ensure reliable lubricant delivery. On the other hand, the tapering of the inner element or the receiving segment can ensure that in the region of the upper end of the lateral surface there is a substantially continuous transition, ie a transition without an abrupt drop in pressure, for the lubricant from the gap into a bore of the crankshaft. Accordingly, an adverse reduction in the flow of the lubricant can be avoided.

Um die Förderung des Schmiermittels weiter zu verbessern, ist vorgesehen, dass die Innenwand und/oder die Mantelfläche mindestens eine spiralförmig verlaufende Rille aufweist. D.h. die Innenwand und/oder die Mantelfläche können auch mehrere Rillen aufweisen.In order to further improve the delivery of the lubricant, it is provided that the inner wall and/or the lateral surface has at least one groove running in a spiral shape. I.e. the inner wall and/or the lateral surface can also have several grooves.

Die mindestens eine Rille stellt neben dem Spalt ein zusätzliches Fördervolumen für das Schmiermittel zur Verfügung, das unabhängig von der Spaltbreite ist. Aufgrund der auf das Schmiermittel wirkenden Zentrifugalkräfte wird das Schmiermittel in und durch die mindestens eine Rille gedrückt.In addition to the gap, the at least one groove provides an additional delivery volume for the lubricant that is independent of the gap width. Due to the centrifugal forces acting on the lubricant, the lubricant is forced into and through the at least one groove.

Vorzugsweise weist die Mantelfläche die mindestens eine spiralförmige Rille auf, welche in Richtung vom unteren Ende zum oberen Ende der Mantelfläche verläuft. Die mindestens eine Rille kann sich dabei vom unteren Ende zum oberen Ende der Mantelfläche erstrecken. Sie kann aber theoretisch z.B. auch nur im Bereich des unteren Endes beginnen und/oder im Bereich des oberen Endes aufhören, sodass ein gewisser Überstand der Mantelfläche über die Rille im Bereich des unteren und/oder oberen Endes gegeben ist. In Richtung der Längsachse des Innenelements gesehen verläuft die mindestens eine Rille spiralförmig um diese Längsachse, wobei die Rille theoretisch auch auf der Längsachse enden könnte. Der guten Ordnung halber wird festgehalten, dass der Verlauf der Rille natürlich auch in umgekehrter Richtung, d.h. vom oberen Ende zum unteren Ende der Mantelfläche gegeben ist.The lateral surface preferably has the at least one spiral-shaped groove which runs in the direction from the lower end to the upper end of the lateral surface. The at least one groove can extend from the lower end to the upper end of the lateral surface. You can theoretically, for example, start only in the area of the lower end and/or stop in the area of the upper end, so that a certain overhang of the lateral surface over the groove in the area of the lower and/or upper end is given. Seen in the direction of the longitudinal axis of the inner element, the at least one groove runs spirally around this longitudinal axis, it being possible for the groove to theoretically also end on the longitudinal axis. For the sake of good order, it is noted that the course of the groove is of course also given in the opposite direction, ie from the upper end to the lower end of the lateral surface.

Um den Schmiermittelfluss, insbesondere im Hinblick auf seine Stabilität bzw. Kontinuität, zu optimieren, ist es erfindungsgemäß vorgesehen, dass die mindestens eine Rille einen variierenden Steigungswinkel aufweist, der vorzugsweise vom unteren Ende zum oberen Ende der Mantelfläche hin zunimmt.In order to optimize the flow of lubricant, in particular with regard to its stability or continuity, the invention provides that the at least one groove has a varying pitch angle, which preferably increases from the lower end to the upper end of the lateral surface.

Bei einer bevorzugten Ausführungsform der erfindungsgemäßen Schmiermittelaufnahme ist vorgesehen, dass der lichte Querschnitt des Hülsenelements zumindest in seinem Aufnahmesegment kegelstumpfförmig ausgebildet ist. Dies erweist sich einerseits herstellungstechnisch als günstig. Andererseits wirkt sich dies auch günstig auf das Strömungsverhalten des Schmiermittels bzw. Öls aus, da zumindest im Aufnahmesegment eine entsprechend glatte Innenwand gegeben ist.In a preferred embodiment of the lubricant receptacle according to the invention, it is provided that the clear cross section of the sleeve element is designed in the shape of a truncated cone, at least in its receptacle segment. On the one hand, this proves to be favorable in terms of production technology. On the other hand, this also has a favorable effect on the flow behavior of the lubricant or oil, since there is a correspondingly smooth inner wall at least in the receiving segment.

Falls die Innenwand die mindestens eine Rille aufweist, ist mit dem oben Gesagten natürlich gemeint, dass der lichte Querschnitt des Hülsenelements zumindest in seinem Aufnahmesegment abgesehen von der mindestens einen Rille kegelstumpfförmig ausgebildet ist.If the inner wall has the at least one groove, what is said above naturally means that the clear cross-section of the sleeve element is designed in the shape of a truncated cone, at least in its receiving segment, apart from the at least one groove.

Bei einer bevorzugten Ausführungsform der erfindungsgemäßen Schmiermittelaufnahme ist vorgesehen, dass die Mantelfläche des Innenelements als Mantelfläche eines Kegelstumpfs ausgebildet ist. Wiederum erweist sich dies einerseits herstellungstechnisch als günstig. Andererseits wirkt sich dies auch günstig auf das Strömungsverhalten des Schmiermittels bzw. Öls aus, da eine glatte Mantelfläche gegeben ist.In a preferred embodiment of the lubricant receptacle according to the invention, it is provided that the lateral surface of the inner element is designed as the lateral surface of a truncated cone. On the one hand, this again proves to be favorable in terms of manufacturing technology. On the other hand, this also has a favorable effect on the flow behavior of the lubricant or oil, since there is a smooth lateral surface.

Falls die Mantelfläche die mindestens eine Rille aufweist, ist mit dem oben Gesagten natürlich gemeint, dass die Mantelfläche abgesehen von der mindestens einen Rille als Mantelfläche eines Kegelstumpfs ausgebildet ist.If the lateral surface has the at least one groove, what is said above naturally means that the lateral surface, apart from the at least one groove, is designed as the lateral surface of a truncated cone.

Besonders günstige Strömungsverhältnisse liegen dabei vor, wenn auch zumindest das Aufnahmesegment kegelstumpfförmig ausgebildet ist, insbesondere wenn dabei eine zur Mantelfläche korrespondierende Auslegung vorgenommen wird. Entsprechend ist es bei einer besonders bevorzugten Ausführungsform der erfindungsgemäßen Schmiermittelaufnahme vorgesehen, dass der Kegelstumpfform des Aufnahmesegments des lichten Querschnitts ein Kegel mit einem ersten Öffnungswinkel zugrunde liegt, dass der Kegelstumpfform, gemäß der die Mantelfläche ausgebildet ist, ein Kegel mit einem zweiten Öffnungswinkel zugrunde liegt und dass die absolute Differenz zwischen dem ersten Öffnungswinkel und dem zweiten Öffnungswinkel kleiner gleich 10°, bevorzugt kleiner gleich 5°, besonders bevorzugt gleich 0°, ist. Als absolute Differenz ist dabei der Absolutbetrag der Differenz der beiden Öffnungswinkel zu verstehen.Particularly favorable flow conditions are present when at least the receiving segment is designed in the shape of a truncated cone, in particular when a design corresponding to the lateral surface is carried out. Accordingly, in a particularly preferred embodiment of the lubricant receptacle according to the invention, it is provided that the truncated cone shape of the receptacle segment of the clear cross section is based on a cone with a first opening angle, that the truncated cone shape according to which the lateral surface is formed is based on a cone with a second opening angle and that the absolute difference between the first opening angle and the second opening angle is less than or equal to 10°, preferably less than or equal to 5°, particularly preferably equal to 0°. The absolute difference is to be understood as the absolute value of the difference between the two opening angles.

Bei einer bevorzugten Ausführungsform der erfindungsgemäßen Schmiermittelaufnahme ist vorgesehen, dass das Innenelement im Bereich des unteren Endes der Mantelfläche mindestens einen abstehenden Flügel und/oder ein Befestigungselement, vorzugsweise eine Öse, für ein Fixierungsmittel aufweist. Diese Ausgestaltung dient dazu, dass sich das Innenelement bei Rotation der Kurbelwelle nicht oder maximal nur um einen bestimmten Winkelbetrag verdreht, wohingegen das Hülsenelement mit der Kurbelwelle rotiert. Hierzu kann der Flügel, der in den Schmiermittelsumpf eintaucht, aufgrund der Viskosität des Schmiermittels ausreichen, d.h. das Schmiermittel bewirkt einen hinreichend großen Widerstand gegen eine Drehung des Innenelements. Zur Erhöhung dieses Widerstands kann die Fläche des Flügels entsprechend größer gestaltet werden. Typischerweise steht der mindestens eine Flügel nicht von der Mantelfläche ab, sondern von einer Art Grundfläche des Innenelements, die im Wesentlichen normal auf die Längsachse des Innenelements steht. Insbesondere erstreckt sich der mindestens eine Flügel zumindest abschnittsweise parallel - sowie normal - zur Längsachse und weist dabei vom oberen Ende der Mantelfläche weg.In a preferred embodiment of the lubricant receptacle according to the invention, it is provided that the inner element has at least one protruding wing and/or a fastening element, preferably an eyelet, for a fixing means in the region of the lower end of the lateral surface. This configuration serves to ensure that the inner element does not rotate or only rotates by a certain angular amount when the crankshaft rotates, whereas the sleeve element rotates with the crankshaft. For this purpose, the wing, which dips into the lubricant sump, is sufficient due to the viscosity of the lubricant, ie the lubricant causes a sufficiently large resistance to rotation of the inner element. To increase this resistance, the area of the wing can be made correspondingly larger. Typically, the at least one wing does not protrude from the lateral surface, but from a kind of base surface of the Inner member that is substantially normal to the longitudinal axis of the inner member. In particular, the at least one wing extends at least in sections parallel—and normal—to the longitudinal axis and points away from the upper end of the lateral surface.

Alternativ oder zusätzlich kann ein Fixierungsmittel, beispielsweise in Form eines Bügels oder einer Halterung, vorgesehen sein, das einerseits am Befestigungselement befestigt wird und sich andererseits an einem im Wesentlichen unbeweglichen Element, z.B. am Stator, abstützt oder mit diesem starr verbunden ist.Alternatively or additionally, a fixing means, for example in the form of a bracket or a bracket, can be provided, which is fastened to the fastening element on the one hand and is supported on an essentially immovable element, e.g. on the stator, on the other hand or is rigidly connected to it.

Das Fixierungsmittel kann auch dazu dienen, das Innenelement bezogen auf die Längsachse, d.h. mit einem Richtungsanteil parallel zur Längsachse, des Hülsenelements fix oder beweglich zu lagern. Alternativ oder zusätzlich dazu kann zum Zwecke einer solchen Lagerung der Auftrieb ausgenutzt werden, den das Innenelement beim Eintauchen in den Schmiermittelsumpf erfährt. Insbesondere kann das Innenelement dabei so ausgelegt sein, dass es auf dem Schmiermittel aufschwimmt (also nicht völlig untergeht), was eine besonders kostengünstige Lagerung des Innenelements darstellt. Entsprechend ist es bei einer bevorzugten Ausführungsform der erfindungsgemäßen Schmiermittelaufnahme vorgesehen, dass das Innenelement aus einem Material, vorzugsweise aus einem Kunststoff, gefertigt ist, dessen Dichte geringer ist als die Dichte des Schmiermittels. Die Fertigung des Innenelements aus einem Leichtmetall bzw. einer Leichtmetalllegierung, insbesondere einer Aluminiumlegierung, zur Erzielung der gewünschten Dichte wäre dabei auch denkbar.The fixing means can also serve to mount the inner element in a fixed or movable manner in relation to the longitudinal axis, ie with a directional component parallel to the longitudinal axis, of the sleeve element. Alternatively or additionally, the buoyancy experienced by the inner element when immersed in the lubricant sump can be used for the purpose of such a bearing. In particular, the inner element can be designed in such a way that it floats on the lubricant (ie does not sink completely), which represents a particularly cost-effective mounting of the inner element. Accordingly, in a preferred embodiment of the lubricant holder according to the invention, it is provided that the inner element is made of a material, preferably a plastic, whose density is lower than the density of the lubricant. It would also be conceivable to manufacture the inner element from a light metal or a light metal alloy, in particular an aluminum alloy, to achieve the desired density.

Analog zum oben Gesagten ist es bei einem Kältemittelkompressor mit einem hermetisch kapselbaren Kompressorgehäuse, einer in einem Gehäuseinneren des Kompressorgehäuses angeordneten elektrischen Antriebseinheit, umfassend einen Rotor und einen Stator, einer mit dem Rotor drehfest verbundenen Kurbelwelle, sowie mit einer in dem Gehäuseinneren angeordneten Kolben-Zylinder-Einheit, welche einen beweglich in einem Zylinder der Kolben-Zylinder-Einheit gelagerten Kolben umfasst, welcher zur Verdichtung von Kältemittel von der Kurbelwelle antreibbar ist, erfindungsgemäß vorgesehen, dass der Kältemittelkompressor eine im Betriebszustand befindliche erfindungsgemäße Schmiermittelaufnahme aufweist, um Schmiermittel aus einem in einem Bodenbereich des Kompressorgehäuses ausgebildeten Schmiermittelsumpf über die Kurbelwelle zu fördern.It is analogous to the above in a refrigerant compressor with a hermetically encapsulated compressor housing, an electric drive unit arranged in the interior of the compressor housing, comprising a rotor and a stator, a crankshaft non-rotatably connected to the rotor, and a piston-cylinder arranged in the interior of the housing -Unit, which comprises a piston which is movably mounted in a cylinder of the piston-cylinder unit and which can be driven by the crankshaft to compress refrigerant, according to the invention that the refrigerant compressor has a lubricant receptacle according to the invention which is in the operating state, in order to collect lubricant from one in one To promote bottom area of the compressor housing trained lubricant sump over the crankshaft.

Wie ebenfalls weiter oben erläutert, kann das Innenelement oder das Hülsenelement drehfest mit der Kurbelwelle verbunden werden. Entsprechend ist es bei einer bevorzugten Ausführungsform des erfindungsgemäßen Kältemittelkompressors vorgesehen, dass das Hülsenelement der Schmiermittelaufnahme drehfest mit der Kurbelwelle verbunden ist.As also explained above, the inner member or the sleeve member can be non-rotatably connected to the crankshaft. Accordingly, in a preferred embodiment of the refrigerant compressor according to the invention, it is provided that the sleeve element of the lubricant receptacle is connected to the crankshaft in a rotationally fixed manner.

Bei einer bevorzugten Ausführungsform des erfindungsgemäßen Kältemittelkompressors ist vorgesehen, dass die Kurbelwelle eine, bevorzugt zumindest abschnittsweise schräg zu einer Drehachse der Kurbelwelle verlaufende, Bohrung aufweist, die mit dem lichten Querschnitt des Hülsenelements in fluidischer Verbindung steht, wobei das Innenelement in die Bohrung hineinragt. Diese Anordnung ist durch die Verjüngung des Innenelements möglich und gewährleistet einen besonders guten Übergang für das Schmiermittel vom Spalt in die Bohrung der Kurbelwelle. Über mindestens eine Austrittsbohrung kann das Schmiermittel sodann aus der Kurbelwelle - genauer aus der Bohrung der Kurbelwelle - zu zu schmierenden Stellen austreten. Vorzugsweise sind mehrere Austrittsbohrungen vorgesehen, die entlang der Drehachse der Kurbelwelle gesehen hintereinander angeordnet sind.In a preferred embodiment of the refrigerant compressor according to the invention, it is provided that the crankshaft has a bore, preferably at least partially oblique to an axis of rotation of the crankshaft, which is in fluid communication with the clear cross section of the sleeve element, with the inner element protruding into the bore. This arrangement is possible due to the narrowing of the inner element and ensures a particularly good transition for the lubricant from the gap into the bore of the crankshaft. The lubricant can then escape from the crankshaft—more precisely, from the bore of the crankshaft—to points to be lubricated via at least one outlet bore. Preferably there are several exit bores provided, which are arranged one behind the other seen along the axis of rotation of the crankshaft.

Gemäß dem weiter oben bereits Gesagten ist es bei einer bevorzugten Ausführungsform des erfindungsgemäßen Kältemittelkompressors vorgesehen, dass das Innenelement bezogen auf die Längsachse des Hülsenelements beweglich ist. Durch eine entsprechende Bewegung des Innenelements parallel zur Längsachse des Hülsenelements wird die Spaltbreite geändert. Entsprechend kann die Spaltbreite an Betriebsparameter wie etwa die Temperatur und/oder die Viskosität des Schmiermittels und/oder die Drehzahl angepasst werden, um einen optimalen Schmiermittelfluss zu ermöglichen. Beispielsweise kann bei einem dünnflüssiger werdenden Schmiermittel die Spaltbreite reduziert werden, um eine erhöhte Förderung zu bewirken.According to what has already been said above, it is provided in a preferred embodiment of the refrigerant compressor according to the invention that the inner element is movable in relation to the longitudinal axis of the sleeve element. The gap width is changed by a corresponding movement of the inner element parallel to the longitudinal axis of the sleeve element. Accordingly, the gap width can be adjusted to operating parameters such as the temperature and/or the viscosity of the lubricant and/or the speed in order to enable an optimal flow of the lubricant. For example, with a lubricant that is becoming thinner, the gap width can be reduced in order to bring about increased delivery.

Insbesondere kann eine solche Justierung oder Regelung der Spaltbreite in einfacher Weise automatisch bzw. von selbst erfolgen. Hierzu ist es bei einer bevorzugten Ausführungsform des erfindungsgemäßen Kältemittelkompressors vorgesehen, dass ein als Federelement ausgebildetes Fixierungsmittel, vorzugsweise in Form eines federnden Drahtbügels, vorgesehen ist, mit dem das Innenelement im Wesentlichen drehfest mit dem Stator oder anderen Bauteilen des Kältemittelkompressors verbunden ist. Wie bereits geschildert, können geringfügige Verdrehwinkel des Innenelements toleriert werden, die sich aufgrund der Elastizität des Federelements ergeben.In particular, such an adjustment or regulation of the gap width can take place automatically or by itself in a simple manner. For this purpose, a preferred embodiment of the refrigerant compressor according to the invention provides that a fixing means designed as a spring element, preferably in the form of a resilient wire clip, is provided, with which the inner element is essentially non-rotatably connected to the stator or other components of the refrigerant compressor. As already described, slight twisting angles of the inner element can be tolerated, which result from the elasticity of the spring element.

Die Verbindung mit dem Stator oder anderen - im Wesentlichen unbeweglichen - Bauteilen des Kältemittelkompressors kann direkt oder indirekt, d.h. unter Zwischenschaltung weiterer Elemente, gegeben sein.The connection to the stator or other - essentially immobile - components of the refrigerant compressor can be direct or indirect, i.e. with the interposition of other elements.

Das Federelement stellt insbesondere eine gewisse Beweglichkeit des Innenelements parallel zur Längsachse des Hülsenelements sicher. Das Federelement bewirkt dabei, dass das Innenelement bis zu einem gewissen Grad in Richtung Aufnahmesegment gedrückt wird, was tendenziell zu einer Verringerung der Spaltbreite führt. Dem wirkt ein gewisser Druck des Schmiermittels im Spalt entgegen, welcher Druck von unterschiedlichen Faktoren abhängt. Beispielsweise wird das Innenelement von der Innenwand des Aufnahmesegments gegen die Federkraft des Federelements umso stärker weg gedrückt, je dickflüssiger das Schmiermittel ist oder je größer die Drehzahl ist, und desto größer bleibt die Spaltbreite.. Wird das Schmiermittel dünnflüssiger oder sinkt die Drehzahl, so wird das Innenelement durch das im Spalt strömende Schmiermittel von der Innenwand des Aufnahmesegments weniger stark gegen die Federkraft des Federelements weg gedrückt, und die Spaltbreite verringert sich entsprechend.In particular, the spring element ensures a certain mobility of the inner element parallel to the longitudinal axis of the sleeve element. The spring element causes that the inner member is pushed towards the receiving segment to some degree, which tends to reduce the gap width. This is counteracted by a certain pressure of the lubricant in the gap, which pressure depends on various factors. For example, the inner element is pressed away from the inner wall of the receiving segment against the spring force of the spring element, the stronger the thicker the lubricant is or the higher the speed, and the larger the gap width remains the inner element is pressed less strongly away from the inner wall of the receiving segment by the lubricant flowing in the gap against the spring force of the spring element, and the gap width decreases accordingly.

Alternativ kann die Justierung - zumindest grob - auch unter der oben geschilderten Ausnutzung des Auftriebs des Innenelements im Schmiermittel erfolgen, wobei bei Vorhandensein des mindestens einen Flügels auf das Fixierungsmittel auch gänzlich verzichtet werden kann. Durch den Auftrieb wird das Innenelement grundsätzlich in Richtung Aufnahmesegment gedrückt, was tendenziell zu einer Verringerung der Spaltbreite führt - analog zur oben beschriebenen Ausführungsform mit Federelement. Dem wirkt der Druck des Schmiermittels im Spalt entgegen, welcher Druck von unterschiedlichen Faktoren abhängt. Beispielsweise wird die Spaltbreite umso größer, je dickflüssiger das Schmiermittel ist oder je größer die Drehzahl ist. Wird das Schmiermittel dünnflüssiger oder sinkt die Drehzahl, so verringert sich die Spaltbreite entsprechend.Alternatively, the adjustment can also take place—at least roughly—using the above-described utilization of the buoyancy of the inner element in the lubricant, in which case the fixing means can also be dispensed with entirely if the at least one wing is present. Due to the buoyancy, the inner element is basically pressed in the direction of the receiving segment, which tends to lead to a reduction in the gap width—similar to the embodiment with the spring element described above. This is counteracted by the pressure of the lubricant in the gap, which pressure depends on various factors. For example, the more viscous the lubricant or the higher the speed, the greater the gap width. If the lubricant becomes thinner or the speed decreases, the gap width decreases accordingly.

Insbesondere können auf die geschilderte Weise Schwankungen der Schmiermittelförderung aufgrund von Drehzahlschwankungen automatisch ausgeglichen werden. Solche Drehzahlschwankungen können besonders ausgeprägt bei Kompressoren mit variabler Drehzahl und sehr geringen Trägheitsmomenten von Kurbelwelle und Rotor auftreten.In particular, fluctuations in the lubricant delivery due to speed fluctuations can be automatically compensated for in the manner described. Such speed fluctuations can be particularly pronounced in compressors with variable Speed and very low moments of inertia of the crankshaft and rotor occur.

KURZE BESCHREIBUNG DER FIGURENBRIEF DESCRIPTION OF THE FIGURES

Die Erfindung wird nun anhand eines Ausführungsbeispiels näher erläutert. Die Zeichnungen sind beispielhaft und sollen den Erfindungsgedanken zwar darlegen, ihn aber keinesfalls einengen oder gar abschließend wiedergeben.The invention will now be explained in more detail using an exemplary embodiment. The drawings are exemplary and are intended to explain the idea of the invention, but in no way restrict or even conclusively reproduce it.

Dabei zeigt:

Fig. 1
ein Innenelement einer Ausführungsform einer erfindungsgemäßen Schmiermittelaufnahme in axonometrischer Ansicht
Fig. 2
eine Schnittansicht der Ausführungsform der erfindungsgemäßen Schmiermittelaufnahme, wobei die Schmiermittelaufnahme auf einer Kurbelwelle eines erfindungsgemäßen Kältemittelkompressors montiert ist
Fig. 3
eine Schnittansicht eines erfindungsgemäßen Kältemittelkompressors mit der Schmiermittelaufnahme aus Fig. 2
It shows:
1
an inner element of an embodiment of a lubricant receptacle according to the invention in an axonometric view
2
a sectional view of the embodiment of the lubricant receiver according to the invention, wherein the lubricant receiver is mounted on a crankshaft of a refrigerant compressor according to the invention
3
a sectional view of a refrigerant compressor according to the invention with the lubricant receptacle 2

WEGE ZUR AUSFÜHRUNG DER ERFINDUNGWAYS TO CARRY OUT THE INVENTION

Fig. 1 zeigt eine axonometrische Ansicht eines Innenelements 9 einer erfindungsgemäßen Schmiermittelaufnahme 1. Letztere ist in einem Betriebszustand und an einer Kurbelwelle 2 eines erfindungsgemäßen Kältemittelkompressors 3 befestigt in Fig. 2 in einer Schnittansicht gezeigt. 1 shows an axonometric view of an inner element 9 of a lubricant receptacle 1 according to the invention. The latter is in an operating state and is attached to a crankshaft 2 of a refrigerant compressor 3 according to the invention in 2 shown in a sectional view.

Die Schmiermittelaufnahme 1 dient zur vertikalen Förderung von Schmiermittel, insbesondere Öl 15, aus einem in einem Bodenbereich 25 eines Kompressorgehäuses 18 des Kältemittelkompressors 3 ausgebildeten Schmiermittelsumpf 26, vgl. die Schnittansicht der Fig. 3, über die Kurbelwelle 2. Die Kurbelwelle 2 weist hierzu eine in Fig. 2 gut erkennbare Bohrung 27 auf, von der das Öl 15 über Austrittsbohrungen 28 zu zu schmierenden Stellen austreten kann. Die Bohrung 27 kann zur optimalen Förderung des Öls 15 schräg zu einer Drehachse 29 der Kurbelwelle 2 verlaufend ausgeführt sein, wie in Fig. 2 dargestellt.The lubricant holder 1 is used for the vertical promotion of lubricant, in particular oil 15, from one in one Lubricant sump 26 formed in the bottom area 25 of a compressor housing 18 of the refrigerant compressor 3, see the sectional view of FIG 3 , via the crankshaft 2. The crankshaft 2 has a 2 easily recognizable bore 27, from which the oil 15 can escape via outlet bores 28 to points to be lubricated. For optimal delivery of the oil 15, the bore 27 can be designed to run obliquely to an axis of rotation 29 of the crankshaft 2, as shown in FIG 2 shown.

Im Kompressorgehäuse 18 ist außerdem eine elektrische Antriebseinheit 19 mit einem Rotor 20 und einem Stator 21 angeordnet, wobei die Kurbelwelle 2 drehfest mit dem Rotor 20 verbunden ist. Weiters befindet sich im Kompressorgehäuse 18 eine Kolben-Zylinder-Einheit 22, welche einen beweglich in einem Zylinder 24 der Kolben-Zylinder-Einheit 22 gelagerten Kolben 23 umfasst, welcher zur Verdichtung von Kältemittel von der Kurbelwelle 2 antreibbar ist.An electric drive unit 19 with a rotor 20 and a stator 21 is also arranged in the compressor housing 18 , the crankshaft 2 being connected to the rotor 20 in a rotationally fixed manner. Also located in the compressor housing 18 is a piston-cylinder unit 22 which includes a piston 23 which is movably mounted in a cylinder 24 of the piston-cylinder unit 22 and can be driven by the crankshaft 2 to compress refrigerant.

Die Schmiermittelaufnahme 1 umfasst ein Hülsenelement 4 mit einem von einer Innenwand 34 begrenzten lichten Querschnitt 5, der sich entlang einer Längsachse 6 des Hülsenelements 4 von einem oberen Ende 7 bis zu einem unteren Ende 8 des Hülsenelements 4 erstreckt. Wie in Fig. 2 ersichtlich, kann der lichte Querschnitt 5 am oberen Ende 7 zur Aufnahme der Kurbelwelle 2 dienen, um beispielsweise mittels eines Presssitzes eine drehfeste Verbindung zwischen dem Hülsenelement 4 und damit der Schmiermittelaufnahme 1 und der Kurbelwelle 2 herzustellen.The lubricant holder 1 comprises a sleeve element 4 with a clear cross section 5 delimited by an inner wall 34 which extends along a longitudinal axis 6 of the sleeve element 4 from an upper end 7 to a lower end 8 of the sleeve element 4 . As in 2 As can be seen, the clear cross section 5 at the upper end 7 can serve to accommodate the crankshaft 2 in order to produce a non-rotatable connection between the sleeve element 4 and thus the lubricant receptacle 1 and the crankshaft 2, for example by means of a press fit.

Es sind aber prinzipiell auch erfindungsgemäße Schmiermittelaufnahmen 1 möglich, bei denen eine drehfeste Verbindung der Schmiermittelaufnahme 1 mit der Kurbelwelle 2 über eine drehfeste Verbindung zwischen dem Innenelement 9 und der Kurbelwelle 2 erfolgt.In principle, however, lubricant receptacles 1 according to the invention are also possible in which the lubricant receptacle 1 is non-rotatably connected to the crankshaft 2 via a non-rotatably connected connection between the inner element 9 and the crankshaft 2 .

Weiters umfasst die Schmiermittelaufnahme 1 das Innenelement 9, das eine Mantelfläche 10 aufweist, die sich entlang einer Längsachse 11 des Innenelements 9 von einem unteren Ende 12 bis zu einem oberen Ende 13 erstreckt und im dargestellten Ausführungsbeispiel eine Rille 14 aufweist. Diese Rille 14 verläuft spiralförmig in Richtung vom unteren Ende 12 zum oberen Ende 13 und erstreckt sich vom unteren Ende 12 bis zum oberen Ende 13 der Mantelfläche 10. Die Innenwand 34 weist im dargestellten Ausführungsbeispiel keine Rille auf, obgleich dies prinzipiell möglich ist.Furthermore, the lubricant receptacle 1 comprises the inner element 9, which has an outer surface 10 which extends along a longitudinal axis 11 of the inner element 9 from a lower end 12 to an upper end 13 and has a groove 14 in the exemplary embodiment shown. This groove 14 runs spirally in the direction from the lower end 12 to the upper end 13 and extends from the lower end 12 to the upper end 13 of the lateral surface 10. The inner wall 34 has no groove in the illustrated embodiment, although this is possible in principle.

Im Betriebszustand der Schmiermittelaufnahme 1 ist das Innenelement 9 mit seiner Mantelfläche 10 zumindest abschnittsweise - im dargestellten Ausführungsbeispiel im Wesentlichen vollständig - innerhalb des lichten Querschnitts 5 des Hülsenelements 4, genauer in einem zur Aufnahme vorgesehenen Aufnahmesegment 33 des lichten Querschnitts 5, angeordnet. Dabei ist in Richtung vom unteren Ende 8 zum oberen Ende 9 des Hülsenelements 4 gesehen das untere Ende 12 der Mantelfläche 10 vor dessen oberen Enden 13 angeordnet, d.h. das Hülsenelement 4 und das Innenelement 9 sind gewissermaßen gleich orientiert bzw. ausgerichtet. Das Hülsenelement 4 und das Innenelement 9 sind weiters so ausgelegt, dass das Innenelement 9 und das Hülsenelement 4 relativ zueinander um die Längsachse 6 des Hülsenelements 4 und/oder die Längsachse 11 des Innenelements 9 verdrehbar sind. Diese Drehung wird beim Betrieb des Kältemittelkompressors 3 durch die drehfeste Verbindung der Schmiermittelaufnahme 1 mit der Kurbelwelle 2 vermittelt bzw. erzeugt. Grundsätzlich kommt es nur auf die relative Drehung zwischen dem Hülsenelement 4 und dem Innenelement 9 an, d.h. es wäre denkbar, dass das Innenelement 9 rotatorisch angetrieben wird und das Hülsenelement 4 rotatorisch im Wesentlichen fixiert ist. Im gezeigten Ausführungsbeispiel wird aufgrund der drehfesten Verbindung des Hülsenelements 4 mit der Kurbelwelle 2 das Hülsenelement 4 rotatorisch angetrieben, wenn sich die Kurbelwelle 2 dreht, das Innenelement 9 hingegen nicht.In the operating state of the lubricant receptacle 1, the inner element 9 is arranged with its lateral surface 10 at least in sections - essentially completely in the exemplary embodiment shown - within the clear cross section 5 of the sleeve element 4, more precisely in a receiving segment 33 of the clear cross section 5 provided for receiving. Viewed in the direction from the lower end 8 to the upper end 9 of the sleeve element 4, the lower end 12 of the lateral surface 10 is arranged in front of its upper end 13, ie the sleeve element 4 and the inner element 9 are to a certain extent oriented or aligned in the same way. The sleeve element 4 and the inner element 9 are also designed such that the inner element 9 and the sleeve element 4 can be rotated relative to one another about the longitudinal axis 6 of the sleeve element 4 and/or the longitudinal axis 11 of the inner element 9 . During operation of the refrigerant compressor 3 , this rotation is mediated or generated by the non-rotatable connection of the lubricant receptacle 1 to the crankshaft 2 . In principle, only the relative rotation between the sleeve element 4 and the inner element 9 is important, ie it would be conceivable for the inner element 9 to be driven in rotation and for the sleeve element 4 to be essentially fixed in terms of rotation. In the embodiment shown, due to the non-rotatable connection of the sleeve element 4 with the crankshaft 2 the sleeve element 4 is driven in rotation when the crankshaft 2 rotates, but the inner element 9 does not.

Um Drehbewegungen des Innenelements 9 weitgehend zu vermeiden, kann dieses z.B. mit dem Stator 21 mittels eines Fixierungsmittels verbunden werden. Das Innenelement 9 kann hierfür, wie in Fig. 1 dargestellt ist, ein Befestigungselement in Form einer Öse 16 aufweisen, mit der das Fixierungsmittel in Eingriff gebracht werden kann.In order to largely avoid rotary movements of the inner element 9, this can be connected to the stator 21 by means of a fixing means, for example. For this purpose, the inner element 9 can be used, as in 1 shown, have a fastening element in the form of an eyelet 16 with which the fixing means can be brought into engagement.

Wie beispielsweise aus Fig. 2 hervorgeht, ergibt sich im Betriebszustand, d.h. bei der Anordnung des Innenelements 9 im Hülsenelement 4, ein Spalt 30 mit einer Spaltbreite 31 zwischen der Mantelfläche 10 und der Innenwand 34, die den lichten Querschnitt 5 und damit insbesondere das Aufnahmesegment 33 begrenzt. Entsprechend kann in diesen Spalt 30 das Öl 15 aus dem Schmiermittelsumpf 26 eintreten, wenn das Innenelement 9 und das Hülsenelement 4 zumindest abschnittsweise in den Schmiermittelsumpf 26 ragen. Dabei ragt das Hülsenelement 4 insbesondere im Bereich seines unteren Endes 8 in den Schmiermittelsumpf 26 und das Innenelement 9 insbesondere im Bereich des unteren Endes 12 seiner Mantelfläche 10. Aufgrund der Viskosität des Öls 15 bzw. der Reibung zwischen Öl 15 und Hülsenelement 4 wirkt auf das Öl 15 bei Drehung des Hülsenelements 4 eine entsprechende Zentrifugalkraft. Diese drückt das Öl 15 im Spalt 30 und insbesondere in der mindestens einen Rille 14 in Richtung vom unteren Ende 12 zum oberen Ende 13 der Mantelfläche 10 und damit in Richtung Kurbelwelle 2.Such as from 2 shows, in the operating state, ie when the inner element 9 is arranged in the sleeve element 4, there is a gap 30 with a gap width 31 between the lateral surface 10 and the inner wall 34, which delimits the clear cross section 5 and thus in particular the receiving segment 33. Accordingly, the oil 15 from the lubricant sump 26 can enter this gap 30 if the inner element 9 and the sleeve element 4 protrude at least in sections into the lubricant sump 26 . The sleeve element 4 projects into the lubricant sump 26, in particular in the area of its lower end 8, and the inner element 9, in particular in the area of the lower end 12 of its lateral surface 10. Due to the viscosity of the oil 15 or the friction between the oil 15 and the sleeve element 4, the Oil 15 upon rotation of the sleeve member 4 a corresponding centrifugal force. This presses the oil 15 in the gap 30 and in particular in the at least one groove 14 in the direction from the lower end 12 to the upper end 13 of the lateral surface 10 and thus in the direction of the crankshaft 2.

Über die Rille 14 kann das Öl 15 in jedem Fall besonders gut Richtung Kurbelwelle 4 fließen - unabhängig von der genauen Spaltbreite 31. Bei dem gezeigten Ausführungsbeispiel steht die Bohrung 27 der Kurbelwelle 2 mit dem lichten Querschnitt 5 und damit insbesondere auch mit der Rille 14 in fluidischer Verbindung, sodass das Öl 15 bis in die Bohrung 27 gelangen kann.In any case, the oil 15 can flow particularly well in the direction of the crankshaft 4 via the groove 14 - regardless of the exact gap width 31. In the exemplary embodiment shown, the bore 27 of the crankshaft 2 with the clear cross section 5 and thus in particular also with the groove 14 is in more fluid Connection so that the oil 15 can get into the bore 27.

Einerseits verjüngt sich der lichte Querschnitt 5 zumindest im Aufnahmesegment 33 in Richtung vom unteren Ende 8 zum oberen Ende 7 hin. Andererseits verjüngt sich das Innenelement 9 im Bereich der Mantelfläche 10 in Richtung vom unteren Ende 12 zum oberen Ende 13 der Mantelfläche 10 hin. Durch die Verjüngung des Innenelements 9 bzw. des Aufnahmesegments 33 kann dieses im Bereich des unteren Endes 12 der Mantelfläche 10 einen großen Durchmesser aufweisen, wodurch auch bei niedrigen Drehzahlen hinreichend große Tangentialgeschwindigkeiten bzw. Zentrifugalkräfte (im Spalt 30) realisiert werden, um eine zuverlässige Förderung des Öls 15 zu gewährleisten. Andererseits kann durch die Verjüngung des Innenelements 9 bzw. des Aufnahmesegments 33 sichergestellt werden, dass im Bereich des oberen Endes 13 der Mantelfläche 10 ein im Wesentlichen kontinuierlicher Übergang, d.h. ein Übergang ohne abrupten Druckabfall, für das Öl 15 vom Spalt 30 in die Bohrung 27 der Kurbelwelle 2 erfolgt. Bei dem dargestellten Ausführungsbeispiel wird dieser kontinuierliche Übergang nochmals verbessert, indem das Innenelement 9 mit seiner Verjüngung so ausgelegt ist, dass das Innenelement 9 in die Bohrung 27 hineinragt, vgl. Fig. 2. Entsprechend kann eine nachteilige Reduktion des Schmiermittelflusses praktisch vollständig vermieden werden.On the one hand, the clear cross section 5 tapers at least in the receiving segment 33 in the direction from the lower end 8 to the upper end 7 . On the other hand, the inner element 9 tapers in the area of the lateral surface 10 in the direction from the lower end 12 to the upper end 13 of the lateral surface 10 . Due to the narrowing of the inner element 9 or the receiving segment 33, this can have a large diameter in the area of the lower end 12 of the lateral surface 10, whereby sufficiently large tangential speeds or centrifugal forces (in the gap 30) can be realized even at low speeds in order to ensure reliable delivery of the oil 15 to ensure. On the other hand, the tapering of the inner element 9 or the receiving segment 33 can ensure that in the area of the upper end 13 of the lateral surface 10 there is a substantially continuous transition, i.e. a transition without an abrupt pressure drop, for the oil 15 from the gap 30 into the bore 27 the crankshaft 2 takes place. In the exemplary embodiment shown, this continuous transition is further improved in that the inner element 9 is designed with its taper in such a way that the inner element 9 protrudes into the bore 27, cf. 2 . Accordingly, a disadvantageous reduction in the flow of lubricant can be avoided almost completely.

Die Form der Verjüngung des lichten Querschnitts 5 im Aufnahmesegment 33 einerseits und die Form der Verjüngung des Innenelements 9 im Bereich der Mantelfläche 10 andererseits sind bei dem dargestellten Ausführungsbeispiel aufeinander abgestimmt, um eine optimale Anordnung des Innenelements 9 im Hülsenelement 4 im Betriebszustand zu ermöglichen. Hierzu ist einerseits der lichte Querschnitt 5 des Hülsenelements 4 zumindest in seinem Aufnahmesegment 33 kegelstumpfförmig ausgebildet, wobei dieser Kegelstumpfform ein Kegel mit einem ersten Öffnungswinkel Θ1 zugrunde liegt. Andererseits ist die Mantelfläche 10 des Innenelements 9 abgesehen von der mindestens einen Rille 14 als Mantelfläche eines Kegelstumpfs ausgebildet, wobei dieser Kegelstumpfform ein Kegel mit einem zweiten Öffnungswinkel Θ2 zugrunde liegt. Die oben genannte Abstimmung wird bei dem gezeigten Ausführungsbeispiel weiters dadurch optimiert, dass der Absolutbetrag der Differenz zwischen dem ersten Öffnungswinkel Θ1 und dem zweiten Öffnungswinkel Θ2 kleiner gleich 10°, bevorzugt kleiner gleich 5°, besonders bevorzugt gleich 0°, ist.The shape of the narrowing of the clear cross-section 5 in the receiving segment 33 on the one hand and the shape of the narrowing of the inner element 9 in the area of the lateral surface 10 on the other hand are matched to one another in the exemplary embodiment shown in order to enable an optimal arrangement of the inner element 9 in the sleeve element 4 in the operating state. For this purpose, on the one hand, the clear cross section 5 of the sleeve element 4 is frustoconical, at least in its receiving segment 33 formed, this truncated cone shape being based on a cone with a first opening angle Θ1. On the other hand, the lateral surface 10 of the inner element 9 apart from the at least one groove 14 is designed as the lateral surface of a truncated cone, this truncated cone shape being based on a cone with a second opening angle Θ2. In the exemplary embodiment shown, the above-mentioned matching is further optimized in that the absolute amount of the difference between the first opening angle Θ1 and the second opening angle Θ2 is less than or equal to 10°, preferably less than or equal to 5°, particularly preferably equal to 0°.

Bei dem gezeigten Ausführungsbeispiel ist weiters vorgesehen, dass das Innenelement 9 bezogen auf die Längsachse 6 des Hülsenelements 4, d.h. mit einem Richtungsanteil parallel zur Längsachse 6, beweglich gelagert ist. Im Zusammenspiel mit dem sich verjüngenden Aufnahmesegment 33 und dem sich verjüngenden Innenelement 9 kann hierdurch die Spaltbreite 31 grundsätzlich justiert werden, insbesondere zur Anpassung an Betriebsparameter wie etwa die Temperatur und/oder die Viskosität des Öls 15 und/oder die Drehzahl, um einen optimalen Schmiermittelfluss zu ermöglichen. Beispielsweise könnte bei einem dünnflüssiger werdenden Öl 15 die Spaltbreite 31 reduziert werden, um eine erhöhte Förderung zu bewirken. Besonders genau ist die Justiermöglichkeit bei dem gezeigten Ausführungsbeispiel aufgrund der oben genannten Kegelstumpfformen.In the exemplary embodiment shown, it is further provided that the inner element 9 is movably mounted in relation to the longitudinal axis 6 of the sleeve element 4, i.e. with a directional portion parallel to the longitudinal axis 6. In interaction with the tapering receiving segment 33 and the tapering inner element 9, the gap width 31 can be adjusted in principle, in particular to adapt to operating parameters such as the temperature and/or the viscosity of the oil 15 and/or the speed, in order to achieve an optimal lubricant flow to allow. For example, in the case of oil 15 becoming thinner, the gap width 31 could be reduced in order to bring about increased delivery. The possibility of adjustment is particularly precise in the exemplary embodiment shown due to the above-mentioned truncated cone shapes.

Konkret ist bei der gezeigten Ausführungsform sogar eine automatische Justierung vorgesehen. Gemäß Fig. 3 ist hierfür das Fixierungsmittel als Federelement in Form eines federnden Drahtbügels 32 ausgebildet, mit dem das Innenelement 9 im Wesentlichen drehfest mit dem Stator 21 verbunden ist. Geringfügige Verdrehwinkel des Innenelements 9, die sich aufgrund der Elastizität des federnden Drahtbügels 32 möglicherweise ergeben, können dabei toleriert werden. Der federnde Drahtbügel 32 bewirkt jedenfalls, dass das Innenelement 9 bis zu einem gewissen Grad in Richtung Aufnahmesegment 33 gedrückt wird, was tendenziell zu einer Verringerung der Spaltbreite 31 führt. Dem wirkt ein gewisser Druck des Öls 15 im Spalt 30 entgegen, welcher Druck von unterschiedlichen Faktoren abhängt. Beispielsweise wird das Innenelement 9 von der Innenwand 34 des Aufnahmesegments 33 gegen die Federkraft des federnden Drahtbügels 32 umso stärker weg gedrückt, je dickflüssiger das Öl 15 ist oder je größer die Drehzahl ist, und desto größer bleibt die Spaltbreite 31. Wird das Öl 15 dünnflüssiger oder sinkt die Drehzahl, so wird das Innenelement 9 durch das im Spalt 30 strömende Öl 15 von der Innenwand des Aufnahmesegments 33 weniger stark gegen die Federkraft des federnden Drahtbügels 32 weg gedrückt, und die Spaltbreite 31 verringert sich entsprechend.In concrete terms, an automatic adjustment is even provided in the embodiment shown. According to 3 For this purpose, the fixing means is designed as a spring element in the form of a resilient wire clip 32, with which the inner element 9 is essentially non-rotatably connected to the stator 21. Slight twisting angles of the inner element 9, which due to the elasticity of the springy wire clip 32 may arise can be tolerated. In any case, the resilient wire clip 32 causes the inner element 9 to be pressed to a certain extent in the direction of the receiving segment 33 , which tends to lead to a reduction in the gap width 31 . This is counteracted by a certain pressure of the oil 15 in the gap 30, which pressure depends on various factors. For example, the inner element 9 is pushed away from the inner wall 34 of the receiving segment 33 against the spring force of the resilient wire bracket 32, the stronger the more viscous the oil 15 is or the higher the speed, and the larger the gap width 31 remains. If the oil 15 becomes thinner or if the speed drops, the inner element 9 is pressed away less strongly from the inner wall of the receiving segment 33 against the spring force of the resilient wire clip 32 by the oil 15 flowing in the gap 30, and the gap width 31 is reduced accordingly.

BEZUGSZEICHENLISTEREFERENCE LIST

11
Schmiermittelaufnahmelubricant intake
22
Kurbelwellecrankshaft
33
Kältemittelkompressorrefrigerant compressor
44
Hülsenelementsleeve element
55
Lichter Querschnitt des HülsenelementsClear cross-section of the sleeve element
66
Längsachse des HülsenelementsLongitudinal axis of the sleeve element
77
Oberes Ende des HülsenelementsUpper end of the sleeve element
88th
Unteres Ende des HülsenelementsLower end of the sleeve element
99
Innenelementinterior element
1010
Mantelfläche des InnenelementsLateral surface of the inner element
1111
Längsachse des InnenelementsLongitudinal axis of the inner element
1212
Unteres Ende der MantelflächeLower end of the lateral surface
1313
Oberes Ende der MantelflächeUpper end of the lateral surface
1414
Rillegroove
1515
Öloil
1616
Öseeyelet
1818
Kompressorgehäusecompressor housing
1919
Elektrische AntriebseinheitElectric drive unit
2020
Rotorrotor
2121
Statorstator
2222
Kolben-Zylinder-EinheitPiston-cylinder unit
2323
KolbenPistons
2424
Zylindercylinder
2525
Bodenbereichfloor area
2626
Schmiermittelsumpflubricant sump
2727
Bohrung der Kurbelwellebore of the crankshaft
2828
Austrittsbohrungexit hole
2929
Drehachse der KurbelwelleAxis of rotation of the crankshaft
3030
Spaltgap
3131
Spaltbreitegap width
3232
Federnder DrahtbügelSpringy wire hanger
3333
Aufnahmesegment des lichten QuerschnittsRecording segment of the clear cross-section
3434
Innenwandinner wall
Θ1Θ1
Erster ÖffnungswinkelFirst opening angle
Θ2Θ2
Zweiter ÖffnungswinkelSecond opening angle

Claims (11)

  1. Lubricant holder (1) for vertical conveying of lubricant (15) by means of a crankshaft (2) of a coolant compressor (3), comprising a sleeve element (4) having a clear cross-section (5) delimited by an inside wall (34), which clear cross-section extends along a longitudinal axis (6) of the sleeve element (4), from an upper end (7) to a lower end (8) of the sleeve element (4), the lubricant holder (1) furthermore comprising an inner element (9) that has a mantle surface (10) that extends along a longitudinal axis (11) of the inner element (9), from a lower end (12) to an upper end (13), wherein in an operating state of the lubricant holder (1)
    - the inner element (9) is arranged within the clear cross-section (5) of the sleeve element (4) with its mantle surface (10), at least in certain areas,
    - viewed in the direction from the lower end (8) to the upper end (7) of the sleeve element (4), the lower end (12) of the mantle surface (10) is disposed in front of its upper end (13), and
    - the inner element (9) and the sleeve element (4) can be rotated relative to one another about the longitudinal axis (6) of the sleeve element (4) and/or the longitudinal axis (11) of the inner element (9), wherein the clear cross-section (5) narrows from the lower end (8) to the upper end (7) of the sleeve element (4), at least in a holding segment (33) intended for holding the inner element (9), wherein the inner element (9) narrows in the region of the mantle surface (10), from the lower end (12) to the upper end (13) of the mantle surface (10), and wherein the inside wall (34) and/or the mantle surface (10) has/have at least one groove (14) that runs in spiral shape, characterised in that the at least one groove (14) has a varying angle of inclination, which preferably increases from the lower end (12) to the upper end (13) of the mantle surface (10).
  2. Lubricant holder (1) according to claim 1, characterised in that the clear cross-section (5) of the sleeve element (4) is configured in the form of a truncated cone, at least in its holding segment (33).
  3. Lubricant holder (1) according to one of claims 1 to 2, characterised in that the mantle surface (10) of the inner element (9) is configured as the mantle surface of a truncated cone.
  4. Lubricant holder (1) according to claim 3 and to claim 2, characterised in that the truncated-cone shape of the holding segment (33) of the clear cross-section (5) is based on a cone having a first opening angle (Θ1),
    that a truncated-cone shape according to which the mantle surface (10) is configured is based on a cone having a second opening angle (Θ2),
    and that the absolute difference between the first opening angle (Θ1) and the second opening angle (Θ2) is less than or equal to 10°, preferably less than or equal to 5°, particularly preferably equal to 0°.
  5. Lubricant holder (1) according to one of claims 1 to 4, characterised in that the inner element (9) has at least one projecting wing and/or a fastening element, preferably an eye (16), for a fixation means, in the region of the lower end (12) of the mantle surface (10).
  6. Lubricant holder (1) according to one of claims 1 to 5, characterised in that the inner element (9) is produced from a material, preferably a plastic, having a density that is less than the density of the lubricant (15).
  7. Coolant compressor (3) having a compressor housing (18) that can be hermetically encapsulated, an electrical drive unit (19) arranged in a housing interior of the compressor housing (18), comprising a rotor (20) and a stator (21), a crankshaft (2) connected with the rotor (20) in torque-proof manner, as well as a piston/cylinder unit (22) arranged in the housing interior, which piston/cylinder unit comprises a piston (23) movably mounted in a cylinder (24) of the piston/cylinder unit (22), which piston can be driven by the crankshaft (2) for compression of coolant, wherein the coolant compressor (3) has a lubricant holder (1) according to one of claims 1 to 6 that is in the operating state, so as to convey lubricant (15) out of a lubricant sump (26) formed in a bottom region (25) of the compressor housing (18), by way of the crankshaft (2).
  8. Coolant compressor (3) according to claim 7, characterised in that the sleeve element (4) of the lubricant holder (1) is connected with the crankshaft (2) in torque-proof manner.
  9. Coolant compressor (3) according to one of claims 7 to 8, characterised in that the crankshaft (2) has a bore (27), which bore preferably runs at a slant to an axis of rotation (29) of the crankshaft (2) at least in certain areas, which bore stands in a fluidic connection with the clear cross-section (5) of the sleeve element (4), wherein the inner element (9) projects into the bore (27) .
  10. Coolant compressor (3) according to one of claims 7 to 9, characterised in that the inner element (9) can be moved with reference to the longitudinal axis (6) of the sleeve element (4).
  11. Coolant compressor (3) according to one of claims 7 to 10, characterised in that a fixation means configured as a spring element, preferably in the form of a resilient wire bracket (32), is provided, with which the inner element (9) is connected with the stator (21) or other components of the coolant compressor (3), essentially in torque-proof manner.
EP18197570.7A 2018-09-28 2018-09-28 Lubricant holder for a refrigerant compressor Active EP3628866B1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP18197570.7A EP3628866B1 (en) 2018-09-28 2018-09-28 Lubricant holder for a refrigerant compressor
PCT/EP2019/076159 WO2020064998A1 (en) 2018-09-28 2019-09-27 Lubricant receptacle for a refrigerant compressor
CN201980063273.1A CN112752904B (en) 2018-09-28 2019-09-27 Lubricant extraction device for refrigerant compressor
US17/276,532 US11225957B2 (en) 2018-09-28 2019-09-27 Lubricant receptacle for a refrigerant compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18197570.7A EP3628866B1 (en) 2018-09-28 2018-09-28 Lubricant holder for a refrigerant compressor

Publications (2)

Publication Number Publication Date
EP3628866A1 EP3628866A1 (en) 2020-04-01
EP3628866B1 true EP3628866B1 (en) 2022-03-02

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EP18197570.7A Active EP3628866B1 (en) 2018-09-28 2018-09-28 Lubricant holder for a refrigerant compressor

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US (1) US11225957B2 (en)
EP (1) EP3628866B1 (en)
CN (1) CN112752904B (en)
WO (1) WO2020064998A1 (en)

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IT245317Y1 (en) * 1998-07-01 2002-03-20 Zanussi Elettromecc PERFECTED HERMETIC MOTOR-COMPRESSOR GROUP
KR100395957B1 (en) * 2001-05-18 2003-08-27 주식회사 엘지이아이 Oil Pumping apparatus for hermetic compressor
KR100395956B1 (en) * 2001-05-18 2003-08-27 주식회사 엘지이아이 Oil Pumping apparatus for hermetic compressor
KR100422367B1 (en) * 2001-07-14 2004-03-12 삼성광주전자 주식회사 Oil pickup apparatus for Hermetic compressor
EP1605163A1 (en) 2003-03-14 2005-12-14 Matsushita Electric Industrial Co., Ltd. Compressor
BRPI0604908A (en) * 2006-10-31 2008-07-01 Whirlpool Sa refrigeration compressor oil pump
BRPI0705336A2 (en) * 2007-10-31 2009-06-23 Whirlpool Sa fixing arrangement of an oil pump on a refrigeration compressor
CN201810523U (en) * 2010-09-27 2011-04-27 加西贝拉压缩机有限公司 Oil pumping structure applied to hermetically sealed compressor
EP2638289B1 (en) * 2010-11-11 2017-06-28 Arçelik Anonim Sirketi A hermetic compressor the lubrication performance of which is improved
CN104454458A (en) * 2014-12-02 2015-03-25 华意压缩机(荆州)有限公司 Internal spiral groove oil suction pipe for variable-frequency refrigerator compressor
CN106979140B (en) * 2016-01-19 2021-04-06 恩布拉科压缩机工业和制冷解决方案有限公司 Variable speed cooling compressor including a lubrication oil pumping system
JP6628815B2 (en) * 2016-02-02 2020-01-15 三菱電機株式会社 Refrigerant compression device and refrigeration device
AT15828U1 (en) 2016-12-27 2018-07-15 Secop Gmbh LUBRICANT CONSUMPTION FOR A REFRIGERANT COMPRESSOR AND REFRIGERANT COMPRESSOR

Also Published As

Publication number Publication date
CN112752904A (en) 2021-05-04
US20210310471A1 (en) 2021-10-07
EP3628866A1 (en) 2020-04-01
US11225957B2 (en) 2022-01-18
WO2020064998A1 (en) 2020-04-02
CN112752904B (en) 2022-09-06

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