EP3628866B1 - Logement de lubrifiant pour un compresseur de réfrigérant - Google Patents

Logement de lubrifiant pour un compresseur de réfrigérant 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
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German (de)
English (en)
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EP3628866A1 (fr
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/fr
Priority to CN201980063273.1A priority patent/CN112752904B/zh
Priority to US17/276,532 priority patent/US11225957B2/en
Priority to PCT/EP2019/076159 priority patent/WO2020064998A1/fr
Publication of EP3628866A1 publication Critical patent/EP3628866A1/fr
Application granted granted Critical
Publication of EP3628866B1 publication Critical patent/EP3628866B1/fr
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)

Claims (11)

  1. Réceptacle à lubrifiant (1) pour l'acheminement vertical de lubrifiant (15) au moyen d'un vilebrequin (2) d'un compresseur de réfrigérant (3), comprenant un élément de manchon (4) avec une section libre (5) délimitée par une paroi intérieure (34), qui s'étend le long d'un axe longitudinal (6) de l'élément de manchon (4) d'une extrémité supérieure (7) à une extrémité inférieure (8) de l'élément de manchon (4), lequel réceptacle à lubrifiant (1) comprend en outre un élément intérieur (9) qui présente une surface d'enveloppe (10) s'étendant le long d'un axe longitudinal (11) de l'élément intérieur (9) d'une extrémité inférieure (12) à une extrémité supérieure (13), dans lequel, dans un état de fonctionnement du réceptacle à lubrifiant (1),
    - l'élément intérieur (9) est disposée avec sa surface d'enveloppe (10) au moins en partie à l'intérieur de la section libre (5) de l'élément de manchon (4),
    - vu dans la direction de l'extrémité inférieure (8) vers l'extrémité supérieure (9) de l'élément de manchon (4), l'extrémité inférieure (12) de la surface d'enveloppe (10) est disposée devant son extrémité supérieure (13) et
    - l'élément intérieur (9) et l'élément de manchon (4) sont capables de rotation l'un par rapport à l'autre autour de l'axe longitudinal (6) de l'élément de manchon (4) et/ou de l'axe longitudinal (11) de l'élément intérieur (9), la section libre (5) se resserrant de l'extrémité inférieure (8) vers l'extrémité supérieure (7) de l'élément de manchon (4) au moins dans un segment de réception (33) destiné à recevoir l'élément intérieur (9), et l'élément intérieur (9) se resserrant au niveau de la surface d'enveloppe (10) de l'extrémité inférieure (12) à l'extrémité supérieure (13) de la surface d'enveloppe (10) et la paroi intérieure (34) et/ou la surface d'enveloppe (10) présentant au moins une rainure (14) en spirale,
    caractérisé en ce que l'au moins une rainure (14) présente un angle de pente variable, qui augmente de préférence de l'extrémité inférieure (12) vers l'extrémité supérieure (13) de la surface d'enveloppe (10).
  2. Réceptacle à lubrifiant (1) selon la revendication 1, caractérisé en ce que la section libre (5) de l'élément de manchon (4) est en forme de tronc de cône au moins dans son segment de réception (33).
  3. Réceptacle à lubrifiant (1) selon l'une des revendications 1 à 2, caractérisé en ce que la surface d'enveloppe (10) de l'élément intérieur (9) est conformée comme la surface d'enveloppe d'un tronc de cône.
  4. Réceptacle à lubrifiant (1) selon les revendications 3 et 2, caractérisé en ce que la forme tronconique du segment de réception (33) de la section libre (5) définit un cône ayant un premier angle d'ouverture (Θ1),
    en ce que la forme tronconique donnée à la surface d'enveloppe (10) se base sur un cône ayant un deuxième angle d'ouverture (Θ2)
    et en ce que la différence absolue entre le premier angle d'ouverture (Θ1) et le deuxième angle d'ouverture (Θ2) est inférieure ou égale à 10°, de préférence inférieure ou égale à 5°, en particulier égale à 0°.
  5. Réceptacle à lubrifiant (1) selon l'une des revendications 1 à 4, caractérisé en ce que l'élément intérieur (9) présente au niveau de l'extrémité inférieure (12) de la surface d'enveloppe (10) au moins une ailette qui s'en écarte et/ou un élément de fixation, de préférence un œillet (16), pour un moyen de fixation.
  6. Réceptacle à lubrifiant (1) selon l'une des revendications 1 à 5, caractérisé en ce que l'élément intérieur (9) est fait d'un matériau, de préférence d'un matière plastique, dont la masse volumique est inférieure à celle du lubrifiant (15).
  7. Compresseur de réfrigérant (3) avec un carter de compresseur (18) pouvant être encapsulé de façon hermétique, une unité d'entraînement électrique (19) disposée à l'intérieur du carter de compresseur (18) et comprenant un rotor (20) et un stator (21), un vilebrequin (2) relié de façon solidaire en rotation au rotor (20) et avec une unité de piston et cylindre (22) disposée à l'intérieur du carter, comprenant un piston (23) supporté avec possibilité de mouvement dans un cylindre (24) de l'unité de piston et cylindre (22) qui peut être entraîné par le vilebrequin (2) pour comprimer du réfrigérant,
    lequel compresseur de réfrigérant (3) comprend un réceptacle à lubrifiant (1) selon l'une des revendications 1 à 6 qui se trouve dans l'état de fonctionnement pour acheminer du lubrifiant (15) à partir d'un bac à lubrifiant (26) formé dans une partie de fond (25) du carter de compresseur (18) à l'aide du vilebrequin (2).
  8. Compresseur de réfrigérant (3) selon la revendication 7, caractérisé en ce que l'élément de manchon (4) du réceptacle à lubrifiant (1) est relié de façon solidaire en rotation au vilebrequin (2).
  9. Compresseur de réfrigérant (3) selon l'une des revendications 7 à 8, caractérisé en ce que le vilebrequin (2) présente un alésage (27), de préférence oblique au moins par sections par rapport à un axe de rotation (29) du vilebrequin (2), qui est en liaison fluidique avec la section libre (5) de l'élément de manchon (4), l'élément intérieur (9) dépassant dans l'alésage (27).
  10. Compresseur de réfrigérant (3) selon l'une des revendications 7 à 9, caractérisé en ce que l'élément intérieur (9) peut être déplacé par rapport à l'axe longitudinal (6) de l'élément de manchon (4).
  11. Compresseur de réfrigérant (3) selon l'une des revendications 7 à 10, caractérisé en ce qu'il est prévu un élément de fixation conformé comme un élément de ressort, de préférence formé par un étrier de fil formant ressort (32), avec lequel l'élément intérieur (9) est relié de façon sensiblement solidaire en rotation avec le stator (21) ou avec d'autres pièces du compresseur de réfrigérant (3).
EP18197570.7A 2018-09-28 2018-09-28 Logement de lubrifiant pour un compresseur de réfrigérant Active EP3628866B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP18197570.7A EP3628866B1 (fr) 2018-09-28 2018-09-28 Logement de lubrifiant pour un compresseur de réfrigérant
CN201980063273.1A CN112752904B (zh) 2018-09-28 2019-09-27 用于制冷剂压缩机的润滑剂提取装置
US17/276,532 US11225957B2 (en) 2018-09-28 2019-09-27 Lubricant receptacle for a refrigerant compressor
PCT/EP2019/076159 WO2020064998A1 (fr) 2018-09-28 2019-09-27 Réception de lubrifiant pour un compresseur de réfrigérant

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18197570.7A EP3628866B1 (fr) 2018-09-28 2018-09-28 Logement de lubrifiant pour un compresseur de réfrigérant

Publications (2)

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

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EP18197570.7A Active EP3628866B1 (fr) 2018-09-28 2018-09-28 Logement de lubrifiant pour un compresseur de réfrigérant

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EP (1) EP3628866B1 (fr)
CN (1) CN112752904B (fr)
WO (1) WO2020064998A1 (fr)

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT245317Y1 (it) * 1998-07-01 2002-03-20 Zanussi Elettromecc Gruppo motocompressore ermetico perfezionato
KR100395957B1 (ko) * 2001-05-18 2003-08-27 주식회사 엘지이아이 밀폐형 압축기의 오일펌핑장치
KR100395956B1 (ko) * 2001-05-18 2003-08-27 주식회사 엘지이아이 밀폐형 압축기의 오일펌핑장치
KR100422367B1 (ko) * 2001-07-14 2004-03-12 삼성광주전자 주식회사 밀폐형 압축기의 오일 픽업장치
KR100679130B1 (ko) * 2003-03-14 2007-02-07 마쯔시다덴기산교 가부시키가이샤 압축기
BRPI0604908A (pt) * 2006-10-31 2008-07-01 Whirlpool Sa bomba de óleo para compressor de refrigeração
BRPI0705336A2 (pt) * 2007-10-31 2009-06-23 Whirlpool Sa arranjo de fixação de uma bomba de óleo em um compressor de refrigeração
CN201810523U (zh) * 2010-09-27 2011-04-27 加西贝拉压缩机有限公司 应用于全封闭制冷压缩机的泵油结构
WO2012062860A1 (fr) * 2010-11-11 2012-05-18 Arcelik Anonim Sirketi Compresseur hermétique dont les performances de lubrification sont améliorées
CN104454458A (zh) * 2014-12-02 2015-03-25 华意压缩机(荆州)有限公司 一种用于变频冰箱压缩机的内螺旋槽吸油管
CN106979140B (zh) * 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 包括润滑油泵送***的变速冷却压缩机
WO2017134742A1 (fr) * 2016-02-02 2017-08-10 三菱電機株式会社 Dispositif de compression de réfrigérant et dispositif de réfrigération
AT15828U1 (de) 2016-12-27 2018-07-15 Secop Gmbh Schmiermittelaufnahme für einen kältemittelkompressor und kältemittelkompressor

Also Published As

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

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