WO2018216654A1 - 密閉型冷媒圧縮機および冷凍装置 - Google Patents
密閉型冷媒圧縮機および冷凍装置 Download PDFInfo
- Publication number
- WO2018216654A1 WO2018216654A1 PCT/JP2018/019478 JP2018019478W WO2018216654A1 WO 2018216654 A1 WO2018216654 A1 WO 2018216654A1 JP 2018019478 W JP2018019478 W JP 2018019478W WO 2018216654 A1 WO2018216654 A1 WO 2018216654A1
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- WIPO (PCT)
- Prior art keywords
- shaft portion
- rotor
- main shaft
- oil supply
- balance
- Prior art date
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Classifications
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- 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
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- 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
- F04B39/0094—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 crankshaft
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- 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
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- 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
- F04B39/0284—Constructional details, e.g. reservoirs in the casing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
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- 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
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/122—Cylinder block
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/13—Vibrations
Definitions
- the present invention relates to a so-called reciprocating hermetic refrigerant compressor that compresses refrigerant by reciprocating a piston in a cylinder, and a refrigeration apparatus including the hermetic refrigerant compressor.
- a so-called reciprocating refrigerant compressor has a configuration in which an electric element and a compression element are accommodated in a sealed container, and lubricating oil is also enclosed in the sealed container. Lubricating oil is stored in the lower part of the sealed container.
- the compression element includes a cylinder and a piston. When the vertical direction of the hermetic container is a vertical direction, the cylinder and the piston are arranged in a horizontal direction (a direction perpendicular to the vertical direction). The compression element compresses the refrigerant by reciprocating the piston in the cylinder by the electric element.
- Such reciprocating refrigerant compressors have conventionally been required to reduce vibration, but in recent years, further reduction in vibration and further downsizing are also required.
- the compression element since the compression element includes the cylinder and the piston arranged in the lateral direction as described above, load imbalance (unbalance) tends to occur in the lateral direction due to the reciprocating motion of the piston. This load imbalance is one of the major factors causing the vibration of the refrigerant compressor.
- the compression element includes a crankshaft in which a main shaft portion is supported by a bearing portion of a cylinder block. Therefore, a method of attaching a balance weight to the crankshaft is known.
- the electric element includes a stator and a rotor, and among these, a method of attaching a balance weight to the upper surface or the lower surface of the rotor is known.
- Patent Document 1 discloses an end in which a balance weight is fixed to an eccentric shaft portion of a crankshaft, and a weight portion made of a rolled material partially having a right-angled bending portion is integrated with an end face of a rotor of an electric element.
- a configuration in which a plate is provided is disclosed. According to this configuration, the load imbalance can be alleviated by the balance weight and the weight portion, and the weight portion is integrated with the end plate, thereby improving the assembly workability and preventing the number of parts from increasing.
- the crankshaft is provided with an oil supply mechanism in addition to the main shaft portion and the eccentric shaft portion. Since the main shaft portion and the bearing portion, or the eccentric shaft portion and the connecting means (connecting rod) form a sliding portion with each other, the oil supply mechanism removes the lubricating oil stored below in the sealed container. Supply to lubricate.
- a typical oil supply mechanism as disclosed in Patent Document 2, for example, there is a configuration including a first oil supply passage, an oil supply groove, a second oil supply passage, and the like.
- the first oil supply passage is a hole provided so as to extend upward from the lower end portion of the main shaft portion, and is inclined with respect to the shaft center (rotational axis center) of the main shaft portion.
- the upper end of the first oil supply passage communicates with a spiral oil supply groove formed on the outer surface of the main shaft portion.
- the second oil supply passage is provided from the main shaft portion to the eccentric shaft portion, and communicates with the oil supply groove.
- the lubricating oil stored in the sealed container is sucked into the first oil supply passage by centrifugal force generated by the rotation of the crankshaft, supplied to the oil supply groove, and further supplied from the oil supply groove to the second oil supply passage.
- the lubricating oil supplied to the oil supply groove lubricates the sliding portion constituted by the main shaft portion and the bearing portion, and the lubricating oil supplied to the second oil supply passage slides constituted by the connecting means and the eccentric shaft portion. Lubricate the part.
- the first oil supply passage is provided as an inclined hole in the main shaft portion, so that the lubricating oil can be easily sucked up by the centrifugal force generated by the rotation of the crankshaft.
- the present invention has been made to solve such a problem, and is a reciprocating hermetic refrigerant compressor capable of relieving the load imbalance of the main shaft portion and realizing further lower vibration.
- the purpose is to provide.
- a hermetic refrigerant compressor according to the present invention is enclosed in a sealed container in which lubricating oil is enclosed and the lubricating oil is stored below, and is accommodated in the sealed container.
- the electric element has a stator and the main shaft portion fixed.
- a balance adjusting means for adjusting an unbalance of a load caused by at least the structure of the main shaft portion.
- the load imbalance generated in the main shaft portion due to the structure of the main shaft portion of the crankshaft itself is not adjusted in the main shaft portion or the crankshaft, but on the rotor fixed to the main shaft portion. Adjustment is made by providing a balance adjusting means. Since the rotor has a cylindrical shape or a column shape extending in a direction orthogonal to the axial direction of the crankshaft, it is easier to provide a balance adjusting means than the elongated crankshaft or main shaft portion, and the balance adjustment. It is also possible to finely adjust the position where the means is provided. Thereby, when viewed as the whole compressor main body, it is possible to satisfactorily relax (reduce or cancel) the unbalance of the load on the main shaft portion. As a result, it is possible to further reduce the vibration of the hermetic refrigerant compressor.
- the present invention also includes a refrigeration apparatus including the hermetic refrigerant compressor having the above-described configuration. Accordingly, it is possible to provide a hermetic refrigerant compressor capable of realizing further vibration reduction.
- FIG. 4 is a schematic diagram for explaining positions of balance holes as an example of balance adjusting means provided in the rotor shown in FIGS. 3A to 3C. It is a typical side view which shows an example of the gravity center position in the crankshaft shown in FIG.
- FIG. 10 It is a typical side view which shows the other example of the gravity center position in the crankshaft shown in FIG. It is a schematic diagram explaining the preferable position of the balance hole provided in the rotor fixed to the crankshaft shown in FIG. 10 and FIG. 13A and 13B are schematic views showing another example of the rotor and balance adjusting means shown in FIGS. 3A to 3C. It is sectional drawing which shows one structural example of the hermetic refrigerant compressor which concerns on Embodiment 2 of this indication. 15A to 15C are diagrams showing other examples of the electric element provided in the hermetic refrigerant compressor shown in FIG. It is a schematic diagram which shows one structural example of the article
- a hermetic refrigerant compressor includes a hermetic container in which lubricating oil is enclosed and the lubricating oil is stored below, an electric element housed in the hermetic container, and the hermetic container.
- a compression element that is housed and driven by the electric element, and the compression element is disposed in the hermetic container along a direction intersecting the vertical direction with a crankshaft including a main shaft portion and an eccentric shaft portion.
- a piston coupled to the eccentric shaft portion and reciprocating in the cylinder, the electric element includes a stator and a rotor to which the main shaft portion is fixed, and The rotor is configured to be provided with balance adjusting means for adjusting load unbalance caused by at least the structure of the main shaft portion.
- the load imbalance generated in the main shaft portion due to the structure of the main shaft portion of the crankshaft itself is not adjusted in the main shaft portion or the crankshaft, but on the rotor fixed to the main shaft portion. Adjustment is made by providing a balance adjusting means. Since the rotor has a cylindrical shape or a column shape extending in a direction orthogonal to the axial direction of the crankshaft, it is easier to provide a balance adjusting means than the elongated crankshaft or main shaft portion, and the balance adjustment. It is also possible to finely adjust the position where the means is provided. Thereby, when viewed as the whole compressor main body, it is possible to satisfactorily relax (reduce or cancel) the unbalance of the load on the main shaft portion. As a result, it is possible to further reduce the vibration of the hermetic refrigerant compressor.
- the balance adjusting means may be at least one of a balance hole and a balance weight provided in the rotor.
- the balance adjusting means uses the balance hole for adjusting the balance by partially reducing the weight of the rotor or the balance weight for adjusting the balance by partially increasing the weight of the rotor. It will be. Therefore, it is possible to more favorably ease the load imbalance of the main shaft portion.
- the compression element further includes a bearing portion that pivotally supports the main shaft portion
- the crankshaft further includes an oil supply mechanism.
- the oil supply mechanism includes The balance adjustment is included when an oil supply passage communicating with the lower end surface of the main shaft portion is included, the center of gravity of the oil supply passage is deviated from the axis of the main shaft portion, and the balance adjusting means is the balance hole.
- the means is provided in a semi-cylindrical region of the rotor that is located on the opposite side of the axis of the main shaft portion as viewed from the center of gravity of the oil supply passage. There may be.
- the position where the balance adjusting means is provided in the rotor is specified as a region (semi-cylindrical region) on the opposite side of the center of gravity of the oil supply passage with respect to the axis of the main shaft.
- a radial line extending from the rotation axis of the rotor through the center of gravity of the eccentric shaft portion is defined as a 0 ° reference line, and the center of gravity of the oil supply passage
- the balance adjusting means is within a range of 5 to 175 ° when viewed from the reference line in the semi-cylindrical region of the rotor.
- region may be sufficient.
- the position where the balance adjusting means is provided in the rotor is specified as a further fan-shaped columnar region from within the semi-columnar region.
- the balance adjusting means includes a sectoral columnar region that is within a range of 5 to 40 ° when viewed from the reference line in the semicylindrical region of the rotor, Also, it may be configured to be provided in at least one of the sectoral columnar regions within the range of 140 to 175 °.
- the position where the balance adjusting means is provided in the rotor is specified as at least one of the two sectoral columnar regions further limited from the sectoral columnar region. As a result, it is possible to further favorably relax the load imbalance of the main shaft portion.
- the balance hole may be provided in an iron core of the rotor.
- the balance hole is provided in the iron core of the rotor, the balance hole with a simpler configuration can be provided with a good degree of freedom according to the load unbalance situation. Thereby, the balance of the load of a rotor can be adjusted favorably.
- the balance hole may be configured to extend along the rotation axis direction of the rotor.
- the load balance of the rotor can be adjusted well.
- the balance hole may be a blind hole or a through hole having a bottom surface.
- the balance of the load is adjusted by adjusting the depth of the balance hole, the balance of the load of the rotor can be adjusted favorably.
- the balance adjusting unit adjusts the load imbalance caused by the reciprocating motion of the piston in addition to the load imbalance caused by the structure of the main shaft portion. It may be.
- the semi-cylindrical region or the sector columnar region is preferably used so as to adjust the load imbalance caused by the reciprocating motion of the piston. It is only necessary to provide a balance adjusting means at the position. Thereby, it is possible to satisfactorily relieve the load imbalance of the whole hermetic refrigerant compressor.
- the present disclosure also includes a refrigeration apparatus including the hermetic refrigerant compressor having the above-described configuration. Accordingly, it is possible to provide a hermetic refrigerant compressor capable of realizing further vibration reduction.
- the hermetic refrigerant compressor 10A includes an electric element 20A and a compression element 30 that are accommodated in the hermetic container 11, and the inside of the hermetic container 11 includes Refrigerant gas and lubricating oil 13 are enclosed.
- the electric element 20 ⁇ / b> A and the compression element 30 constitute the compressor body 12.
- the compressor body 12 is disposed in the sealed container 11 in a state where it is elastically supported by a suspension spring 14 provided at the bottom of the sealed container 11.
- the closed container 11 is provided with a suction pipe 15 and a discharge pipe 16.
- One end of the suction pipe 15 communicates with the internal space of the sealed container 11 and the other end is connected to a refrigeration apparatus (not shown) to constitute a refrigeration cycle such as a refrigerant circuit.
- the discharge pipe 16 has one end connected to the compression element 30 and the other end connected to the refrigeration apparatus. As will be described later, the refrigerant gas compressed by the compression element 30 is led to the refrigerant circuit via the discharge pipe 16, and the refrigerant gas from the refrigerant circuit is led to the internal space of the sealed container 11 via the suction pipe 15. .
- the specific structure of the airtight container 11 is not specifically limited, In this Embodiment, it is formed by drawing of an iron plate, for example.
- the refrigerant gas enclosed in the hermetic container 11 is enclosed in a refrigerant circuit to which the hermetic refrigerant compressor 10A is applied at a relatively low temperature at a pressure equivalent to that on the low pressure side.
- the lubricating oil 13 is enclosed in the sealed container 11 and lubricates a crankshaft 40 (described later) provided in the compression element 30. As shown in FIG. 1, the lubricating oil 13 is stored in the bottom portion of the sealed container 11.
- the kind of refrigerant gas is not specifically limited, Gas well-known in the field
- R600a that is a hydrocarbon-based refrigerant gas is preferably used.
- R600a has a relatively low global warming potential and is one of refrigerant gases that are preferably used from the viewpoint of protecting the global environment.
- the type of the lubricating oil 13 is not specifically limited, and those known in the field of the compressor can be suitably used.
- the electric element 20A includes at least a stator (stator) 21A and a rotor (rotor) 22A.
- the stator 21A is fixed by a fastener such as a bolt (not shown) below a cylinder block 31 (described later) included in the compression element 30, and the rotor 22A is coaxial with the stator 21A inside the stator 21A. Is arranged.
- the rotor 22A fixes a main shaft portion 41 of a crankshaft 40 (described later) included in the compression element 30 by, for example, shrink fitting.
- the stator 21A has a plurality of windings (not shown), and the rotor 22A has a plurality of permanent magnets (not shown) so as to face the plurality of windings.
- a permanent magnet is embedded in an iron core that is a main body of the rotor 22A. Therefore, the electric element 20A is an IPM (Interior Permanent Magnet Motor) type motor.
- IPM Interior Permanent Magnet Motor
- the electric element 20A in the present embodiment is an inner rotor type motor.
- the rotor 22A rotates at an axis Z1 along the vertical direction indicated by a one-dot chain line in the figure.
- the lower surface of the rotor 22A faces the oil surface of the lubricating oil 13, and the upper surface of the rotor 22A faces a bearing portion 35 that is a part of a cylinder block 31 (described later).
- the rotor 22A is provided with a balance hole 27 as a balance adjusting means. A specific configuration of the rotor 22A including the balance hole 27 will be described later.
- the electric element 20A including the stator 21A and the rotor 22A is connected to an external inverter drive circuit (not shown) and is inverter-driven at a plurality of operating frequencies.
- the compression element 30 is driven by the electric element 20A and compresses the refrigerant gas.
- the compression element 30 is accommodated in the airtight container 11 so that it may be located above the electric element 20A.
- the compression element 30 includes a cylinder block 31, a cylinder 32, a piston 33, a compression chamber 34, a bearing portion 35, a crankshaft 40, a thrust bearing 36, a valve plate 37, a cylinder head 38, and a suction muffler. 39 etc.
- the cylinder block 31 is provided with a cylinder 32 and a bearing portion 35.
- the cylinder 32 is disposed along a direction that intersects the vertical direction, and is fixed to the bearing portion 35.
- the vertical direction is the vertical direction
- the horizontal direction is the horizontal direction
- the cylinder 32 Are arranged along the lateral direction in the sealed container 11.
- the bearing portion 35 rotatably supports the main shaft portion 41 of the crankshaft 40, but the cylinder 32 is fixed to the bearing portion 35 so as to be unevenly distributed at a position on the outer side when viewed from the main shaft portion 41. .
- a substantially cylindrical bore having the same diameter as the piston 33 is formed, and the piston 33 is inserted into the cylinder 32 so as to be freely slidable.
- a compression chamber 34 is formed by the cylinder 32 and the piston 33, and the refrigerant gas is compressed therein.
- the bearing portion 35 rotatably supports the main shaft portion 41 of the crankshaft 40.
- the crankshaft 40 is supported in the sealed container 11 so that its axis is in the vertical direction.
- the main shaft portion 41, the eccentric shaft portion 42, the flange portion 43, the connecting rod 44, the oil supply A mechanism 50 or the like is provided.
- the main shaft portion 41 is fixed to the rotor 22A of the electric element 20A, and the eccentric shaft portion 42 is provided eccentric to the main shaft portion 41.
- the flange portion 43 integrally connects the main shaft portion 41 and the eccentric shaft portion 42.
- a thrust bearing 36 is provided between the flange portion 43 and the bearing portion 35.
- the bearing portion 35 provided in the cylinder block 31 supports the main shaft portion 41 of the crankshaft 40 so as to be rotatable. Therefore, the outer peripheral surface of the main shaft portion 41 and the inner peripheral surface of the bearing portion 35 are sliding surfaces.
- a thrust bearing 36 is provided on the upper surface of the bearing portion 35, and a flange portion 43 of the crankshaft 40 is in contact with the upper surface of the thrust bearing 36. When the main shaft portion 41 rotates, the flange portion 43 also rotates. The rotation of the flange portion 43 is also supported by the thrust bearing 36.
- the connecting rod 44 is a connecting portion (connecting means) that connects the eccentric shaft portion 42 of the crankshaft 40 and the piston 33, and the rotational movement of the crankshaft 40 is transmitted to the piston 33 by the connecting rod 44 as will be described later.
- the oil supply mechanism 50 is provided so as to communicate from the lower end of the main shaft portion 41 immersed in the lubricating oil 13 to the upper end of the eccentric shaft portion 42, and includes a crankshaft 40, a bearing portion 35, Lubricating oil 13 is supplied to the thrust bearing 36 and the like. A specific configuration example of the oil supply mechanism 50 will be described later.
- the piston 33 inserted into the cylinder 32 is connected to the connecting rod 44.
- the axis of the piston 33 is provided so as to intersect with the axial direction of the crankshaft 40.
- the crankshaft 40 is provided so that the axis is in the vertical direction, but the piston 33 is provided so that the axis is in the horizontal direction. Therefore, the axial direction of the piston 33 is a direction orthogonal to the axial direction of the crankshaft 40.
- the connecting rod 44 connects the piston 33 and the eccentric shaft portion 42 as described above. Since the flange portion 43 and the eccentric shaft portion 42 are rotated by the rotation of the main shaft portion 41, the rotational motion of the crankshaft 40 rotated by the electric element 20 ⁇ / b> A is transmitted to the piston 33 via the connecting rod 44. As a result, the piston 33 reciprocates within the cylinder 32.
- the piston 33 is inserted into one end (crankshaft 40 side) of the cylinder 32, but the other end (opposite side of the crankshaft 40) is formed by the valve plate 37 and the cylinder head 38. It is sealed.
- the valve plate 37 is located between the cylinder 32 and the cylinder head 38 and is provided with a suction valve and a discharge valve (not shown).
- a discharge space is formed inside the cylinder head 38, and the refrigerant gas from the compression chamber 34 is discharged into the discharge space of the cylinder head 38 when the discharge valve of the valve plate 37 is opened.
- the cylinder head 38 communicates with the suction pipe 15.
- the suction muffler 39 is positioned below the sealed container 11 when viewed from the cylinder 32 and the cylinder head 38.
- the suction muffler 39 has a sound deadening space inside. Since the suction muffler 39 communicates with the compression chamber 34 via the valve plate 37, the refrigerant gas in the suction muffler 39 is sucked into the compression chamber 34 when the suction valve of the valve plate 37 is opened.
- crankshaft 40 is balanced in order to reduce (reduce or cancel) the load imbalance (imbalance) caused by the reciprocating motion of the piston 33.
- a weight may be attached.
- a crank weight may be attached to the upper end of the crankshaft 40, that is, the upper end of the eccentric shaft portion 42, or a shaft weight may be attached to the flange portion 43.
- the oil supply mechanism 50 includes a first oil supply passage 51, a first series passage hole 52, an oil supply groove 53, an oil supply hole portion 54, a second oil supply passage 55, a second communication hole 56, and the like.
- the left side view shows that the axis Z1 of the main shaft portion 41 coincides with the axis Z2 of the eccentric shaft portion 42, and the eccentric shaft portion 42 is on the near side (main shaft portion).
- 41 is a side view of the crankshaft 40 as viewed from the back side (41), and the right side (right view) shows the axis Z1 of the main shaft portion 41 and the axis Z2 of the eccentric shaft portion 42 most. It is the side view which looked at the crankshaft 40 from the direction to separate.
- crankshaft 40 when the direction (longitudinal direction) in which the crankshaft 40 extends is the “vertical direction”, the direction in which the main shaft portion 41 and the eccentric shaft portion 42 are arranged in parallel is the “vertical direction” of the crankshaft 40. If the direction perpendicular to the vertical direction and in which the main shaft portion 41 and the eccentric shaft portion 42 can be viewed in parallel is defined as the “lateral direction” of the crankshaft 40, the left diagram of FIG. The “right side view” of FIG. 2 is the “lateral side view” of the crankshaft 40.
- FIG. 2 illustrates the crankshaft 40 from the side face in the vertical direction with the eccentric shaft portion 42 in front.
- front side the side with the eccentric shaft portion 42 in front in the vertical direction
- rear side the opposite side, that is, the side in front of the main shaft portion 41 in the vertical direction
- the lateral side view (right diagram) of FIG. 2 illustrates the crankshaft 40 from the side surface in which the eccentric shaft portion 42 is located on the left side and the main shaft portion 41 is located on the right side in the lateral direction.
- the side where the eccentric shaft portion 42 is located on the left side in the lateral direction is referred to as “front side”
- the opposite side that is, the side where the eccentric shaft portion 42 is located on the right side (the main shaft portion 41 is located on the left side) is referred to as “back side”.
- the flange portion 43 has a rear portion that extends in the lateral direction (front side and back side).
- the first oil supply passage 51 is provided inside the lower end of the main shaft portion 41, and is configured as a hole formed so as to extend upward from the end surface of the lower end of the main shaft portion 41.
- the first oil supply passage 51 is inclined with respect to the axis Z ⁇ b> 1 of the main shaft portion 41. That is, the first oil supply passage 51 is inclined so that the center line of the first oil supply passage 51 is laterally separated from the axis Z1 as it goes upward.
- the first oil supply passage 51 is inclined toward the front side (right side in the vertical side view), but is not limited thereto, and is on the back side (left side in the vertical side view). It may be inclined or not necessarily inclined.
- the first series of through holes 52 are located outside the main shaft portion 41 at the upper end of the first oil supply passage 51. It is provided so as to communicate with the side surface.
- the first series of through holes 52 are also connected to an oil supply groove 53 provided on the outer peripheral surface of the main shaft portion 41. Therefore, the first oil supply passage 51 and the oil supply groove 53 communicate with each other through the first series of through holes 52.
- the first series of through holes 52 communicate with the outer peripheral surface on the front side of the main shaft portion 41, but this is not limitative. Not.
- the oil supply groove 53 is a groove-like portion formed in a spiral shape on the outer peripheral surface of the main shaft portion 41 as shown in FIG.
- the lower end (one end) of the oil supply groove 53 communicates with the first oil supply passage 51 through the first series of holes 52 as described above.
- one end of the oil supply groove 53 (the end portion on the first series through hole 52 side) is an upstream end of the lubricating oil 13.
- the upper end portion (the other end) of the oil supply groove 53 reaches the outer peripheral surface of the upper end of the main shaft portion 41, in other words, the position adjacent to the lower surface of the flange portion 43 in the main shaft portion 41. Connected to. Therefore, the other end of the oil supply groove 53 (an end portion on the oil supply hole portion 54 side) is a downstream end of the lubricating oil 13.
- the oil supply groove 53 is formed in a spiral shape that is inclined with respect to the axis Z ⁇ b> 1 of the main shaft portion 41 so that the downstream side is upward when viewed from the upstream side of the lubricating oil 13. Therefore, in the vertical side view (left figure) of FIG. 2, the oil supply groove 53 located on the front outer peripheral surface which is the front side is indicated by a solid line, and the oil supply groove 53 located on the rear outer peripheral surface which is the opposite side is indicated by a broken line. This is shown in the figure. On the other hand, in the lateral side view (right view) of FIG.
- the oil supply groove 53 located on the outer peripheral surface on the front side that is the front side is shown, and the oil supply groove 53 located on the outer peripheral surface on the back side that is the opposite side is shown.
- the oil supply groove 53 is formed so as to wind the outer peripheral surface of the main shaft portion 41 about one and a half times (about 1.6 laps). It is not limited.
- the oil supply hole portion 54 is provided on the outer peripheral surface of the upper end of the main shaft portion 41 so as to be connected to the upper end portion of the oil supply groove 53 as described above.
- the second oil supply passage 55 communicates with the second oil supply passage 55.
- the oil supply hole portion 54 is formed as a recess having an opening on the outer surface of the main shaft portion 41, the opening side is connected to the oil supply groove 53, and the second oil supply passage 55 communicates with the upper side of the recess.
- the oil supply hole portion 54 is formed so as to open to the back side on the outer peripheral surface of the upper end of the main shaft portion 41, but is not limited thereto.
- the second oil supply passage 55 extends upward from the inside of the upper end of the main shaft portion 41 to the inside of the eccentric shaft portion 42 through the inside of the flange portion 43 as shown in a vertical side view (left diagram) of FIG. It is the tubular part formed in this way.
- the lower end of the second oil supply passage 55 communicates with the oil supply hole portion 54 as described above, and the upper end of the second oil supply passage 55 reaches the upper end of the eccentric shaft portion 42.
- the oil supply hole portion 54 is formed on the outer peripheral surface on the back side of the main shaft portion 41, so the second oil supply passage 55 is inclined from the back side to the front side (the same direction as the first oil supply passage 51).
- the present invention is not limited to this.
- the second communication hole 56 is provided so as to communicate with the outer peripheral surface of the eccentric shaft portion 42 from the side in the eccentric shaft portion 42 in the second oil supply passage 55.
- the second communication hole 56 is an outer peripheral surface that becomes the front side in the eccentric shaft portion 42.
- the present invention is not limited to this.
- the hermetic refrigerant compressor 10A having the above configuration will be specifically described together with the operation thereof.
- the hermetic refrigerant compressor 10 ⁇ / b> A includes the suction pipe 15 and the discharge pipe 16, and these are connected to a refrigeration apparatus having a known configuration, thereby The circuit is configured.
- the operation of the oil supply mechanism 50 at this time will be specifically described.
- the lubricating oil 13 stored at the bottom of the sealed container 11 is sucked into the first oil supply passage 51 by the centrifugal force generated by the rotation of the crankshaft 40.
- the lubricating oil 13 sucked into the first oil supply passage 51 is supplied to the upstream end of the oil supply groove 53 through the first series of through holes 52.
- the lubricating oil 13 supplied to the upstream end of the oil supply groove 53 by the rotation of the crankshaft 40 flows toward the upper end of the main shaft portion 41 along the oil supply groove 53 and is connected to the downstream end of the oil supply groove 53. Part 54 is reached.
- the oil supply groove 53 is formed in a spiral shape wound around the outer peripheral surface of the main shaft portion 41.
- the main shaft portion 41 is rotatably inserted into the bearing portion 35, and the outer peripheral surface of the main shaft portion 41 and the inner peripheral surface of the bearing portion 35 slide with the rotation of the crankshaft 40. Therefore, the lubricating oil 13 flowing through the oil supply groove 53 lubricates the sliding portion constituted by the main shaft portion 41 and the bearing portion 35.
- the oil supply hole 54 communicates with the second oil supply passage 55, the lubricating oil 13 that has reached the oil supply hole 54 is supplied to the second oil supply passage 55.
- the oil supply hole portion 54 communicates with the outer peripheral surface side, a part of the lubricating oil 13 reaching the oil supply hole portion 54 is supplied to the outer peripheral surface on the upper end side of the main shaft portion 41, Lubricate.
- a part of the lubricating oil 13 supplied to the outer peripheral surface on the upper end side of the main shaft portion 41 can be supplied to the lower surface of the upper flange portion 43 by a known configuration. Therefore, this part of the lubricating oil 13 can lubricate the thrust bearing 36 located between the flange portion 43 and the bearing portion 35.
- the lubricating oil 13 supplied to the second oil supply passage 55 flows through the second oil supply passage 55 and reaches the upper end of the eccentric shaft portion 42.
- a part of the lubricating oil 13 flowing through the second oil supply passage 55 is supplied to the connecting rod 44 from the second communication hole 56. Since the inner peripheral surface of the connecting rod 44 and the outer peripheral surface of the eccentric shaft portion 42 are sliding surfaces, a part of the lubricating oil 13 supplied from the second communication hole 56 is constituted by the connecting rod 44 and the eccentric shaft portion 42. Lubricate the sliding part.
- the lubricating oil 13 reaching the upper end of the eccentric shaft portion 42 is supplied to the cylinder 32 and the piston 33, and lubricates the sliding portion constituted by these.
- the suction, compression, and discharge of the refrigerant gas in the compression chamber 34 will be specifically described.
- the direction in which the volume of the compression chamber 34 increases is referred to as “increase direction” for convenience
- the direction in which the volume of the compression chamber 34 decreases is referred to as “decrease direction” for convenience.
- the low-temperature refrigerant gas returned from the refrigeration apparatus is once released from the suction pipe 15 to the internal space of the sealed container 11. Thereafter, the refrigerant gas is introduced into the sound deadening space in the suction muffler 39.
- the intake valve of the valve plate 37 since the intake valve of the valve plate 37 is starting to open, the introduced refrigerant gas flows into the compression chamber 34. Thereafter, when the piston 33 starts to move in a decreasing direction from the bottom dead center in the cylinder 32, the refrigerant gas in the compression chamber 34 is compressed, and the pressure in the compression chamber 34 increases. Further, the suction valve of the valve plate 37 is closed due to the difference between the pressure in the compression chamber 34 and the pressure in the suction muffler 39.
- a discharge valve (not shown) starts to open due to the difference between the pressure in the compression chamber 34 and the pressure in the cylinder head 38.
- the compressed refrigerant gas is discharged into the cylinder head 38 until the piston 33 reaches the top dead center in the cylinder 32.
- the refrigerant gas discharged into the cylinder head 38 is sent to the refrigeration apparatus via the discharge pipe 16.
- the refrigerant gas circulates in the refrigeration cycle.
- the specific driving method of the hermetic refrigerant compressor 10A that performs such an operation is not particularly limited.
- the hermetic refrigerant compressor 10A may be driven by simple on / off control, as described above, it is preferable that the hermetic refrigerant compressor 10A is inverter-driven by a plurality of operating frequencies. In the inverter drive, the operation control of the hermetic refrigerant compressor 10A can be optimized by decreasing or increasing the rotational speed of the electric element 20A.
- FIG. 1 a balance adjusting unit that is provided in the rotor 22A and adjusts an unbalance of a load caused by at least the structure of the main shaft portion 41 is shown in FIG. Details will be described with reference to FIGS. 3C and 4.
- FIG. 1 a balance adjusting unit that is provided in the rotor 22A and adjusts an unbalance of a load caused by at least the structure of the main shaft portion 41 is shown in FIG. Details will be described with reference to FIGS. 3C and 4.
- the hermetic refrigerant compressor 10A is provided with a balance hole 27 as a balance adjusting means for the rotor 22A included in the electric element 20A.
- the balance hole 27 may be a hole that is formed in the iron core that is the main body of the rotor 22A and extends along the rotation axis direction of the rotor 22A.
- the specific configuration of the balance hole 27 is not particularly limited.
- the balance hole 27 is configured as a blind hole having a bottom surface, but may be configured as a through-hole penetrating the rotor 22A (iron core of the main body).
- the balance adjusting means is not limited to the balance hole 27, and any means can be used as long as it can adjust at least the load unbalance caused by the structure of the main shaft portion 41.
- the rotor 22A according to the present embodiment is an IPM type as described above, a permanent magnet 23 is embedded in the iron core that is the main body of the rotor 22A as shown in FIGS. 3A to 3C. Therefore, in the example illustrated in FIGS. 3A and 3C, the balance hole 27 is provided in the iron core other than the portion where the permanent magnet 23 is embedded. In the present embodiment, as indicated by broken lines in FIGS. 3A and 3C, the entire permanent magnet 23 is embedded in the iron core. Therefore, the rotor 22A does not include a magnet protection member that covers the outer peripheral surface of the permanent magnet 23 (no magnet protection member is required).
- the rotor 22A has a shaft insertion hole 26 at the center thereof as shown in FIGS. 3A to 3C.
- the shaft insertion hole 26 can be inserted into the main shaft portion 41 of the crankshaft 40 and the lower end of the bearing portion 35 of the cylinder block 31. Therefore, the center line in the extending direction of the shaft insertion hole 26 is the rotation center of the rotor 22 ⁇ / b> A and is the axis Z ⁇ b> 1 of the main shaft portion 41 in the crankshaft 40.
- the axis Z1 is indicated by a cross mark
- FIG. 3B corresponding to the longitudinal sectional view, it is indicated by a dashed line.
- the shaft insertion hole 26 has a two-stage configuration in which the inner diameter differs between the upper part and the lower part. This is because a part of the bearing portion 35 in which the main shaft portion 41 is inserted is inserted at the upper portion of the shaft insertion hole 26 and only the main shaft portion 41 is inserted at the lower portion.
- the bearing portion 35 constitutes a lower portion of the cylinder block 31 and has a shape that extends in the entire lateral direction of the sealed container 11 in the present embodiment.
- the center portion of the bearing portion 35 has a cylindrical shape protruding downward, and the upper portion of the main shaft portion 41 is inserted. Therefore, the shaft insertion hole 26 has a large upper diameter and a lower lower diameter. Accordingly, the cylindrical portion of the bearing portion 35 (and the main shaft portion 41 inserted therein) can be inserted at the upper portion, and only the main shaft portion 41 can be inserted and supported at the lower portion.
- the iron core that constitutes the main body of the rotor 22A is formed by, for example, laminating disc-shaped electromagnetic steel plates (thin iron plates). Therefore, in order to integrate a plurality of electromagnetic steel sheets into an iron core, as shown in FIGS. 1 and 3B, a fastening member is provided so as to penetrate in a direction along the axis Z1.
- a plurality of electromagnetic steel plates are integrated by caulking pins 24. Each electromagnetic steel sheet is provided with a caulking hole for inserting the caulking pin 24.
- end plates 25 are provided on the upper surface and the lower surface of the rotor 22A, respectively.
- the end plate 25 is integrally fixed by a caulking pin 24 together with the iron core.
- an opening may be formed in the end plate 25 located on the lower surface of the rotor 22A as shown in FIG. 3C.
- the balance hole 27 is formed as a blind hole having a bottom surface on the upper side and an open bottom surface of the rotor 22A.
- the specific shape of the rotor 22A is not particularly limited, in the present embodiment, as shown in FIG. 3B, the diameter of the rotor 22A with respect to the length in the rotation axis direction (vertical direction) of the rotor 22A. It is preferable that the length in the direction (horizontal direction) is large. That is, the rotor 22A preferably has a “thick and short” configuration in which the diameter Ld is larger than the axial length Lr. For example, as shown in FIG. 3B, when the length of the rotor 22A in the rotation axis direction is “Lr” and the diameter of the rotor 22A is “Ld”, the length Lr is smaller than the diameter Ld. (Lr ⁇ Ld).
- the position where the balance adjusting means is provided in the rotor 22A is not particularly limited as long as it is at least a position where the load imbalance of the main shaft portion 41 can be relaxed (reduced or offset).
- a position where the balance adjusting means is provided a position based on the position of the center of gravity of the first oil supply passage 51, which is one of the main factors of load unbalance in the main shaft portion 41, can be cited.
- the load imbalance derived from the first oil supply passage 51 is alleviated as much as possible. A need arises. Therefore, in order to provide balance adjusting means for the rotor 22A, it is necessary to consider at least the position of the center of gravity of the space portion of the first oil supply passage 51.
- crankshaft 40 includes not only the main shaft portion 41 but also an eccentric shaft portion 42 having a shaft center different from that of the main shaft portion 41. Therefore, in order to alleviate the load imbalance of the main shaft portion 41, it is necessary to consider not only the gravity center position of the first oil supply passage 51 but also the gravity center position of the eccentric shaft portion 42.
- a balance weight is usually attached to the crankshaft 40 in order to alleviate the load imbalance resulting from the reciprocating motion of the piston 33. Therefore, in order to alleviate the load imbalance of the main shaft portion 41, it is necessary to consider the position of the center of gravity of the balance weight.
- the center of gravity position of the first oil supply passage 51 is set to “oil supply passage center of gravity W1”
- the center of gravity position of the eccentric shaft portion 42 is set to “eccentric shaft portion center of gravity W2”
- the position of the balance weight provided on the crankshaft 40 is set to “weight center of gravity. 4
- the eccentric shaft portion gravity center W2 and the weight gravity center W3 are positioned on a straight line together with the rotation axis of the rotor 22A, that is, the axis Z1 of the main shaft portion 41, as indicated by the X mark in FIG.
- the oil supply passage center of gravity W1 is located outside this straight line.
- the direction in which the oil supply passage center of gravity W1 is located as viewed from the axis Z1 is the D1 direction
- the direction in which the eccentric shaft center of gravity W2 is located is the D2 direction
- the direction in which the weight center of gravity W3 is located is the D3 direction
- the line corresponding to the D3 direction coincides with the diameter of the rotor 22A
- the D1 direction is a direction substantially orthogonal to the diameter. That is, when the rotor 22A is divided into two equal parts along the vertical direction (axial center Z1 direction), the oil supply passage center of gravity W1 is located in one of the two semi-cylindrical regions.
- the balance adjusting means may be provided in the other semi-cylindrical region instead of one semi-cylindrical region where the oil supply passage center of gravity W1 is located.
- one semi-cylindrical region where the oil supply passage gravity center W1 is located is referred to as a “centroid-side semi-cylindrical region 22a”, and the other semi-cylindrical region provided with the balance adjusting means is The side semi-cylindrical region 22b ”.
- the balance adjusting means is the balance hole 27, and the oil supply passage center of gravity W1 is positioned in the center-of-gravity side semi-cylindrical region 22a on the upper side in the drawing (strictly speaking, the oil supply passage center of gravity W1 is Since it is located in the main shaft portion 41, the oil supply passage gravity center W1 is located in the shaft insertion hole 26 in the rotor 22A in FIG. 4).
- the balance hole 27 may be provided at any position of the adjustment-side semi-cylindrical region 22b, which is the lower side in the drawing, as illustrated by a dotted line in FIG.
- the position where the balance hole 27 (balance adjusting means) is provided in the rotor 22A is the adjustment side half of the rotor 22A located on the opposite side of the axis Z1 as viewed from the center of gravity W1 of the oil supply passage.
- the inside of the columnar region 22b can be exemplified.
- the adjustment-side semi-cylindrical region 22b can be expressed by an angle range based on the rotation axis of the rotor 22A (that is, the axis Z1 of the main shaft portion 41).
- a radial line extending from the rotation axis (axial center Z1) of the rotor 22A through the eccentric shaft portion gravity center W2 is defined as a 0 ° reference line, and the direction opposite to the oil supply passage gravity center W1.
- the balance adjustment means is within the range of 0 to 180 ° when viewed from the reference line in the adjustment-side semi-cylindrical region 22b of the rotor 22A. This reference line coincides with the line in the D2 direction.
- the balance weight attached to the crankshaft 40 includes options such as a crank weight provided at the upper end of the eccentric shaft portion 42 or a shaft weight provided at the flange portion 43.
- a line corresponding to the D2 direction which is the direction in which the eccentric shaft portion gravity center W2 is located, of the D2 direction and the D3 direction corresponding to the diameter of the rotor 22A is used as a reference line with an angle of 0 °. .
- the balance hole 27 (balance adjusting means) is provided on the adjustment side semi-cylindrical region 22b (lower side in FIG. 4) opposite to the gravity center side semi-cylindrical region 22a (upper side in FIG. 4) where the oil supply passage center of gravity W1 is located. ),
- the angle in the direction toward the adjustment-side semi-cylindrical region 22b when viewed from the D2 direction that is the 0 ° reference line may be a positive (plus) angle.
- the angle in the direction toward the center-of-gravity side semi-cylindrical region 22a is a negative (minus) angle.
- this angular range is illustrated as a broken-line bidirectional arrow ⁇ 1 (0 ° ⁇ ⁇ 1 ⁇ 180 °).
- the balance hole 27 is provided, not the entire adjustment-side semi-cylindrical region 22b but a narrower range can be set.
- the center of gravity W1 of the oil supply passage has been ignored, so that it is in a state where two of the three centroids in FIG. 4, the eccentric centroid W2 and the weight centroid W3 should be considered.
- the weight center of gravity W3 of these two centers of gravity causes a load unbalance
- the balance hole 27 is provided as a balance adjusting means in order to alleviate this unbalance
- the position of the balance hole 27 is in the D2 direction. Directly above the line, that is, at a position of 0 °.
- the eccentric shaft portion gravity center W2 is the cause of unbalance
- the position of the balance hole 27 is directly above the line in the D3 direction, that is, an angle of 180 °.
- the balance hole 27 can be slightly shifted from the vicinity of the angle 0 ° or 180 ° toward the side opposite to the oil supply passage center of gravity W1. preferable.
- the balance hole 27 (balance adjustment means) is 5 to 175 ° out of the adjustment-side semi-cylindrical region 22b (angle range 0 to 180 °). It is preferable to be provided in a sector-shaped columnar region that falls within the range (5 ° ⁇ ⁇ 2 ⁇ 175 °). In other words, it is preferable to provide the balance hole 27 at a position shifted by 5 ° or more from the position of the angle 0 ° or the angle 180 °.
- the structure that is the main cause of the unbalance of the load generated in the main shaft portion 41 is the inclined first oil supply passage 51, but the oil supply groove 53 provided to be wound around the outer peripheral surface of the main shaft portion 41,
- the first through holes 52 and the oil supply holes 54 can also be a cause of load imbalance. Therefore, the position of the center of gravity W1 of the oil supply passage may be set in consideration of not only the center of gravity of the first oil supply passage 51 but also the shift of the center of gravity due to the oil supply groove 53, the first through hole 52, and the oil supply hole portion 54.
- the balance hole 27 may be provided in the adjustment-side semi-cylindrical region 22b so that the center of gravity of the first oil supply passage 51 and the center of gravity of the oil supply groove 53, the first through hole 52, and the oil supply hole portion 54 are taken into consideration.
- balance adjusting means such as the balance hole 27 is provided on the rotor 22A in order to adjust the load unbalance caused by the reciprocating motion of the piston 33 in addition to the load unbalance due to the structure of the main shaft portion 41. May be. Therefore, the unbalance resulting from the reciprocating motion of the piston 33 can be mitigated by the balance adjusting means provided on the rotor 22 ⁇ / b> A together with the balance weight provided on the crankshaft 40.
- FIG. 5 corresponds to the vertical side view (left view) of FIG. 2
- FIG. 6 corresponds to the lateral side view (right view) of FIG.
- the rotor 22A fixed to the main shaft portion 41 is also shown as a schematic cross-sectional view, and the oil supply passage gravity center W1, the eccentric shaft portion gravity center W2, and the weight gravity center W3 are also the same as in FIG. Is indicated by an X mark.
- the weight center of gravity W3 is the position of the center of gravity of the crank weight 45, it is expressed as a weight center of gravity W3-1.
- the balance weight is a crank weight 45 provided at the upper portion of the eccentric shaft portion 42
- the weight center of gravity W 3-1 is located above the eccentric shaft portion 42 and viewed from the front side in the longitudinal direction. Is located on the axis Z1 (overlapping the axis Z2 of the eccentric shaft portion 42).
- the weight center of gravity W3-1 is unevenly distributed on the rear side (right side in the figure) as viewed from the axis Z1. Therefore, as indicated by the block arrow Fc in FIG. 6, when the crankshaft 40 is rotating, a centrifugal force is applied to the rear side with respect to the crank weight 45.
- the eccentric shaft portion gravity center W2 is located on the axis Z2 (overlapping the axis Z1) in the eccentric shaft portion 42 when viewed from the front side in the vertical direction.
- the eccentric shaft portion 42 when viewed from the front side in the lateral direction, the eccentric shaft portion 42 is eccentric to the front side with respect to the main shaft portion 41, so that the crankshaft 40 rotates as indicated by the block arrow Fc in FIG. 6.
- a centrifugal force is applied to the front side with respect to the eccentric shaft portion 42.
- the oil supply passage center of gravity W1 When viewed from the front side in the longitudinal direction as shown in FIG. 5, the oil supply passage center of gravity W1 is slightly displaced from the axis Z1 in the main shaft portion 41 according to the inclination direction of the first oil supply passage 51 (in FIG. Tilted to the right front). In FIG. 5, the position where the center of gravity W1 of the oil supply passage is displaced from the axis Z1 is shown as an unbalance radius Ra. Further, as seen from the lateral front side as shown in FIG. 6, since the first oil supply passage 51 is not inclined in the horizontal direction, the oil supply passage center of gravity W1 is located on the axis Z1.
- the rotor 22A is provided with a balance hole 27 as a balance adjusting means for adjusting an unbalance of a load derived from the first oil supply passage 51.
- a balance hole 27 As seen from the front side in the vertical direction as shown in FIG. 5, it is located on the front side of the main shaft portion 41 (hidden by the main shaft portion 41 in FIG. 5), but “balance hole gravity center W 0” which is the center of gravity position of the balance hole 27. Is a position slightly deviated from the axis Z1 to the opposite side of the oil supply passage center of gravity W1 (in FIG. 5, it is displaced to the front side on the left side in the figure).
- the balance hole 27 when viewed from the front side in the lateral direction, the balance hole 27 is provided in the rotor 22 ⁇ / b> A at the front side when viewed from the crankshaft 40.
- the balance hole 27 is a blind hole that opens downward, the balance hole gravity center W0 is unevenly distributed below the rotor 22A.
- the balance weight is the crank weight 45
- the inside of the sector columnar region having the angle range ⁇ 3 can be cited.
- the balance hole 27 in the angle range ⁇ 3 it is possible to satisfactorily relax (reduce or cancel) the unbalance radius Ra shown in FIG.
- the adjustment side semi-cylindrical region 22b has 5 to 40 as viewed from the reference line (D2 direction). It is more preferable that the balance hole 27 is provided in the sector columnar region (5 ° ⁇ ⁇ 3 ⁇ 40 °) within the range of °.
- a plurality of balance holes 27 may be provided in the rotor 22A, but in this case, the balance hole centroid W0 in all of the plurality of balance holes 27 is a centroid position to be considered.
- the inverter is driven at a plurality of operation frequencies as described above.
- a low speed operation for reducing the rotation speed of the electric element 20A and a high speed operation for increasing the rotation speed of the electric element 20A occur.
- the natural frequency of the compressor body 12 elastically supported by the suspension spring 14 is generally close to the low-speed rotation speed of the inverter operation. For this reason, during high speed operation, the load imbalance of the main shaft portion 41 derived from the first oil supply passage 51 is often negligible as before.
- the operating speed is determined by the natural frequency of the compressor body 12 elastically supported by the suspension spring 14. Since the main shaft portion 41 is close to the main shaft portion 41 due to the structure of the main shaft portion 41, it is clear that the load imbalance of the main shaft portion 41 causes vibration.
- FIG. 8 shows an operation result in which the relationship between the number and the vibration is shown in a graph.
- the difference between the compressor of the present embodiment and the conventional compressor is basically only whether or not the balance hole 27 is provided in the rotor 22A.
- the vertical axis indicates the relative magnitude of vibration
- the horizontal axis indicates the rotational speed (unit: r / s) of the electric element 20A.
- a broken line is a result of a conventional compressor, and a continuous line is this form compressor.
- the rotational speed of the horizontal axis in the operation result is a numerical value based on a specific configuration provided in the conventional compressor and the compressor of the present embodiment, and if the specific configuration is different or the type of the compressor is different, Needless to say, the number of revolutions is also different.
- the vibration is not so large, for example, when rotating at 26 to 30 r / s.
- the magnitude of vibration becomes a peak at a low speed of about 21 r / s. This large vibration is influenced by the load imbalance of the main shaft portion 41.
- the balance hole 27 is provided in the adjustment-side semi-cylindrical region 22b of the rotor 22A, so that the load unbalance of the main shaft portion 41 is good.
- the conventional compressor is used in almost all the rotation speed ranges shown in the graph except that the vibration is approximately the same at about 17 r / s which is the minimum rotation speed on the graph.
- the magnitude of vibration is less than.
- the vibration is the smallest during the low speed rotation of about 20 r / s, and the magnitude of the vibration is the same as that during the high speed rotation of about 30 r / s.
- the horizontal axis is the position of the balance hole 27.
- the line in the D2 direction is a reference line with an angle of 0 °, and the balance hole 27 is positive and negative. Indicates the position.
- the vertical axis indicates the relative magnitude of vibration, as in FIG.
- the position of the balance hole 27 is changed within a range of ⁇ 10 ° to + 40 °, and the magnitude of vibration of the compressor according to the present embodiment is observed.
- the balance hole 27 is provided in the range of + 5 ° to + 40 °, that is, in the fan-shaped columnar region having the angle range ⁇ 3 shown in FIG. It can be seen that it can be reduced.
- the vibration is smaller in the range of + 10 ° to + 35 °, and within the range of + 14 ° to + 26 ° (within the range of 20 ° ⁇ 6 °). It can be seen that the vibration is further reduced.
- the vibration may be sufficiently reduced even within the range of 0 ° to + 5 ° or beyond + 40 °. Needless to say.
- FIG. 10 corresponds to the vertical side view (left view) of FIG. 2
- FIG. 11 corresponds to the lateral side view (right view) of FIG.
- the rotor 22 ⁇ / b> A is also shown as a schematic cross-sectional view, and three or four barycentric positions are indicated by X marks.
- the weight gravity center W3 is the position of the gravity center of the shaft weight 46, it is expressed as a weight gravity center W3-2.
- the eccentric shaft portion center of gravity W ⁇ b> 2 overlaps the axis Z ⁇ b> 2 (in FIG. 10, the axis Z ⁇ b> 1 in the eccentric shaft portion 42) when viewed from the front side in the vertical direction. (Not shown).
- the eccentric shaft portion 42 when viewed from the front side in the lateral direction, the eccentric shaft portion 42 is eccentric to the front side with respect to the main shaft portion 41, so that the crankshaft 40 rotates as shown by the block arrow Fc in FIG. 11.
- a centrifugal force is applied to the front side with respect to the eccentric shaft portion 42.
- the weight gravity center W3-2 is a position on the axis Z1 of the main shaft portion 41 (overlapping the axis Z2 of the eccentric shaft portion 42) in the flange portion 43 when viewed from the front side in the vertical direction. Further, as shown in FIG. 11, when viewed from the front side in the lateral direction, the weight gravity center W3-2 is unevenly distributed on the rear side (right side in the figure) as viewed from the axis Z1. Therefore, as indicated by the block arrow Fc in FIG. 11, when the crankshaft 40 is rotating, a centrifugal force is applied to the rear side with respect to the shaft weight 46.
- the oil supply passage center of gravity W1 When viewed from the front side in the longitudinal direction as shown in FIG. 10, the oil supply passage center of gravity W1 is located at a position slightly shifted from the axis Z1 in the main shaft portion 41 in accordance with the inclination direction of the first oil supply passage 51 (FIG. Tilted to the right front).
- the position where the oil supply passage center of gravity W1 deviates from the axis Z1 is shown as an unbalance radius Ra as in FIG.
- the first oil supply passage 51 when viewed from the front side in the horizontal direction, the first oil supply passage 51 is not inclined in the horizontal direction, so the oil supply passage center of gravity W1 is located on the axis Z1.
- the balance hole 27 is hidden behind the main shaft portion 41 when viewed from the front side in the vertical direction.
- the balance hole center of gravity W0 is similar to that of FIG. The position is slightly shifted to the opposite side (in FIG. 10, it is shifted to the back side on the left side in the figure).
- the balance hole 27 is provided in the rotor 22 ⁇ / b> A at a position on the rear side when viewed from the crankshaft 40. This position is opposite to the position of the balance hole 27 (front position) in the crank weight 45 shown in FIG.
- the balance hole 27 is a blind hole that opens downward, the balance hole gravity center W0 is unevenly distributed on the lower side of the rotor 22A.
- the rotor 22A is centrifuged to the rear side opposite to the side where the balance hole 27 is provided (front side). It takes power. Accordingly, in FIG. 11, the force (moment) that attempts to rotate the upper and lower portions of the crankshaft 40 is reduced by the centrifugal force at the three locations indicated by the block arrows Fc. Therefore, the force that the crankshaft 40 swings is reduced.
- a more preferable position of the balance hole 27 provided in the rotor 22A is, for example, in the sector columnar region in the angle range ⁇ 4 as shown in FIG. .
- the positional relationship among the oil supply passage center of gravity W1, the eccentric shaft center of gravity W2, and the weight center of gravity W3-2 is the same as in FIG. Further, the three gravity center positions and the balance hole gravity center W0 are in the positional relationship described above (see FIGS. 10 and 11).
- the balance hole 27 is provided in the sector columnar region (140 ° ⁇ ⁇ 4 ⁇ 175 °) that falls within the range of °.
- the sectoral columnar region in the angle range ⁇ 3 and the sectoral columnar region in the angle range ⁇ 4 are in a line-symmetric positional relationship with reference to the diameter line that coincides with the D1 direction.
- the rotor 22A constituting the electric element 20A has a balance adjusting means for adjusting the load imbalance caused by at least the structure of the main shaft portion 41.
- the balance hole 27 may be provided as an adjustment side semi-cylindrical shape located on the opposite side across the axis Z1 of the main shaft portion 41 as viewed from the oil supply passage center of gravity W1. It is preferable to be in the region 22b.
- this adjustment-side semi-cylindrical region 22b is shown in an angular range, a radial line (line in the D2 direction) extending from the rotation axis (axial center Z1) of the rotor 22A through the eccentric shaft portion gravity center W2 is 0 °.
- the angle range ⁇ 1 0 ° to 180 °.
- the sector columnar region of the angle range ⁇ 2 5 to 175 °, and further, depending on the type (installation position) of the balance weight provided in the crankshaft 40.
- the balance hole 27 as the balance adjusting means, the load unbalance caused by the structure of the main shaft portion 41 is not adjusted at the main shaft portion 41 or the crankshaft 40 but is fixed to the main shaft portion 41. Adjustment is performed in the rotor 22A. Since the rotor 22A has a cylindrical shape or a columnar shape extending in a direction orthogonal to the axial direction of the crankshaft 40, it is easier to provide balance adjusting means than the elongated crankshaft 40 or the main shaft portion 41. At the same time, the position where the balance adjusting means is provided can be finely adjusted.
- the load imbalance of the main shaft portion 41 can be relaxed (reduced or offset) satisfactorily.
- the balance hole 27 is employed as the balance adjusting means.
- the balance adjusting means is not limited to the balance hole 27, and may be a balance weight attached to the rotor 22A.
- the balance weight attached to the rotor 22A is “rotor weight”, for example, FIG. 13A or FIG.
- the structure which fixes the rotor weight 28 to the upper surface of the rotor 22A can be mentioned.
- the rotor weight 28 may be fixed to the lower surface of the rotor 22A, or the rotor weight 28 may be fixed to both the upper surface and the lower surface.
- the position where the rotor weight 28 is provided is not particularly limited, but if the position where the balance hole 27 is provided is used as a reference, the position where the rotor weight 28 is provided is located on the opposite side of the rotation axis (rotation center) of the rotor 22A. Position.
- the balance hole 27 adjusts the balance by partially reducing the weight of the rotor 22A, it can be said that the balance adjustment means is “negative balance”.
- the rotor weight 28 adjusts the balance by partially adding weight to the rotor 22A. Therefore, it can be said that the balance adjusting means is “positive balance”. Therefore, the position where the rotor weight 28 is provided is opposite to the position of the balance hole 27.
- the balance hole 27 is formed in the rotor 22A as shown in FIG. Of these, it is provided in the sector columnar region of the angle range ⁇ 3.
- the rotor weight 28 is used instead of the balance hole 27, the fan-shaped columnar region (the same as the angle range ⁇ 3) on the opposite side via the axis Z1 that is the rotation axis of the rotor 22A.
- the rotor weight 28 may be provided in the region.
- a preferable position of the balance hole 27 is the axis of the main shaft portion 41 as viewed from the center of gravity of the first oil supply passage 51 in the rotor 22A.
- the balance adjusting means is the rotor weight 28 having a positive balance
- the preferred position of the rotor weight 28 is the rotor 22A located on the side where the center of gravity position of the first oil supply passage 51 exists.
- the center-of-gravity side semi-cylindrical region 22b (the semi-cylindrical region having an angle range of 180 ° to 360 ° in FIG. 4).
- a balance hole 27 and a rotor weight 28 may be used in combination as a balance adjusting means.
- the balance hole 27 is formed in the iron core as a blind hole that opens to the lower surface, as in FIG. 3B, and the rotor weight 28 is fixed to the upper surface in the same manner as in FIG. 13A.
- the balance adjusting unit may be at least one of the balance hole 27 and the rotor weight 28, but may be configured such that the balance can be adjusted by other than the balance hole 27 or the rotor weight 28.
- the position of the balance adjusting unit may be limited based on different conditions. For example, when the balance adjusting means is provided in a plurality of different places, the balance adjusting means is provided unevenly on the iron core that is the main body of the rotor 22A so as not to be line-symmetric or point-symmetric with respect to the rotation axis (axis Z1). May be.
- the balance hole 27 is provided in the iron core of the rotor 22A.
- the balance hole 27 may be provided in a portion other than the iron core depending on the configuration of the rotor 22A.
- the balance hole 27 is configured to extend along the direction of the rotation axis of the rotor 22A (the axis Z1 of the main shaft portion 41), but the configuration of the balance hole 27 is not limited thereto. Other configurations may be used.
- the balance adjustment means may be configured to adjust the balance with respect to the structure of the oil supply mechanism 50 such as the first oil supply passage 51 or the oil supply groove 53 and the like that causes load imbalance in the main shaft portion 41.
- the specific shape or the like for the balance hole 27, the direction of the hole, the diameter of the hole, the depth of the hole, whether or not it is a through hole, etc.
- the configuration that causes load imbalance in the main shaft portion 41 is not limited to the oil supply passage or the oil supply groove that configures the oil supply mechanism 50, and may be various configurations provided in the main shaft portion 41.
- the inclination of the first oil supply passage 51 is the main cause of unbalance of the load generated in the main shaft portion 41.
- the present disclosure is not limited to this, and the first oil supply passage 51 may not be inclined if the position of the oil supply passage center of gravity W1 is deviated from the axis Z1 of the main shaft portion 41.
- the position of the oil supply passage center of gravity W1 can be set in consideration of not only the center of gravity of the first oil supply passage 51 but also the deviation of the center of gravity due to the oil supply groove 53, the first through hole 52, and the oil supply hole portion 54. Therefore, if the oil supply passage center of gravity W1 is deviated from the axis Z1 when viewed as the main shaft portion 41 as a whole, the rotor 22A is provided with balance adjusting means such as the balance hole 27 or the rotor weight 28. Thus, the unbalance of the load of the main shaft portion 41 can be relaxed (reduced or offset) satisfactorily.
- the electric element 20A is an inner rotor type motor, but the present disclosure is not limited thereto, and the electric element may be an outer rotor type motor.
- the hermetic refrigerant compressor 10B according to the second embodiment is housed in the hermetic container 11 in the same manner as the hermetic refrigerant compressor 10A according to the first embodiment.
- the electric element 20B and the compression element 30 are provided, and the refrigerant gas and the lubricating oil 13 are sealed in the sealed container 11, and the electric element 20B is an outer rotor type motor. is there.
- the electric element 20B is composed of at least a stator 21B and a rotor 22B, similarly to the electric element 20A according to the first embodiment.
- the stator 21B has a shaft insertion hole 26 at the center thereof, and the bearing portion 35 of the compression element 30 with respect to the shaft insertion hole 26. Is fixed by press-fitting or the like.
- the rotor 22B is coaxially disposed so as to surround the outer periphery of the stator 21B, as shown in FIGS. 14, 15A, and 15B.
- the length of the rotor 22B in the rotation axis direction (axial center Z1 direction) is smaller than the diameter of the rotor 22B. That is, the rotor 22B in the second embodiment also has a large and short configuration similar to the rotor 22A in the first embodiment.
- the permanent magnets 23 are evenly arranged on the inner periphery of a cylindrical yoke 29 that rotates on the outer periphery of the stator 21B.
- the yoke 29 may be formed in a disk shape having a larger diameter than the flange portion 43, or the cylindrical yoke 29 is fixed to the outer periphery of a frame having a larger diameter than the flange portion 43. It may be a configuration.
- a shaft insertion hole 26 is provided at the center of the yoke 29 (or frame) of the rotor 22B.
- the shaft insertion hole 26 is the main shaft of the crankshaft 40.
- the lower end of the portion 41 is fixed by welding or the like.
- the hermetic refrigerant compressor 10B according to the present embodiment is the same as the hermetic refrigerant compressor 10A according to the first embodiment (see FIG. 1) except that the electric element 20B is an outer rotor type motor. Therefore, the specific description is omitted.
- the suction pipe 15 is not shown.
- the hermetic refrigerant compressor 10B according to the present embodiment also includes the suction pipe 15 in the same manner as the hermetic refrigerant compressor 10A shown in FIG. Yes.
- the permanent magnet 23 provided in the rotor 22A is not shown, but in FIG. 14, the permanent magnet 23 provided in the rotor 22B is illustrated.
- the operation of the hermetic refrigerant compressor 10B is basically the same as that of the hermetic refrigerant compressor 10A. That is, when the electric element 20B is energized, a current flows through the stator 21B to generate a magnetic field, and the rotor 22B fixed to the main shaft portion 41 of the crankshaft 40 rotates. As a result, the crankshaft 40 rotates and the piston 33 reciprocates in the cylinder 32 via the connecting rod 44 that is rotatably attached to the eccentric shaft portion 42, so that the refrigerant is compressed by the compression element 30. Become.
- the balance that is a balance adjusting unit with respect to the rotor 22B included in the electric element 20B.
- a hole 27 is provided.
- an iron core as a main body is configured as a yoke 29, and a permanent magnet 23 is provided on the inner peripheral surface of the yoke 29. Therefore, the electric element 20B is an SPM type motor.
- the rotor 22B does not include a magnet protection member that covers the surface (inner peripheral surface) of the permanent magnet 23 (does not require a magnet protection member).
- the balance hole 27 extends along the axis Z1 direction of the rotor 22B, as shown in FIGS. 14 and 15B.
- the balance hole 27 when viewed from the upper surface or the lower surface of the rotor 22B, the balance hole 27 is unevenly distributed in a part near the outer periphery of the rotor 22B.
- the balance hole 27 is provided at a position at least a part of which is outside the permanent magnet 23 when viewed from the axial center Z1 of the rotor 22B.
- the specific position of the balance hole 27 is not particularly limited.
- the specific configuration of the balance hole 27 is as described in the first embodiment. That is, the balance hole 27 is located on the rotor 22B on the opposite side of the shaft center Z1 of the main shaft portion 41 when viewed from the center of gravity position of the first oil supply passage 51 (oil supply passage center of gravity W1). What is necessary is just to be provided in the semi-cylindrical area
- the balance hole 27 is within the sector-shaped columnar region (region of the angle range ⁇ 2 shown in FIG. 4) within the range of 5 to 175 ° as viewed from the reference line.
- the sector-shaped columnar region region of angle range ⁇ 3 shown in FIG. 7 in the range of 5 to 40 ° when viewed from the reference line, and in the range of 140 to 175 ° Provided in at least one of the fan-shaped columnar regions (region of the angle range ⁇ 4 shown in FIG. 11).
- the balance hole 27 as a balance adjusting means, the load imbalance due to the structure of the main shaft portion 41 can be reduced.
- adjustment can be made at the rotor 22B fixed to the main shaft portion 41.
- the load imbalance of the main shaft portion 41 can be relaxed (reduced or offset) satisfactorily.
- it is possible to further reduce the vibration of the hermetic refrigerant compressor 10B.
- the hermetic refrigerant compressor 10A or 10B according to the present disclosure can be widely and suitably used for a refrigeration cycle or various devices (refrigeration devices) having a substantially equivalent configuration.
- refrigerators household refrigerators, commercial refrigerators
- ice machines showcases
- dehumidifiers heat pump water heaters
- heat pump washer / dryers vending machines
- air conditioners air compressors, etc.
- it does not specifically limit.
- the basic configuration of the refrigeration apparatus 60 will be described using the article storage device illustrated in FIG.
- the 16 includes a refrigeration apparatus body 61 and a refrigerant circuit.
- the refrigeration apparatus main body 61 is composed of a heat-insulating box with one surface opened and a door that opens and closes the opening of the box.
- the inside of the refrigeration apparatus main body 61 includes a storage space 62 for storing articles, a machine room 63 for storing a refrigerant circuit, etc., a partition wall 64 for partitioning the storage space 62 and the machine room 63, and the like.
- the refrigerant circuit is connected to the hermetic refrigerant compressor 10A described in the first embodiment or the hermetic refrigerant compressor 10B described in the second embodiment, the radiator 65, the decompression device 66, the heat absorber 67, and the like. 68 is connected in a ring shape. That is, the refrigerant circuit is an example of a refrigeration cycle using the hermetic refrigerant compressor 10A or 10B according to the present disclosure.
- the hermetic refrigerant compressor 10A or 10B, the radiator 65, and the decompression device 66 are arranged in the machine chamber 63, and the heat absorber 67 is provided in a storage space 62 including a blower not shown in FIG. Has been placed.
- the cooling heat of the heat absorber 67 is agitated so as to circulate in the storage space 62 by a blower, as indicated by a broken arrow.
- the refrigeration apparatus 60 is mounted with the hermetic refrigerant compressor 10A according to the first embodiment or the hermetic refrigerant compressor 10B described in the second embodiment.
- the rotor 22 ⁇ / b> A or 22 ⁇ / b> B has a balance adjusting unit that adjusts at least the load imbalance caused by the structure of the main shaft portion 41, for example, the balance A hole 27 is provided.
- the hermetic refrigerant compressor 10A or 10B it is possible to satisfactorily reduce or cancel the load imbalance of the main shaft portion 41 when viewed as the compressor main body 12 as a whole. As a result, it is possible to further reduce the vibration of the hermetic refrigerant compressor 10A or 10B. By operating the refrigerant circuit with such a hermetic refrigerant compressor 10A or 10B, the vibration of the refrigeration apparatus 60 can be further reduced.
- the present invention can be widely and suitably used in the field of hermetic refrigerant compressors constituting a refrigeration cycle. Furthermore, refrigeration using a hermetic refrigerant compressor, such as household refrigeration equipment such as electric refrigerators and air conditioners, or commercial refrigeration equipment such as dehumidifiers, commercial showcases, and vending machines. It can be suitably used widely in the field of devices.
- a hermetic refrigerant compressor such as household refrigeration equipment such as electric refrigerators and air conditioners, or commercial refrigeration equipment such as dehumidifiers, commercial showcases, and vending machines. It can be suitably used widely in the field of devices.
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Abstract
Description
まず、本開示に係る密閉型冷媒圧縮機の代表的な構成例について、図1および図2を参照して具体的に説明する。
図1に示すように、本実施の形態1に係る密閉型冷媒圧縮機10Aは、密閉容器11内に収容される電動要素20Aおよび圧縮要素30を備えており、密閉容器11の内部には、冷媒ガスおよび潤滑油13が封入されている。電動要素20Aおよび圧縮要素30は圧縮機本体12を構成している。この圧縮機本体12は、密閉容器11の底部に設けられているサスペンションスプリング14によって弾性的に支持された状態で、当該密閉容器11内に配置されている。
次に、クランクシャフト40に設けられている給油機構50の代表的な構成例について、図2を参照して説明する。
次に、前記構成の密閉型冷媒圧縮機10Aの動作について、その作用とともに具体的に説明する。なお、図1には図示しないが、前記の通り、密閉型冷媒圧縮機10Aは吸入管15および吐出管16を備えており、これらが周知の構成からなる冷凍装置に接続されることにより、冷媒回路を構成している。
次に、本開示に係る密閉型冷媒圧縮機10Aにおいて、回転子22Aに設けられ、少なくとも主軸部41の構造に起因する荷重のアンバランスを調整するバランス調整手段について、図1に加えて図3A~図3Cおよび図4を参照して具体的に説明する。
次に、クランクシャフト40に設けられるバランスウェイトの位置に基づいて、回転子22A(調整側半円柱状領域22b)のうちバランス穴27を設けるより好ましい領域について、図5~図12を参照して具体的に説明する。
前述した構成の密閉型冷媒圧縮機10Aでは、バランス調整手段としてバランス穴27を採用していたが、バランス調整手段はバランス穴27に限定されず、回転子22Aに取り付けられるバランスウェイトでもよい。
前記実施の形態1に係る密閉型冷媒圧縮機10Aは、電動要素20Aがインナーロータ型モータであったが、本開示はこれに限定されず、電動要素がアウターロータ型モータであってもよい。具体的には、図14に示すように、本実施の形態2に係る密閉型冷媒圧縮機10Bは、前記実施の形態1に係る密閉型冷媒圧縮機10Aと同様に、密閉容器11内に収容される電動要素20Bおよび圧縮要素30(圧縮機本体12)を備えており、密閉容器11の内部には、冷媒ガスおよび潤滑油13が封入されているが、電動要素20Bはアウターロータ型モータである。
本実施の形態3では、前記実施の形態1で説明した密閉型冷媒圧縮機10Aまたは前記実施の形態2で説明した密閉型冷媒圧縮機10Bを備える冷凍装置の一例について、図16を参照して具体的に説明する。
11 密閉容器
12 圧縮機本体
13 潤滑油
20A,20B 電動要素
21A,21B 固定子
22A,22B 回転子
23 永久磁石
27 バランス穴(バランス調整手段)
28 回転子ウェイト(バランス調整手段、バランスウェイト)
30 圧縮要素
31 シリンダブロック
32 シリンダ
33 ピストン
34 圧縮室
35 軸受部
40 クランクシャフト
41 主軸部
42 偏心軸部
43 フランジ部
44 コンロッド
45 クランクウェイト(バランスウェイト)
46 シャフトウェイト(バランスウェイト)
50 給油機構
51 第一給油通路
52 第一連通孔
53 給油溝
54 給油孔部
55 第二給油通路
56 第二連通孔
60 冷凍装置
Claims (10)
- 内部に潤滑油が封入され、下方に前記潤滑油が貯留されている密閉容器と、
当該密閉容器内に収容される電動要素と、
前記密閉容器内に収容され、前記電動要素によって駆動される圧縮要素と、
を備え、
前記圧縮要素は、
主軸部および偏心軸部を含むクランクシャフトと、
上下方向に交差する方向に沿って前記密閉容器内に配置されるシリンダと、
前記偏心軸部に連結され、前記シリンダ内で往復運動するピストンと、
を備え、
前記電動要素は、
固定子と、前記主軸部が固定された回転子と、
を備え、
さらに、前記回転子には、少なくとも前記主軸部の構造に起因する荷重のアンバランスを調整するバランス調整手段が設けられていることを特徴とする、
密閉型冷媒圧縮機。 - 前記バランス調整手段は、前記回転子に設けられるバランス穴およびバランスウェイトの少なくともいずれかであることを特徴とする、
請求項1に記載の密閉型冷媒圧縮機。 - 前記圧縮要素は、前記主軸部を軸支する軸受部をさらに備えるとともに、前記クランクシャフトは、給油機構をさらに備えており、
前記給油機構には、前記主軸部の下端面に連通する給油通路が含まれ、当該給油通路の重心位置が前記主軸部の軸心から外れており、
前記バランス調整手段が前記バランス穴であるときに、
前記バランス調整手段は、前記回転子において、前記給油通路の重心位置から見て、前記主軸部の軸心を挟んで対向する側に位置する、当該回転子の半円柱状領域内に設けられていることを特徴とする、
請求項2に記載の密閉型冷媒圧縮機。 - 前記回転子の回転軸から前記偏心軸部の重心位置を通って延伸する半径方向の線を0°の基準線とし、前記給油通路の重心位置とは反対側となる方向の角度を正の角度としたときに、
前記バランス調整手段は、前記回転子の半円柱状領域のうち、前記基準線から見て5~175°の範囲内となる扇形柱状領域内に設けられていることを特徴とする、
請求項3に記載の密閉型冷媒圧縮機。 - 前記バランス調整手段は、前記回転子の半円柱状領域のうち、前記基準線から見て5~40°の範囲内となる扇形柱状領域内、および、140~175°の範囲内となる扇形柱状領域内の少なくとも一方に設けられていることを特徴とする、
請求項4に記載の密閉型冷媒圧縮機。 - 前記バランス穴は、前記回転子の鉄心に設けられていることを特徴とする、
請求項2から5のいずれか1項に記載の密閉型冷媒圧縮機。 - 前記バランス穴は、前記回転子の回転軸方向に沿って延伸する構成であることを特徴とする、
請求項2から6のいずれか1項に記載の密閉型冷媒圧縮機。 - 前記バランス穴は、底面を有する止まり穴または貫通孔であることを特徴とする、
請求項2から7のいずれか1項に記載の密閉型冷媒圧縮機。 - 前記バランス調整手段は、前記主軸部の構造に起因する荷重のアンバランスに加えて、前記ピストンの往復運動により生じる荷重のアンバランスを調整することを特徴とする、
請求項1から8のいずれか1項に記載の密閉型冷媒圧縮機。 - 請求項1から9のいずれか1項に記載の密閉型冷媒圧縮機を備えていることを特徴とする、
冷凍装置。
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EP18806750.8A EP3633193B1 (en) | 2017-05-23 | 2018-05-21 | Hermetic refrigerant compressor and freezing apparatus |
CN201880034600.6A CN110662902B (zh) | 2017-05-23 | 2018-05-21 | 密封制冷压缩机及制冷装置 |
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- 2018-05-21 JP JP2019520241A patent/JP6648342B2/ja active Active
- 2018-05-21 EP EP18806750.8A patent/EP3633193B1/en active Active
- 2018-05-21 WO PCT/JP2018/019478 patent/WO2018216654A1/ja active Application Filing
- 2018-05-21 US US16/616,043 patent/US11473571B2/en active Active
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Publication number | Publication date |
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EP3633193A4 (en) | 2020-04-08 |
EP3633193B1 (en) | 2022-02-16 |
JP6648342B2 (ja) | 2020-02-14 |
JPWO2018216654A1 (ja) | 2019-11-07 |
US20210062798A1 (en) | 2021-03-04 |
EP3633193A1 (en) | 2020-04-08 |
CN110662902B (zh) | 2022-03-25 |
US11473571B2 (en) | 2022-10-18 |
CN110662902A (zh) | 2020-01-07 |
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