WO2023281932A1 - ターボ式流体機械、および冷凍装置 - Google Patents
ターボ式流体機械、および冷凍装置 Download PDFInfo
- Publication number
- WO2023281932A1 WO2023281932A1 PCT/JP2022/021608 JP2022021608W WO2023281932A1 WO 2023281932 A1 WO2023281932 A1 WO 2023281932A1 JP 2022021608 W JP2022021608 W JP 2022021608W WO 2023281932 A1 WO2023281932 A1 WO 2023281932A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- shaft
- connecting portion
- impeller
- holes
- fluid machine
- Prior art date
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 33
- 238000005057 refrigeration Methods 0.000 title claims description 11
- 230000007246 mechanism Effects 0.000 claims abstract description 35
- 230000006835 compression Effects 0.000 claims abstract description 22
- 238000007906 compression Methods 0.000 claims abstract description 22
- 230000002093 peripheral effect Effects 0.000 claims description 14
- 230000008878 coupling Effects 0.000 abstract description 4
- 238000010168 coupling process Methods 0.000 abstract description 4
- 238000005859 coupling reaction Methods 0.000 abstract description 4
- 239000003507 refrigerant Substances 0.000 description 16
- 238000005452 bending Methods 0.000 description 11
- 230000004048 modification Effects 0.000 description 7
- 238000012986 modification Methods 0.000 description 7
- 238000000034 method Methods 0.000 description 5
- 238000001816 cooling Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 238000007789 sealing Methods 0.000 description 4
- 239000000463 material Substances 0.000 description 3
- 238000003466 welding Methods 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- 230000004323 axial length Effects 0.000 description 2
- 230000006837 decompression Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- CWYNVVGOOAEACU-UHFFFAOYSA-N Fe2+ Chemical compound [Fe+2] CWYNVVGOOAEACU-UHFFFAOYSA-N 0.000 description 1
- 238000013019 agitation Methods 0.000 description 1
- 235000009508 confectionery Nutrition 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/053—Shafts
- F04D29/054—Arrangements for joining or assembling shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/051—Axial thrust balancing
- F04D29/0513—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/662—Balancing of rotors
Definitions
- the present disclosure relates to a turbo fluid machine and a refrigeration system.
- Patent Literature 1 discloses a turbo compressor as a turbo fluid machine.
- a turbo compressor In a turbo compressor, mounting holes are formed in the disk portion of the impeller. By attaching a weight to this hole, it is possible to adjust the balance of the turbo compressor.
- Patent Document 1 As shown in FIGS. 6 and 7 of the same document, elongated holes are formed in the disk portion in the axial direction of the impeller, so the thickness of the disk portion increases. As the disk portion becomes thicker and the weight of the impeller increases, the bending moment acting on the shaft increases, making the shaft more susceptible to bending. As a result, there is a problem that the operation in which the shaft is rotated at high speed becomes impossible, and the operation range becomes narrower.
- the present disclosure is to provide a turbo-fluid machine capable of adjusting balance while suppressing shaft deformation.
- a first aspect is a connection that connects a rotationally driven shaft (40), a compression mechanism (50) having an impeller (51), and an end of the shaft (40) and the impeller (51). a portion (70), and the coupling portion (70) is provided with a balance adjustment mechanism (80).
- the balance adjustment mechanism (80) is provided at the connecting portion (70) between the shaft (40) and the impeller (51). Therefore, unlike the conventional example, the balance of the turbo fluid machine can be adjusted without attaching a weight or the like to the impeller (51). As a result, it is possible to suppress an increase in the bending moment acting on the shaft (40) due to an increase in the weight of the impeller (51), thereby suppressing deflection of the shaft (40).
- the shaft (40), the connecting portion (70), and the impeller (51) are separate parts.
- the balance of the unit can be adjusted in a state in which the connecting portion (70) is attached to the shaft (40) to form a unit. Since the impeller (51) is a separate member from the connecting portion (70), the balance can be individually adjusted only with the impeller (51). As a result, it is possible to improve the accuracy of the overall balance adjustment in the turbo fluid machine after assembly.
- the density of the connecting portion (70) is lower than the density of the shaft (40).
- the weight of the connecting portion (70) can be reduced, so that an increase in the bending moment acting on the shaft (40) due to the provision of the connecting portion (70) can be suppressed. Thereby, bending of the shaft (40) can be suppressed.
- the balance adjustment mechanism (80) comprises a plurality of holes (81) formed in the connecting portion (70) and a and a weight component (85) mounted in a predetermined hole (81) in (81).
- the balance can be adjusted by attaching the weight component (85) to a predetermined hole (81) among the plurality of holes (81) of the connecting portion (70).
- a plurality of holes (81) are arranged in the circumferential direction of the connecting portion (70).
- the substantial weight distribution in the circumferential direction of the shaft (40) can be adjusted.
- the connecting portion (70) includes a first row group (L1) consisting of a plurality of holes (81) arranged in the circumferential direction of the connecting portion (70).
- a second row group (L2) is formed, and the first row group (L1) and the second row group (L2) are arranged in the axial direction of the connecting portion (70).
- the substantial weight distribution in the axial direction can be adjusted.
- a first member (90) is arranged with a gap (G) between the outer peripheral surface of the connecting portion (70) and the connecting portion (70).
- the gap (G) between the connecting portion (70) and the first member (90) can be used as a seal portion that suppresses fluid leakage.
- a portion (73a) of the connecting portion (70) surrounded by the first member (90) has a smaller outer diameter than the shaft (40).
- the outer diameter of the portion (73a) of the connecting portion (70) surrounded by the first member (90) is made smaller than the outer diameter of the shaft (40), so that the diameter of the gap (G) is reduced. become smaller. As a result, the area of the sealing portion formed by the gap (G) is reduced, so the fluid is less likely to leak.
- a ninth aspect is a refrigeration system comprising the turbo fluid machine (20) of any one of the first to eighth aspects.
- FIG. 1 is a schematic configuration diagram of a refrigeration system provided with a compressor according to an embodiment.
- FIG. 2 is a schematic longitudinal sectional view showing the overall configuration of the turbo compressor according to the embodiment.
- FIG. 3 is an enlarged perspective view of the connecting portion and its surroundings.
- FIG. 4 is a longitudinal sectional view enlarging the connecting portion and its surroundings.
- FIG. 5 is an enlarged vertical cross-sectional view of the connecting portion and the balance adjustment mechanism.
- FIG. 6 is a schematic configuration diagram for explaining the steps of assembling the shaft, connecting portion, and impeller.
- FIG. 4 is a schematic longitudinal sectional view showing the overall configuration of the turbo compressor according to the embodiment.
- FIG. 3 is an enlarged perspective view of the connecting portion and its surroundings.
- FIG. 4 is a longitudinal sectional view enl
- a turbo fluid machine of the present disclosure is applied to a turbo compressor (20).
- a turbo compressor (20) is provided in the refrigerator (1).
- a refrigerating device (1) shown in Fig. 1 includes a turbo compressor (hereinafter also referred to as a compressor (20)) of the present disclosure.
- a refrigerating device (1) has a refrigerant circuit (1a) filled with a refrigerant.
- the refrigerant circuit (1a) has a compressor (20), a radiator (2), a pressure reducing mechanism (3), and an evaporator (4).
- the decompression mechanism (3) is an expansion valve.
- the refrigerant circuit (1a) performs a vapor compression refrigeration cycle.
- the refrigerant compressed by the compressor (20) releases heat to the air in the radiator (2).
- the refrigerant that has released heat is decompressed by the decompression mechanism (3) and evaporated in the evaporator (4).
- the evaporated refrigerant is sucked into the compressor (20).
- the refrigerator (1) is an air conditioner.
- the air conditioner may be a cooling-only machine, a heating-only machine, or an air conditioner that switches between cooling and heating.
- the air conditioner has a switching mechanism (for example, a four-way switching valve) that switches the circulation direction of the refrigerant.
- the refrigerating device (1) may be a water heater, a chiller unit, a cooling device for cooling the air inside the refrigerator, or the like. Chillers cool the air inside refrigerators, freezers, containers, and the like.
- the expansion mechanism consists of an electronic expansion valve, a temperature sensitive expansion valve, an expander, or a capillary tube.
- FIG. 2 is a schematic longitudinal sectional view of the compressor (20).
- the compressor (20) of this example is a single-stage type having one compression mechanism (50).
- the compressor (20) has a casing (21), a motor (30), a shaft (40) and a compression mechanism (50).
- a casing (21) houses a motor (30), a shaft (40) and a compression mechanism (50).
- the compressor (20) has a bearing member that supports the shaft (40).
- the bearing members have a first radial bearing member (61), a second radial bearing member (62) and a thrust bearing member (63).
- the casing (21) has a body (22), a first closing portion (23), and a second closing portion (24).
- the body (22) is formed in a tubular shape with both ends in the axial direction open.
- the first closing portion (23) closes the open portion on one axial end side of the body portion (22).
- the first closure (23) includes a housing (25) located in its center.
- the second closing portion (24) closes the open portion on the other axial end side of the body portion (22).
- the motor (30) has a stator (31) and a rotor (32).
- the stator (31) is cylindrical.
- the stator (31) is fixed to the inner peripheral surface of the body (22) of the casing (21).
- the rotor (32) is provided inside the stator (31).
- the motor (30) has its operating frequency (rotational speed) adjusted by an inverter device.
- the compressor (20) is of a variable rotation speed inverter type. Therefore, the rotation speed of the motor (30) varies from a relatively low rotation speed to a relatively high rotation speed.
- the shaft (40) is fixed to the axial center of the rotor (32).
- the shaft (40) is rotationally driven by a motor (30).
- the shaft (40) extends along the axial direction of the casing (21).
- the shaft (40) has a first end (41) and a second end (42).
- the first end (41) is the end on the impeller (51) side, and the second end (42) is the end on the side opposite to the impeller (51).
- a thrust plate (43) is provided on the shaft (40) of this example.
- the thrust plate (43) may be formed integrally with the main body (40a) of the shaft (40), or may be configured as a separate part from the main body (40a) of the shaft (40).
- the thrust plate (43) of this example is provided near the first end (41).
- the thrust plate (43) is shaped like a disk extending radially outward from the main body (40a) of the shaft (40).
- the compressor (20) of this example has two radial bearing members (61, 62).
- the number and location of radial bearing members (61, 62) are merely exemplary.
- the first radial bearing member (61) is arranged near the first end (41) of the shaft (40).
- the first radial bearing member (61) is fixed to the body (22) of the casing (21).
- a tubular first radial bearing (61a) is formed at the axial center of the first radial bearing member (61).
- the first radial bearing (61a) rotatably supports the shaft (40).
- the second radial bearing member (62) is arranged near the second end (42) of the shaft (40).
- the second radial bearing member (62) is fixed to the body (22) of the casing (21).
- a tubular second radial bearing (62a) is formed at the axial center of the second radial bearing member (62).
- the second radial bearing (62a) rotatably supports the shaft (40).
- the thrust bearing member (63) is fixed to the central portion of the first radial bearing member (61).
- the thrust bearing member (63) is located near the first end (41) of the shaft (40).
- a thrust bearing (63a) is formed that is in sliding contact with the thrust plate (43). The thrust bearing (63a) restricts axial movement of the shaft (40).
- the compression mechanism (50) is a centrifugal compression mechanism that imparts kinetic energy to the fluid by the centrifugal force of the impeller (51) and converts this kinetic energy into pressure.
- the compression mechanism (50) includes a housing (25) and an impeller (51).
- the impeller (51) includes a disk portion (52), a shaft portion (53) extending axially inside the main body of the impeller (51), and a shaft portion (53) extending along the disk portion (52) and the shaft portion (53).
- a plurality of vanes (54) are formed (see FIG. 3).
- a compression chamber (55) is formed between the housing (25) and the impeller (51).
- the housing (25) is formed with a suction passageway (56) for sending fluid (refrigerant) to the compression chamber (55).
- the compressor (20) has a connecting portion (70).
- the connecting portion (70) connects the first end (41) of the shaft (40) and the impeller (51) (strictly, the shaft portion (53) of the impeller (51)).
- the connecting portion (70) and its peripheral structure will be described in detail with reference to FIGS. 3 to 5.
- FIG. The connecting portion (70) has a base (71), a protrusion (72), and a connecting shaft (73).
- the base (71) has a first surface (71a) and a second surface (71b).
- the first surface (71a) faces the impeller (51).
- the second surface (71b) faces the shaft (40).
- the base (71) is formed in a substantially columnar shape. Strictly speaking, the base (71) is formed in a truncated cone shape in which the diameter of the first surface (71a) is larger than the diameter of the second surface (71b).
- the base (71) has a first tapered portion (71c) whose outer diameter decreases from the first surface (71a) toward the second surface (71b).
- a first recess (44) into which the base (71) is fitted is formed in the first end (41) of the shaft (40).
- a truncated conical space corresponding to the base (71) is formed inside the first recess (44).
- the protrusion (72) protrudes from the second surface (71b) of the base (71) toward the shaft (40).
- the protrusion (72) is formed in a cylindrical shape.
- a first fitting hole (45) continuous with the first recess (44) is formed in the first end (41) of the shaft (40).
- the first fitting hole (45) extends from the bottom of the first recess (44) through the axis of the shaft (40).
- the protrusion (72) fits into the first fitting hole (45).
- the axial length of the first fitting hole (45) is greater than the axial length of the protrusion (72).
- connection shaft (73) extends from the first surface (71a) of the base (71) toward the impeller (51).
- the connecting shaft (73) has a tubular portion (73a) and a second tapered portion (73b).
- the cylindrical portion (73a) extends axially continuously with the base portion (71).
- the cylindrical portion (73a) has an outer diameter smaller than that of the shaft (40).
- the second tapered portion (73b) decreases in outer diameter toward the impeller (51).
- the impeller (51) has a second recessed portion (57) formed in the axial center portion of the back surface of the disk portion (52).
- the second tapered portion (73b) fits into the second concave portion (57).
- a truncated conical space corresponding to the second tapered portion (73b) is formed inside the second recessed portion (57).
- a third fitting hole (74) is formed in the tubular portion (73a).
- the third fitting hole (74) extends axially from the tip of the second tapered portion (73b) to the base portion (71).
- the shaft (53) of the impeller (51) fits into the third fitting hole (74).
- the shaft portion (53) passes through the axial center of the main body of the impeller (51) and protrudes further toward the shaft (40) than the disc portion (52).
- the shaft (53) is fixed to the housing (25) side end of the body of the impeller (51).
- the tubular portion (73a) constitutes an attachment portion to which the weight component (85) is attached.
- the cylindrical portion (73a) is formed with a plurality of holes (81) which will be detailed later.
- the shaft (40), the connecting shaft (73), and the impeller (51) are composed of separate parts. be done.
- the shaft (40) is made of a ferrous material.
- the connecting portion (70) is made of an aluminum-based material.
- the impeller (51) is made of an aluminum-based material.
- the density of the shaft (40) is greater than the density of the joint (70).
- the density of the shaft (40) is greater than that of the impeller (51).
- the density of the connecting portion (70) and the density of the impeller (51) are approximately equal.
- the rigidity of the shaft (40) is higher than that of the connecting portion (70) and the impeller (51). In the compressor (20) of this example, the rigidity of the shaft (40) is increased, and the weight of the connecting portion (70) and the impeller (51) is reduced.
- the compressor (20) has a balance adjustment mechanism (80).
- the balance adjustment mechanism (80) adjusts the weight balance during operation of the compressor (20).
- the balance adjustment mechanism (80) of this example includes a plurality of holes (81) and a weight component (85) attached to an arbitrary hole (81) of the plurality of holes (81).
- a plurality of holes (81) are formed in the connecting portion (70). Specifically, the plurality of holes (81) are formed in the outer peripheral surface of the cylindrical portion (73a). The plurality of holes (81) are positioned to be exposed to the space inside the casing (21). A female screw portion (82) is formed on the inner peripheral surface of the hole (81). In other words, a weight component (85) having an external thread (86) is fastened to the hole (81).
- the plurality of holes (81) in this example includes a plurality of (eg, 10) first holes (81A), a plurality of (eg, 10) second holes (81B), and a plurality of (eg, 10) third holes (81C).
- the plurality of first holes (81A) are arranged in the circumferential direction on the outer peripheral surface of the cylindrical portion (73a).
- the plurality of first holes (81A) are arranged at regular intervals.
- the plurality of second holes (81B) are arranged in the circumferential direction on the outer peripheral surface of the cylindrical portion (73a).
- the plurality of second holes (81B) are arranged at regular intervals.
- the plurality of third holes (81C) are arranged in the circumferential direction on the outer peripheral surface of the cylindrical portion (73a).
- the plurality of first holes (81A) are arranged at regular intervals.
- a plurality of first holes (81A) constitute a first row group (L1).
- a plurality of second holes (81B) constitute a second row group (L2).
- a plurality of third holes (81C) constitute a third row group (L3).
- a first row group (L1), a second row group (L2), and a third row group (L3) are axially arranged in the coupling portion (70) (strictly speaking, the cylindrical portion (73a)). .
- the first row group (L1) is positioned closer to the shaft (40)
- the third row group (L3) is positioned closer to the impeller (51)
- the second row group (L2) is positioned closer to the first row group (L1 ) and the third column group (L3).
- the number of first holes (81A) in the first row group (L1) and the number of second holes (81B) in the second row group (L2) are preferably the same.
- the first holes (81A) of the first row group (L1) and the second holes (81B) of the second row group (L2) preferably overlap each other when viewed in the axial direction.
- the first holes (81A) of the first row group (L1) and the second holes (81B) of the second row group (L2) preferably have the same structure.
- the number of second holes (81B) in the second row group (L2) and the number of third holes (81C) in the third row group (L3) are preferably the same.
- the second holes (81B) of the second row group (L2) and the third holes (81C) of the third row group (L3) preferably overlap each other when viewed in the axial direction.
- the second holes (81B) of the second row group (L2) and the third holes (81C) of the third row group (L3) preferably have the same structure.
- the weight component (85) of this example is a weight having a male screw portion (86).
- the weight part (85) is composed of a so-called "pot screw”.
- a square hole (87) into which a tool such as a hexagonal wrench is fitted is formed in the head of the weight component (85).
- the operator fits the tool into each hole (81) and rotates the weight component (85).
- the male threaded portion (86) of the weight component (85) is fastened to the female threaded portion (82) of the hole (81), and the weight component (85) is attached to the hole (81).
- Plate member A plate member (90) as a sealing member is provided in the vicinity of the compression mechanism (50). It constitutes the first member (90) of the present disclosure.
- the plate member (90) of this example is formed in an annular shape with a through hole (91) formed in the axial direction.
- the plate member (90) is supported by the first closing portion (23) so as to face the rear surface of the disk portion (52) of the impeller (51).
- the connecting portion (70) penetrates the through hole (91) of the plate member (90). Specifically, the tubular portion (73a) of the connecting portion (70) passes through the through hole (91). In other words, the cylindrical portion (73a) forms a portion of the connecting portion (70) surrounded by the first member (90).
- a gap (G) is formed between the plate member (90) and the cylindrical portion (73a).
- the gap (G) is formed in a tubular shape.
- the fluid is agitated as the connecting portion (70) rotates. Thereby, a seal portion is formed in the gap (G) by the fluid flow.
- the fluid in the compression chamber (55) can be prevented from leaking into the space on the motor (30) side through the gap (G).
- the operator attaches the connecting part (70) to the first end (41) of the shaft (40). Specifically, the operator fits the protrusion (72) of the connecting part (70) into the first fitting hole (45) of the first end (41). Press fitting, shrink fitting, welding, adhesion, or the like can be used as a method for fixing the connecting portion (70) to the first end (41) of the shaft (40).
- the operator balances the unit in which the shaft (40) and the connecting portion (70) are fixed. Specifically, the operator attaches the weight component (85) to a predetermined hole (81) among the plurality of holes (81) formed in the connecting portion (70). Thereby, the substantial weight in the circumferential direction or axial direction of the shaft (40) can be adjusted.
- the worker inserts the tubular portion (73a) of the connecting portion (70) into the through hole (91) of the plate member (90).
- the second tapered portion (73b) of the connecting portion (70) protrudes further to the tip side than the plate member (90). Since the connecting portion (70) and the impeller (51) are separate members, the plate member (90) can be positioned around the connecting portion (70) without dividing the plate member (90). Note that when the cylindrical portion (73a) is inserted into the through hole (91), the weight component (85) is positioned so as not to interfere with the inner peripheral surface of the through hole (91).
- the worker attaches the impeller (51) to the connecting portion (70).
- the impeller (51) is a component separate from the shaft (40) and the connecting portion (70). Therefore, the balance of the impeller (51) can be adjusted by the impeller (51) alone.
- the balance adjustment of the impeller (51) is performed by an operator at a predetermined timing before the fourth step.
- an operator fits the shaft portion (53) of the impeller (51) into the third fitting hole (74) of the cylindrical portion (73a).
- press fitting, shrink fitting, welding, adhesion, or the like can be used as a method for fixing the connection portion (70) and the impeller (51).
- a balance adjustment mechanism (80) is provided in the connecting portion (70) connecting the first end (41) of the shaft (40) and the impeller (51). If a weight for balance adjustment or the like is attached to the impeller (51), the thickness of the disk portion (52) of the impeller (51) increases and the weight of the impeller (51) increases. growing. Since the impeller (51) is located farthest from the shaft (40), the greater the weight of the impeller (51), the greater the bending moment acting on the shaft (40), causing the shaft (40) to It becomes easy to bend. As a result, since the shaft (40) cannot be rotated at high speed, the maximum number of revolutions of the compressor (20) is reduced and the operating range of the compressor (20) is narrowed.
- the shaft (40), the connecting portion (70) and the impeller (51) are separate parts. Therefore, the balance can be adjusted only by the unit in which the shaft (40) and the connecting portion (70) are assembled.
- the impeller (51) can be individually balanced while being separated from the shaft (40) and the connecting portion (70). As a result, the final balance can be accurately adjusted in the assembled unit of the shaft (40), the connecting portion (70), and the impeller (51).
- connection part (70) and the impeller (51) By making the connection part (70) and the impeller (51) separate parts, the impeller is attached to the connection part (70) after the connection part (70) is inserted into the through hole (91) of the plate member (90). (51) can be attached. Therefore, the plate member (90) can be positioned around the connecting portion (70) without dividing the plate member (90). This simplifies the structure of the plate member (90).
- the density of the joint (70) is less than the density of the shaft (40). Therefore, the weight of the connecting portion (70) can be reduced, thereby suppressing an increase in the bending moment acting on the shaft (40) due to the connecting portion (70). Thereby, bending of the shaft (40) can be suppressed, and the shaft (40) can be rotated at high speed.
- the density of the impeller (51) is less than that of the shaft (40). This further reduces the weight of the impeller (51), thereby suppressing an increase in the bending moment acting on the shaft (40) due to the impeller (51).
- the balance adjustment mechanism (80) comprises a plurality of holes (81) formed in the connecting portion (70) and weight parts (85) attached to predetermined holes (81) of the plurality of holes (81). include. By attaching the weight component (85) to a predetermined hole (81) among the plurality of holes (81), balance adjustment can be easily performed.
- a plurality of holes (81) are arranged in the circumferential direction of the connecting portion (70). Therefore, it is possible to easily adjust the substantial weight distribution in the circumferential direction of the shaft (40).
- a row group (L1, L2, L3) consisting of a plurality of holes are arranged in the axial direction of the shaft (40). This candy facilitates adjustment of the substantial weight distribution in the axial direction of the shaft (40).
- a plate member (90) as a first member is provided with a gap (G) interposed between the outer peripheral surface of the connecting portion (70) and the plate member (90).
- the fluid is agitated as the connecting portion (70) rotates.
- a seal portion can be formed by fluid flow.
- the fluid compressed in the compression chamber (55) can be prevented from leaking into the space on the motor (30) side.
- the weight component (85) is attached to the outer peripheral surface of the cylindrical portion (73a) of the connecting portion (70). Therefore, when the connecting portion (70) rotates, the weight component (85) can promote agitation of the fluid. As a result, the sealing performance of the sealing portion in the gap (G) can be improved.
- a portion of the connecting portion (70) surrounded by the plate member (90) (that is, the cylindrical portion (73a)) has a smaller outer diameter than the shaft (40). Therefore, the area of the gap between the cylindrical portion (73a) and the plate member (90) can be reduced, thereby preventing the fluid compressed in the compression chamber (55) from leaking into the space on the motor (30) side. can be suppressed.
- the thrust plate (43) may be formed integrally with the connection portion (70). In this case, the weight of the thrust plate (43) can be reduced.
- the connecting portion (70) and the impeller (51) may be configured as one component, and this component may be separate from the shaft (40). In this case, it is preferable that the density of the unit including the connecting portion (70) and the impeller (51) is lower than the density of the shaft (40).
- the shaft (40), the connecting portion (70) and the impeller (51) may be integrated.
- the weight component (85) may be fixed to the connection portion (70) by a fixing method other than fastening (for example, press fitting, shrink fitting, welding, adhesion, etc.).
- the plurality of holes (81) may be arranged in only one row in the axial direction. The plurality of holes (81) do not necessarily have to be arranged in the circumferential direction.
- the configuration relating to the connecting portion (70) of the present disclosure may be applied to a two-stage turbo compressor (20) having two compression mechanisms (50). good.
- the configuration relating to the connecting portion of the present disclosure may be employed in turbo fluid machines other than the turbo compressor (20). Specifically, this configuration may be employed in a turbocharger provided in a vehicle or the like.
- the present disclosure is useful for turbo fluid machines and refrigeration systems.
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Abstract
Description
以下、本開示の実施形態について、図面を参照しながら詳細に説明する。なお、本開示は、以下に示される実施形態に限定されるものではなく、本開示の技術的思想を逸脱しない範囲内で各種の変更が可能である。各図面は、本開示を概念的に説明するためのものであるから、理解の容易のために必要に応じて寸法、比、または数を、誇張あるいは簡略化して表す場合がある。
図1に示す冷凍装置(1)は、本開示のターボ式圧縮機(以下、圧縮機(20)ともいう)を備える。冷凍装置(1)は、冷媒が充填された冷媒回路(1a)を有する。冷媒回路(1a)は、圧縮機(20)、放熱器(2)、減圧機構(3)、および蒸発器(4)を有する。減圧機構(3)は、膨張弁である。冷媒回路(1a)は、蒸気圧縮式の冷凍サイクルを行う。
図2を参照しながら圧縮機(20)の概要について説明する。図2は、圧縮機(20)の概略の縦断面図である。本例の圧縮機(20)は、1つの圧縮機構(50)を有する単段式である。圧縮機(20)は、ケーシング(21)、モータ(30)、軸(40)、および圧縮機構(50)を有する。ケーシング(21)は、モータ(30)、軸(40)、および圧縮機構(50)を収容する。圧縮機(20)は、軸(40)を支える軸受け部材を有する。軸受け部材は、第1ラジアル軸受け部材(61)、第2ラジアル軸受け部材(62)、およびスラスト軸受け部材(63)を有する。
ケーシング(21)は、胴部(22)と、第1閉塞部(23)と、第2閉塞部(24)とを有する。胴部(22)は、軸方向の両端が開放する筒状に形成される。第1閉塞部(23)は、胴部(22)の軸方向の一端側の開放部を閉塞する。第1閉塞部(23)は、その中央に位置するハウジング(25)を含む。第2閉塞部(24)は、胴部(22)の軸方向の他端側の開放部を閉塞する。
モータ(30)は、固定子(31)と回転子(32)とを有する。固定子(31)は、筒状に形成される。固定子(31)は、ケーシング(21)の胴部(22)の内周面に固定される。回転子(32)は、固定子(31)の内部に設けられる。モータ(30)は、インバータ装置によって運転周波数(回転数)が調節される。言い換えると、圧縮機(20)は、回転数が可変なインバータ式である。このため、モータ(30)の回転数は、比較的低速の回転数から比較的高速の回転数までの間で変化する。
軸(40)は、回転子(32)の軸心に固定される。軸(40)は、モータ(30)によって回転駆動される。軸(40)は、ケーシング(21)の軸方向に沿って延びる。軸(40)は、第1端部(41)と第2端部(42)とを有する。第1端部(41)は、羽根車(51)側の端部であり、第2端部(42)は羽根車(51)と反対側の端部である。
本例の圧縮機(20)は、2つのラジアル軸受け部材(61,62)を有する。ラジアル軸受け部材(61,62)の数、および位置は単なる一例である。
スラスト軸受け部材(63)は、第1ラジアル軸受け部材(61)の中央部に固定される。スラスト軸受け部材(63)は、軸(40)の第1端部(41)寄りに位置する。スラスト軸受け部材(63)の内部は、スラストプレート(43)と摺接するスラスト軸受け(63a)が形成される。スラスト軸受け(63a)は、軸(40)の軸方向の移動を規制する。
圧縮機構(50)は、羽根車(51)の遠心力により流体に運動エネルギーを与え、この運動エネルギーを圧力に変換する遠心式の圧縮機構である。圧縮機構(50)は、ハウジング(25)および羽根車(51)を含む。羽根車(51)は、ディスク部(52)と、羽根車(51)の本体の内部を軸方向に延びる軸部(53)と、ディスク部(52)および軸部(53)に沿うように形成される複数の羽根(54)とを有する(図3を参照)。圧縮機構(50)では、ハウジング(25)と羽根車(51)との間に圧縮室(55)が形成される。ハウジング(25)には、流体(冷媒)を圧縮室(55)に送る吸入通路(56)が形成される。
圧縮機(20)は、連結部(70)を有する。連結部(70)は、軸(40)の第1端部(41)と羽根車(51)(厳密には、羽根車(51)の軸部(53))とを連結する。連結部(70)、およびその周辺構造について、図3~図5を参照しながら詳細に説明する。連結部(70)は、基部(71)と、突起部(72)と、連結軸(73)とを有する。
基部(71)は、第1面(71a)と第2面(71b)とを有する。第1面(71a)は、羽根車(51)側を向く面である。第2面(71b)は、軸(40)側を向く面である。基部(71)は、略円柱状に形成される。厳密には、基部(71)は、第1面(71a)の径が第2面(71b)の径よりも大きい円錐台状に形成される。基部(71)は、第1面(71a)から第2面(71b)に向かうにつれて外径を縮小させる第1テーパ部(71c)を有する。
突起部(72)は、基部(71)の第2面(71b)から軸(40)側に向かって突出する。突起部(72)は、円柱状に形成される。軸(40)の第1端部(41)には、第1凹部(44)と連続する第1嵌合穴(45)が形成される。第1嵌合穴(45)は、第1凹部(44)の底から軸(40)の軸心を通るように延びている。第1嵌合穴(45)には、突起部(72)が嵌合する。本例では、第1嵌合穴(45)の軸方向の長さが、突起部(72)の軸方向の長さよりも大きい。
連結軸(73)は、基部(71)の第1面(71a)から羽根車(51)側に向かって延びる。連結軸(73)は、筒部(73a)と、第2テーパ部(73b)とを有する。筒部(73a)は、基部(71)と連続して軸方向に延びる。筒部(73a)の外径は、軸(40)の外径よりも小さい。第2テーパ部(73b)は、羽根車(51)側に向かうにつれて外径を縮小させる。
本例の圧縮機(20)では、軸(40)と、連結軸(73)と、羽根車(51)とが別部品で構成される。軸(40)は、鉄系の材料で構成される。連結部(70)は、アルミ系の材料で構成される。羽根車(51)は、アルミ系の材料で構成される。軸(40)の密度は連結部(70)の密度よりも大きい。軸(40)の密度は羽根車(51)の密度よりも大きい。連結部(70)の密度と羽根車(51)の密度は概ね等しい。軸(40)の剛性は、連結部(70)および羽根車(51)の剛性よりも高い。本例の圧縮機(20)では、軸(40)の剛性を高めるとともに、連結部(70)および羽根車(51)の軽量化を図っている。
圧縮機(20)は、バランス調整機構(80)を備える。バランス調整機構(80)は、圧縮機(20)の運転時における重量バランスを調整する。本例のバランス調整機構(80)は、複数の穴(81)と、複数の穴(81)のうちの任意の穴(81)に取り付けられるウェイト部品(85)とを含む。
複数の穴(81)は、連結部(70)に形成される。具体的には、複数の穴(81)は、筒部(73a)の外周面に形成される。複数の穴(81)は、ケーシング(21)の内部の空間に露出する位置にある。穴(81)の内周面には、雌ネジ部(82)が形成される。言い換えると、穴(81)には、雄ネジ部(86)を有するウェイト部品(85)が締結される。
本例のウェイト部品(85)は、雄ネジ部(86)を有する錘である。ウェイト部品(85)は、いわゆる“イモねじ”によって構成される。ウェイト部品(85)の頭部には、六角レンチなどの工具が嵌合する角穴(87)が形成される。作業者は、所定の穴(81)にウェイト部品(85)を差し込んだ後、工具を各穴(81)に嵌合させ、ウェイト部品(85)を回転させる。これにより、ウェイト部品(85)の雄ネジ部(86)が穴(81)の雌ネジ部(82)に締結され、ウェイト部品(85)が穴(81)に取り付けられる。
圧縮機構(50)の近傍には、シール部材であるプレート部材(90)が設けられる。本開示の第1部材(90)を構成する。本例のプレート部材(90)は、軸方向に貫通穴(91)が形成された環状に形成される。プレート部材(90)は、羽根車(51)のディスク部(52)の背面と対向するように、第1閉塞部(23)に支持される。
圧縮機(20)の運転時には、モータ(30)が通電状態となる。これにより、軸(40)が回転する。軸(40)が回転すると、軸(40)と連結する羽根車(51)が回転する。羽根車(51)が回転すると、冷媒が吸入通路(56)から圧縮室(55)に流入する。圧縮室(55)では、複数の羽根(54)によって冷媒が径方向外方へ送られ、冷媒の流速が早くなる。この冷媒の速度が減速されることで、冷媒の圧力が高くなる。このようにして圧縮された冷媒は、吐出通路(図示省略)を介してケーシング(21)の外部へ送られる。圧縮機(20)から吐出された冷媒は、冷凍装置(1)の冷凍サイクルに利用される。
圧縮機(20)の組み立て時には、作業者が圧縮機(20)の重量のバランス調整を行う。圧縮機(20)の組み立て方法について図6および図7を参照しながら詳細に説明する。
(8-1)
軸(40)の第1端部(41)と、羽根車(51)とを連結する連結部(70)にバランス調整機構(80)が設けられる。仮に、羽根車(51)にバランス調整用の錘などを取り付ける場合、羽根車(51)のディスク部(52)の厚さが大きくなることなどに起因して、羽根車(51)の重量が大きくなる。羽根車(51)は、軸(40)に対して最も遠い位置にあるため、羽根車(51)の重量が大きくなると、軸(40)に作用する曲げモーメントが増大し、軸(40)が撓み易くなる。この結果、軸(40)を高速回転させることができないため、圧縮機(20)の最高回転数が小さくなり、圧縮機(20)の運転範囲が狭くなってしまう。
軸(40)と、連結部(70)と、羽根車(51)とは別部品である。このため、軸(40)と連結部(70)とを組み付けたユニットだけで、バランスを調整できる。羽根車(51)は、軸(40)および連結部(70)と切り離した状態で、個別にバランスを調整できる。この結果、軸(40)、連結部(70)、および羽根車(51)を組み立てたユニットにおいて、最終的に精度よくバランスを調整できる。
連結部(70)の密度は軸(40)の密度よりも小さい。このため、連結部(70)を軽量化できるので、連結部(70)に起因して軸(40)に作用する曲げモーメントが増大することを抑制できる。これにより、軸(40)の撓みを抑制でき、軸(40)を高速回転させることができる。
羽根車(51)の密度は軸(40)の密度よりも小さい。このため、羽根車(51)をさらに軽量化できるので、羽根車(51)に起因して軸(40)に作用する曲げモーメントが増大することを抑制できる。
バランス調整機構(80)は、連結部(70)に形成される複数の穴(81)と、複数の穴(81)のうちの所定の穴(81)に取り付けられるウェイト部品(85)とを含む。複数の穴(81)のうちの所定の穴(81)にウェイト部品(85)を取り付けることで、バランス調整を容易に行うことができる。
連結部(70)では、複数の穴(81)が該連結部(70)の周方向に配列される。このため、軸(40)の周方向における実質的な重量の分布を容易に調整できる。
連結部(70)では、複数の穴からなる列群(L1,L2,L3)が軸(40)の軸方向に配列される。このあめ、軸(40)の軸方向における実質的な重量の分布を容易に調整でいる。
連結部(70)の外周面と隙間(G)を介して配置される第1部材としてのプレート部材(90)を備えている。プレート部材(90)と連結部(70)との間の隙間(G)では、連結部(70)の回転に伴い流体が攪拌される。これにより、隙間(G)では、流体流れによってシール部を形成できる。その結果、圧縮室(55)で圧縮された流体が、モータ(30)側の空間に漏れてしまうことを抑制できる。
連結部(70)のうちプレート部材(90)に囲まれる部分(即ち、筒部(73a))の外径は、軸(40)の外径よりも小さい。このため、筒部(73a)とプレート部材(90)の間の隙間の面積を小さくできるので、圧縮室(55)で圧縮された流体が、モータ(30)側の空間に漏れてしまうことを抑制できる。
上記実施形態については以下のような変形例としてもよい。なお、以下の説明では、原則として実施形態と異なる点について説明する。
図8に示すように、連結部(70)にスラストプレート(43)を一体に形成してもよい。この場合、スラストプレート(43)を軽量化できる。連結部(70)と羽根車(51)とを1つの部品により構成し、この部品を軸(40)と別体としてもよい。この場合、連結部(70)および羽根車(51)を含むユニットの密度を、軸(40)の密度よりも小さくする野が好ましい。軸(40)と連結部(70)と羽根車(51)とを一体の部品としてもよい。
ウェイト部品(85)は、締結以外の固定方法(例えば圧入、焼き嵌め、溶接、接着など)により、連結部(70)に固定されてもよい。複数の穴(81)は、軸方向において一列のみ配列されてもよい。複数の穴(81)は、必ずしも周方向に配列されていなくてもよい。
本開示の連結部(70)に関する構成は、2つの圧縮機構(50)を有する二段式のターボ式圧縮機(20)に適用されてもよい。本開示の連結部に関する構成は、ターボ式圧縮機(20)以外のターボ式流体機械に採用されてもよい。具体的には、本構成は、車両などに設けられるターボチャージャーに採用されてもよい。
20 圧縮機(ターボ式流体機械)
40 軸
50 圧縮機構
51 羽根車
70 連結部
73a 筒部(部分)
80 バランス調整機構
81 穴
85 ウェイト部品
90 プレート部材(第1部材)
G 隙間
L1 第1列群
L2 第2列群
Claims (9)
- 回転駆動される軸(40)と、
羽根車(51)を有する圧縮機構(50)と、
前記軸(40)の端部と前記羽根車(51)とを連結する連結部(70)とを備え、
前記連結部(70)には、バランス調整機構(80)が設けられる
ターボ式流体機械。 - 前記軸(40)と、前記連結部(70)と、前記羽根車(51)とは別部品で構成される
請求項1に記載のターボ式流体機械。 - 前記連結部(70)の密度は、前記軸(40)の密度よりも小さい
請求項2に記載のターボ式流体機械。 - 前記バランス調整機構(80)は、
前記連結部(70)に形成される複数の穴(81)と、
前記複数の穴(81)のうちの所定の穴(81)に取り付けられるウェイト部品(85)とを含む
請求項1~3のいずれか1つに記載のターボ式流体機械。 - 前記連結部(70)では、複数の穴(81)が該連結部(70)の周方向に配列される
請求項4に記載のターボ式流体機械。 - 前記連結部(70)には、前記連結部(70)の周方向に配列される複数の穴(81)からなる第1列群(L1)と第2列群(L2)とが形成され、
前記第1列群(L1)と前記第2列群(L2)とは、前記連結部(70)の軸方向に配列される
請求項5に記載のターボ式流体機械。 - 前記連結部(70)の外周面と隙間(G)を空けて配置される第1部材(90)を備えている
請求項1~6のいずれか1つに記載のターボ式流体機械。 - 前記連結部(70)のうち第1部材(90)に囲まれる部分(73a)の外径が、前記軸(40)の外径よりも小さい
請求項7に記載のターボ式流体機械。 - 請求項1~8のいずれか1つに記載のターボ式流体機械を備えた冷凍装置。
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP22837353.6A EP4336047A1 (en) | 2021-07-05 | 2022-05-26 | Turbo-type fluid machine and refrigeration apparatus |
CN202280046359.5A CN117581024A (zh) | 2021-07-05 | 2022-05-26 | 涡轮式流体机械及制冷装置 |
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JP2021-111530 | 2021-07-05 | ||
JP2021111530A JP7269507B2 (ja) | 2021-07-05 | 2021-07-05 | ターボ式流体機械、および冷凍装置 |
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US18/403,038 Continuation US20240133393A1 (en) | 2021-07-04 | 2024-01-03 | Turbo-type fluid machine and refrigeration apparatus |
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WO2023281932A1 true WO2023281932A1 (ja) | 2023-01-12 |
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Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6082600U (ja) * | 1983-11-07 | 1985-06-07 | 株式会社荏原製作所 | タ−ボ型気体機械の羽根車軸 |
JPH0319401U (ja) * | 1989-07-07 | 1991-02-26 | ||
JP2014088803A (ja) | 2012-10-30 | 2014-05-15 | Mitsubishi Heavy Ind Ltd | インペラ及びこれを備えた回転機械 |
CN212055252U (zh) * | 2020-03-26 | 2020-12-01 | 四川省德阳裕龙电力设备有限公司 | 一种轴向进气轴向排气离心压缩机的转子 |
-
2021
- 2021-07-05 JP JP2021111530A patent/JP7269507B2/ja active Active
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2022
- 2022-05-26 EP EP22837353.6A patent/EP4336047A1/en active Pending
- 2022-05-26 WO PCT/JP2022/021608 patent/WO2023281932A1/ja active Application Filing
- 2022-05-26 CN CN202280046359.5A patent/CN117581024A/zh active Pending
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6082600U (ja) * | 1983-11-07 | 1985-06-07 | 株式会社荏原製作所 | タ−ボ型気体機械の羽根車軸 |
JPH0319401U (ja) * | 1989-07-07 | 1991-02-26 | ||
JP2014088803A (ja) | 2012-10-30 | 2014-05-15 | Mitsubishi Heavy Ind Ltd | インペラ及びこれを備えた回転機械 |
CN212055252U (zh) * | 2020-03-26 | 2020-12-01 | 四川省德阳裕龙电力设备有限公司 | 一种轴向进气轴向排气离心压缩机的转子 |
Also Published As
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EP4336047A1 (en) | 2024-03-13 |
JP7269507B2 (ja) | 2023-05-09 |
CN117581024A (zh) | 2024-02-20 |
JP2023008179A (ja) | 2023-01-19 |
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