JP7391266B2 - Scroll compressor and refrigeration cycle equipment - Google Patents

Description

The present disclosure relates to a scroll compressor and a refrigeration cycle device having a balance weight.

In a scroll compressor, during operation, the refrigerating machine oil in the oil sump of the closed container passes through the oil supply path of the drive shaft, supplies oil to each bearing and sliding part, lubricates these, and then returns to the oil sump. It has become. The refrigerating machine oil circulates inside the sealed container together with the refrigerant, and some of the refrigerating machine oil returns to the oil reservoir, while some of the refrigerating machine oil goes to the discharge pipe together with the refrigerant and is discharged to the outside of the sealed container. If a large amount of so-called refrigeration oil is discharged outside the sealed container, the amount of refrigeration oil held in the oil sump will decrease, and the amount of oil supplied to each bearing and sliding part will decrease. Refrigerating machine oil runs out. When refrigerating machine oil is depleted, abnormal wear or adhesion occurs in each bearing and sliding part, reducing reliability.

Therefore, in conventional scroll compressors, the following techniques are known as techniques for reducing the amount of refrigerating machine oil carried out to the outside of the compressor.

Patent Document 1 discloses a compression mechanism unit that compresses a refrigerant, an electric motor that has a rotor and a stator and drives the compression mechanism unit, a drive shaft that transmits the rotational force of the rotor to the compression mechanism unit, and a compression mechanism. A balance weight (see FIG. 8, which will be described later) is located between the drive shaft and the rotor and is fixed to the drive shaft. In Patent Document 1, the balance weight has a function of reducing the amount of refrigerating machine oil taken out, and the height of the balance weight in the drive shaft direction is set closer to the compression mechanism than the end of the end coil of the stator of the electric motor. It has a prominent height. A semi-cylindrical space for receiving a mixed gas of refrigerant and refrigerating machine oil is formed within the balance weight, and an oil discharge portion that penetrates in the radial direction is provided in the inner wall portion forming the space. The mixed gas received in the internal space of the balance weight is discharged from the oil discharge section to the outside of the balance weight and collides with the end coil or the like. By separating a portion of the refrigerating machine oil contained in the mixed gas due to this collision, the refrigerant gas is suppressed from being taken out of the compressor together with the refrigerating machine oil.

JP 2016-31024 Publication

In the balance weight of Patent Document 1, the internal space of the balance weight is open in the axial direction of the drive shaft. Therefore, the mixed gas that passes through the gap between the drive shaft and the rotor and flows into the internal space of the balance weight from the axial direction does not flow toward the oil discharge part, but instead flows in the axial direction and is discharged to the outside of the balance weight. and may even be discharged outside the compressor. In this case, there was a problem in that the effect of reducing the amount of refrigerating machine oil carried out could not be sufficiently obtained.

The present disclosure has been made to solve the above-mentioned problems, and aims to provide a scroll compressor and a refrigeration cycle device that can reduce the amount of refrigerating machine oil taken out.

A scroll compressor according to the present disclosure includes an airtight container, a compression mechanism section arranged in the airtight container that compresses a refrigerant, a rotor and a stator, an electric motor that drives the compression mechanism section, and a rotor. a drive shaft that transmits rotational force to the compression mechanism; a first balance weight that is arranged between the compression mechanism and the electric motor and fixed to the rotor; a first cup-shaped member having a surrounding cylindrical circumferential surface portion; the first balance weight has an arc-shaped lightweight portion; and an arc-shaped weight portion heavier than the lightweight portion; The child includes a plurality of through passages formed by through holes extending in the axial direction of the drive shaft, and among the plurality of through passages, the through passage is located in an area that overlaps with the weight part when viewed in the axial direction. When referring to the heavy part side through flow path and the other parts as the light weight part side through flow path, the light weight part side through flow path communicates with the internal space of the first cup-shaped member, and the peripheral surface of the first cup-shaped member is The lightweight part side has a first discharge part for discharging the refrigerating machine oil in the first cup-shaped member, and the heavy part of the first balance weight has one end on the upstream side communicating with the heavy part side through flow path, and the downstream The other end of the side is a hole that communicates with the outer circumferential surface of the weight part, and the radial flow passage hole changes the flow direction of the refrigerant containing refrigerant oil that has passed through the weight part side passage from the axial direction to the radial direction. The circumferential surface of the first cup-shaped member has a hole that radially penetrates the circumferential surface at a position opposite to the other end on the downstream side of the radial flow path hole, It has a second discharge part that discharges the coolant to the outside of the first cup-shaped member.

A refrigeration cycle device according to the present disclosure includes a scroll compressor, an outdoor heat exchanger, a pressure reducer, and an indoor heat exchanger.

According to the present disclosure, the flow direction of the refrigerant gas that has passed through the weight section side through flow path is changed from the axial direction to the radial direction by the radial flow path hole. Therefore, compared to the case where the refrigerant gas flows in the axial direction and is discharged to the outside from the opening of the first cup-shaped member, the amount of refrigerating machine oil taken out can be reduced.

1 is a schematic longitudinal sectional view of a scroll compressor according to Embodiment 1. FIG. FIG. 2 is a schematic cross-sectional view showing a first flow path provided on the outer periphery of the guide frame of FIG. 1. FIG. FIG. 2 is a schematic cross-sectional view of the stator of the electric motor of FIG. 1; 2 is a diagram showing a rotor of the electric motor of FIG. 1. FIG. FIG. 3 is a diagram showing a rotor, a first balance weight, and a first cup-shaped member of the scroll compressor according to the first embodiment. FIG. 3 is an explanatory diagram of an oil guide plate of an oil discharge part of the scroll compressor according to Embodiment 1. FIG. 3 is an explanatory diagram of the flow of refrigerant gas in the scroll compressor according to the first embodiment. It is a perspective view which shows the balance weight of a comparative example. FIG. 3 is a schematic plan view of a rotor, a first balance weight, and a first cup-shaped member of a scroll compressor according to a second embodiment. FIG. 7 is a schematic plan view of a rotor, a first balance weight, and a first cup-shaped member of a scroll compressor according to a third embodiment. FIG. 7 is a schematic plan view of a rotor, a first balance weight, and a first cup-shaped member of a scroll compressor according to a fourth embodiment. It is a figure which shows the rotor of the scroll compressor based on Embodiment 5, a 1st balance weight, and a 1st cup-shaped member. FIG. 7 is a diagram showing a rotor, a first balance weight, and a first cup-shaped member of a scroll compressor according to a sixth embodiment. It is a schematic block diagram of the refrigeration cycle apparatus based on Embodiment 7.

Hereinafter, embodiments of a scroll compressor according to the present disclosure will be described based on the drawings. Note that although the scroll compressor described here is an example of a vertical type, the present disclosure can also be applied to a horizontal type. Further, the following drawings including FIG. 1 are schematic representations, and the relationship in size of each component may differ from the actual one.

Embodiment 1.
FIG. 1 is a schematic vertical cross-sectional view of a scroll compressor 100 according to the first embodiment. FIG. 2 is a schematic cross-sectional view showing the first flow path 4f provided on the outer circumference of the guide frame 4 of FIG. The configuration and operation of a vertically installed scroll compressor 100 will be described based on FIGS. 1 and 2.

The scroll compressor 100 is one of the components of a refrigeration cycle used in various industrial machines such as a refrigerator, a freezer, an air conditioner, a refrigeration system, or a water heater.

The scroll compressor 100 sucks in refrigerant circulating in a refrigeration cycle, compresses it, and discharges it in a high temperature and high pressure state. This scroll compressor 100 includes a compression mechanism section 14 that compresses refrigerant, an electric motor 5 that drives the compression mechanism section 14, and a drive shaft 6 that transmits the rotational force of the electric motor 5 to the compression mechanism section 14. . The compression mechanism section 14, the electric motor 5, and the drive shaft 6 are arranged inside the closed container 10. In the case of the vertical scroll compressor 100, the compression mechanism section 14 is disposed on the upper side and the electric motor 5 is disposed on the lower side in the closed container 10, for example. In the following description, the direction in which the drive shaft 6 extends is referred to as the axial direction, the direction perpendicular to the axial direction is referred to as the radial direction, and the direction around the drive shaft is referred to as the circumferential direction.

In the closed container 10, a guide frame 4 is arranged above the electric motor 5, and a subframe 8 holding a drive shaft 6 is arranged below the electric motor 5. The guide frame 4 and subframe 8 are fixed to a closed container 10. A compliant frame 3 is housed on the inner peripheral side of the guide frame 4.

The compression mechanism section 14 includes a fixed scroll 1 and an oscillating scroll 2 that revolves (oscillates) with respect to the fixed scroll 1. The fixed scroll 1 includes a base plate portion 1a and plate-shaped spiral teeth 1b, which are spiral protrusions provided on one surface (lower side in FIG. 1) of the base plate portion 1a. The oscillating scroll 2 also includes a base plate portion 2a and a plate provided on one surface (upper side in FIG. 1) of the base plate portion 2a, which is a spiral protrusion having substantially the same shape as the plate-like spiral teeth 1b. It is composed of a spiral tooth 2b. By meshing the plate-shaped spiral teeth 1b of the fixed scroll 1 and the plate-shaped spiral teeth 2b of the oscillating scroll 2 with each other, a compression chamber 1f whose volume changes relatively is formed.

The outer peripheral portion of the fixed scroll 1 is fastened to the guide frame 4 with bolts (not shown). A suction pipe 13 is provided on the outer periphery of the base plate portion 1a of the fixed scroll 1 for introducing refrigerant gas from the suction port 1e into the compression chamber 1f via the suction check valve 1g. A discharge port 1d is formed in the center of the base plate portion 1a of the fixed scroll 1 to discharge compressed high-pressure refrigerant gas. The compressed and high-pressure refrigerant gas is then discharged into the upper space 10a within the closed container 10. The refrigerant gas discharged into the upper space 10a is led to an oil separation mechanism through a refrigerant flow path, as will be explained later, and a part of the refrigerating machine oil contained in the refrigerant gas is separated. The refrigerant gas from which the refrigerating machine oil has been separated is discharged from the discharge pipe 12 to the outside.

The oscillating scroll 2 is configured to perform a revolution movement (oscillating movement) without rotating relative to the fixed scroll 1 by an Oldham mechanism 9 for preventing rotation movement. In the Oldham mechanism 9, two fixed side keys 9a are formed on the upper surface of the annular Oldham mechanism annular part 9c, and two one pair of swing side keys 9b are formed on the lower surface of the Oldham mechanism annular part 9c. It has a configuration. A pair of Oldham guide grooves 1c are formed on the outer periphery of the base plate portion 1a of the fixed scroll 1 in substantially a straight line. A pair of fixed side keys 9a of the Oldham mechanism 9 are engaged with the Oldham guide groove 1c so as to be able to freely reciprocate and slide. Further, on the outer circumference of the base plate portion 2a of the swinging scroll 2, a pair of Oldham guide grooves 2c having a phase difference of 90 degrees with the Oldham guide groove 1c of the fixed scroll 1 are formed substantially in a straight line. There is. A pair of swing-side keys 9b of the Oldham mechanism 9 are engaged with the Oldham guide groove 2c so as to be able to freely reciprocate and slide.

The Oldham mechanism 9 configured as described above allows the swinging scroll 2 to revolve around the fixed scroll 1 without rotating. Further, a hollow cylindrical boss portion 2d is formed at the center of the surface of the oscillating scroll 2 on the opposite side (lower side in FIG. 1) from the surface on which the plate-shaped spiral teeth 2b are formed. A swing bearing 2e is arranged inside the boss portion 2d. An eccentric shaft portion (swing shaft portion) 6a provided at the upper end of the drive shaft 6 is inserted into the swing bearing 2e. The rotation of the eccentric shaft portion 6a causes the swinging scroll 2 to perform a swinging motion (eccentric rotation motion) relative to the fixed scroll 1. Further, on the opposite side (lower side in FIG. 1) of the plate-like spiral teeth 2b of the base plate portion 2a of the oscillating scroll 2, there is a thrust surface 2f that can slide in pressure contact with the thrust bearing 3a of the compliant frame 3. It is formed. Further, the base plate portion 2a of the swinging scroll 2 is provided with a bleed hole 2g that penetrates the base plate portion 2a, and has a structure in which refrigerant gas that is being compressed in the compression chamber 1f is extracted and guided to the thrust surface 2f. ing.

The compliant frame 3 is housed in the inner space of the guide frame 4. The outer peripheral portion of the compliant frame 3 has an upper cylindrical surface 3p and a lower cylindrical surface 3s. The inner peripheral surface of the guide frame 4 has an upper cylindrical surface 4c into which the upper cylindrical surface 3p of the compliant frame 3 fits, and a lower cylindrical surface 4d into which the lower cylindrical surface 3s of the compliant frame 3 fits. The compliant frame 3 is supported in the radial direction within the guide frame 4 by fitting the upper cylindrical surface 3p and the upper cylindrical surface 4c, and by fitting the lower cylindrical surface 3s and the lower cylindrical surface 4d. has been done. Further, in the center of the lower cylindrical surface 3s of the compliant frame 3, there are provided a main bearing 3c and an auxiliary main bearing 3d that radially support a drive shaft 6 that is rotationally driven by a rotor 5a of the electric motor 5. . Furthermore, the compliant frame 3 is provided with a communication hole 3e that axially penetrates the outer peripheral portion of the compliant frame 3 from within the plane of the thrust bearing 3a. A thrust bearing opening 3t, which is an opening on the upper end side of the communication hole 3e, is arranged to face the bleed hole 2g passing through the base plate portion 2a of the rocking scroll 2.

Between the compliant frame 3 and the boss portion 2d of the swinging scroll 2, a boss portion outer space 2n is provided. Further, the compliant frame 3 is provided with an intermediate pressure regulating valve space 3n. The intermediate pressure regulating valve space 3n accommodates an intermediate pressure regulating valve 3g that regulates the pressure in the boss portion outer space 2n, an intermediate pressure regulating valve holder 3h, and an intermediate pressure regulating spring 3k. The intermediate pressure regulating spring 3k is shortened from its natural length and housed in the intermediate pressure regulating valve space 3n.

A surface (reciprocating sliding surface) 3b on which the Oldham mechanism annular portion 9c makes reciprocating sliding movement is formed on the outer peripheral side of the thrust bearing 3a of the compliant frame 3. Furthermore, a communication hole 3f is formed in the compliant frame 3 so as to communicate with the inner side of the Oldham mechanism annular portion 9c, which communicates the base plate outer peripheral space 2k and the frame upper space 4a. The base plate outer peripheral space 2k is a space on the outer peripheral side of the thrust bearing 3a, that is, a space surrounded by the base plate part 2a of the swinging scroll 2 and the compliant frame 3 at the top and bottom. The frame upper space 4a is a space between the outer peripheral surface of the compliant frame 3 above the intermediate pressure regulating valve space 3n and the inner peripheral surface of the guide frame 4. The boss portion outer space 2n and the inner space of the Oldham mechanism 9 communicate with each other via the communication hole 3f, the intermediate pressure regulating valve space 3n, the frame upper space 4a, and the base plate outer peripheral space 2k. Note that in the first embodiment, the compliant frame 3 and the guide frame 4 are configured separately, but the present invention is not limited to this, and both frames may be configured as one integrated frame.

A frame lower space 4b is formed between the lower outer peripheral surface of the compliant frame 3 and the inner peripheral surface of the guide frame 4. The frame lower space 4b is partitioned at the top and bottom by ring-shaped sealing materials 7a and 7b. Here, two ring-shaped seal grooves are formed on the outer circumferential surface of the compliant frame 3 to accommodate the ring-shaped seal members 7a and 7b, but these seal grooves are formed on the inner circumferential surface of the guide frame 4. You can leave it there. The frame lower space 4b communicates only with the communication hole 3e of the compliant frame 3, and has a structure in which refrigerant gas that is being compressed and is supplied from the bleed hole 2g is sealed therein. Further, the base plate outer circumferential space 2k is a low-pressure space with a suction gas atmosphere having a suction pressure.

The guide frame 4 has its outer peripheral surface fixed to the closed container 10 by shrink fitting, welding, or the like. On the outer periphery of the guide frame 4 and the fixed scroll 1, that is, on the outer periphery of the compression mechanism section 14, a first flow path 4f formed by a notch is provided, as shown in FIG. The refrigerant gas discharged from the discharge port 1d into the upper space 10a of the closed container 10 flows downward into the closed container 10 through the first flow path 4f. The bottom of the airtight container 10 is an oil reservoir 10b in which refrigerating machine oil 11 is stored.

The closed container 10 is provided with a discharge pipe 12 for discharging refrigerant gas to the outside. The first flow path 4f is provided at a position opposite to the discharge pipe 12 in plan view. Further, below the guide frame 4, there is provided a first discharge flow path 4g that extends radially outward from the center portion of the lower end of the guide frame 4, and the first discharge flow path 4g communicates with the discharge pipe 12. Further, a discharge cover 19 is provided below the guide frame 4 so as to surround a lower cylindrical portion of the guide frame 4 having a lower cylindrical surface 4d. The discharge cover 19 penetrates in the axial direction and has an upper opening 19a and a lower opening 19b. A second discharge passage 19c is formed in the discharge cover 19 from the opening 19b to the opening 19a, and the second discharge passage 19c communicates with the first discharge passage 4g.

The electric motor 5 rotates the drive shaft 6 and includes a rotor 5 a fixed to the drive shaft 6 and a stator 5 b fixed to the closed container 10 . The rotor 5a is fixed to the drive shaft 6 by shrink fitting or the like. The outer peripheral surface of the stator 5b is fixed to the closed container 10 by shrink fitting, welding, or the like. The stator 5b is connected to a glass terminal 10c fixed to the airtight container 10 by a lead wire 5h, and receives power from the outside. When the stator 5b starts to be energized, the rotor 5a rotates, and the drive shaft 6 is driven to rotate.

The drive shaft 6 has an eccentric shaft portion 6 a forming an upper portion of the drive shaft 6 and a sub-shaft portion 6 c forming a lower portion of the drive shaft 6 . The drive shaft 6 has a main shaft portion 6b on the eccentric shaft portion 6a side and an intermediate shaft portion 6d on the secondary shaft portion 6c side between the eccentric shaft portion 6a and the counter shaft portion 6c. The eccentric shaft portion 6a is inserted into the swing bearing 2e of the swing scroll 2.

The main shaft portion 6b is rotatably supported by a main bearing 3c and an auxiliary main bearing 3d provided on the compliant frame 3. A main shaft balance weight 6h is fixed to the main shaft portion 6b by shrink fitting. The sub-shaft portion 6c is rotatably supported by a sub-bearing 8a provided on the sub-frame 8. The intermediate shaft portion 6d is fixed to the rotor 5a of the electric motor 5 by shrink fitting.

The drive shaft 6 is provided with an oil supply path 6e consisting of a hole passing through in the axial direction. The oil supply port 6f at the lower end of the oil supply path 6e is immersed in refrigerating machine oil 11 stored in an oil reservoir 10b at the bottom of the closed container 10. Therefore, the refrigerating machine oil 11 in the oil reservoir 10b is sucked up from the oil supply port 6f to the oil supply path 6e by the oil supply mechanism or pump mechanism provided at the lower part of the drive shaft 6. Since the upper end opening of the oil supply passage 6e communicates with the boss portion 2d of the swinging scroll 2, the refrigerating machine oil 11 sucked up into the oil supply passage 6e flows out from the upper end opening of the oil supply passage 6e into the boss portion 2d and is shaken. The dynamic bearing 2e, the eccentric shaft portion 6a, and the swing bearing 2e are lubricated. Further, the oil supply passage 6e is provided with an oil supply hole 6g that branches in the radial direction. Therefore, a part of the oil sucked up into the oil supply passage 6e is supplied to the auxiliary main bearing 3d from the oil supply hole 6g, and lubricates the auxiliary main bearing 3d and the main shaft portion 6b supported by the auxiliary main bearing 3d. There is. Note that the oil supply hole for the main bearing 3c is not shown in FIG. Refrigerating machine oil that has lubricated these sliding parts passes through an inflow hole 8b provided in the subframe 8 and flows into the oil reservoir 10b.

FIG. 3 is a schematic cross-sectional view of the stator 5b of the electric motor 5 in FIG.
As shown in FIG. 3, a second flow path 5g formed by a notch is provided in the outer circumference of the stator 5b. The second flow path 5g and the first flow path 4f on the outer periphery of the guide frame 4 described above are refrigerant flow paths that guide the refrigerant gas discharged from the discharge port 1d into the upper space 10a of the closed container 10 to the bottom of the closed container 10. 30 (see FIG. 1).

FIG. 4 is a diagram showing the rotor 5a of the electric motor 5 in FIG. 1. FIG. 4(a) is a schematic vertical cross-sectional view of the rotor 5a, and FIG. 4(b) is a schematic cross-sectional view (b) of the rotor 5a.

As shown in FIGS. 1 and 4, a plurality of through passages 5f are provided in the rotor 5a at intervals in the circumferential direction. The through flow path 5f is formed of a through hole passing through the rotor 5a in the axial direction. The plurality of through channels 5f are formed point-symmetrically with respect to the axis of the drive shaft 6 or symmetrically with respect to a virtual plane including the axis of the drive shaft 6. Although four through passages 5f are provided here, the number is arbitrary. Further, the rotor 5a is provided with a plurality of fastener holes 5c, into which fasteners 20 described below are inserted, at intervals in the circumferential direction. The fastener hole 5c is formed as a through hole passing through the rotor 5a in the axial direction. The plurality of fastener holes 5c are formed point-symmetrically with respect to the axis of the drive shaft 6 or symmetrically with respect to an imaginary plane including the axis of the drive shaft 6. Although four fastener holes 5c are provided here, the number is arbitrary.

Returning to the explanation of FIG.
The electric motor 5 is provided with a first balance weight 15 and a second balance weight 16 for balancing the unbalance caused by the eccentric rotation movement of the oscillating scroll 2. The first balance weight 15 is fixed to the upper surface of the rotor 5a, and the second balance weight 16 is fixed to the lower surface of the rotor 5a. The first balance weight 15 and the second balance weight 16 rotate together with the rotor 5a. The first balance weight 15 and the second balance weight 16 are made of brass, for example.

The scroll compressor 100 has a total of three balance weights: a first balance weight 15, a second balance weight 16, and the aforementioned main shaft balance weight 6h. The scroll compressor 100 uses these balance weights to offset the imbalance between centrifugal force and moment force caused by the swinging of the swinging scroll 2 via the eccentric shaft portion 6a of the drive shaft 6. Static and dynamic balance.

Hereinafter, with reference to FIG. 1 and the following FIG. 5, an oil separation mechanism and a mechanism for reducing the amount of refrigerating machine oil taken out will be described.
FIG. 5 is a diagram showing the rotor 5a, first balance weight 15, and first cup-shaped member 17 of the scroll compressor 100 according to the first embodiment. FIG. 5A is a schematic plan view of the rotor 5a, the first balance weight 15, and the first cup-shaped member 17. FIG. 5(b) is a schematic vertical cross-sectional view taken along the line AA in FIG. 5(a).

A first cup-shaped member 17 is provided on the upper surface of the rotor 5a. The first balance weight 15 is accommodated in the internal space 17S of the first cup-shaped member 17. The first cup-shaped member 17 prevents the refrigerating machine oil contained in the refrigerant gas around the first balance weight 15 from being turned into a mist due to the rotation of the first balance weight 15 and being discharged from the discharge pipe 12 together with the refrigerant gas. It is something. The first cup-shaped member 17 is preferably formed of a non-magnetic material.

Further, a second cup-shaped member 18 is provided on the lower surface of the rotor 5a. The second balance weight 16 is accommodated in the internal space 18S of the second cup-shaped member 18. The second cup-shaped member 18 prevents the refrigerating machine oil contained in the refrigerant around the second balance weight 16 from being turned into a mist due to the rotation of the second balance weight 16 and being discharged from the discharge pipe 12 together with the refrigerant. be. The second cup-shaped member 18 is preferably formed of a non-magnetic material.

The first balance weight 15, the first cup-shaped member 17, the rotor 5a of the electric motor 5, the second cup-shaped member 18, and the second balance weight 16 are stacked in this order in the axial direction. In the stacked state, the fastener holes formed in each of these constituent parts communicate with each other, and the fastener 20 is inserted into the communication hole to fix each constituent part integrally. Hereinafter, this integral part may be referred to as a rotor integral part.

As shown in FIG. 5, the first cup-shaped member 17 has a disk-shaped bottom part 17a, a cylindrical peripheral part 17b surrounding the outer periphery of the first balance weight 15, and has an internal space 17S. It is formed into a cylindrical shape with a bottom. The first cup-shaped member 17 is rotated such that the drive shaft 6 is passed through a through hole 17aa provided in the bottom part 17a, the bottom part 17a contacts the upper surface of the rotor 5a, and the opening part 17c faces upward. It is fixed to the upper surface of the child 5a. The upper opening 17c of the first cup-shaped member 17 faces the lower opening 19b of the discharge cover 19. The inner diameter D of the opening 19b of the discharge cover 19 and the inner diameter d of the opening 17c of the first cup-shaped member 17 have a relationship of D<d.

In addition to the through hole 17aa, the bottom surface portion 17a of the first cup-shaped member 17 includes a first cup-side flow passage hole 17ab that serves as a flow path for the refrigerant, and a fastener hole (not shown) for passing the fastener 20. ) and are formed. The first cup-side flow passage holes 17ab are provided in the same number as the through-flow passages 5f of the rotor 5a, and are formed at positions facing the through-flow passages 5f.

Further, a first discharge portion 17e for discharging the refrigerating machine oil 11 within the first cup-shaped member 17 is formed on the peripheral surface portion 17b of the first cup-shaped member 17. The first discharge portion 17e is formed on a peripheral surface portion 17b of the first balance weight 15 on the lightweight portion 15a side, which will be described later. The first discharge portion 17e has a discharge hole 17ea that penetrates the peripheral surface portion 17b, and an oil guide plate 17eb that guides refrigerating machine oil to the discharge hole 17ea.

FIG. 6 is an explanatory diagram of the oil guide plate 17eb of the first discharge portion 17e of the scroll compressor 100 according to the first embodiment. FIG. 6 is a diagram of the first discharge portion 17e viewed from the outside in the radial direction.
The oil guiding plate 17eb is formed by cutting and raising the peripheral surface portion 17b with a first notch 17eb1 extending in the axial direction in the peripheral surface portion 17b and a second notch 17eb2 extending in the rotational direction from both ends of the first notch 17eb1. It is made up of pieces. The oil guiding plate 17eb has a shape in which the tip portion of this cut-and-raised piece is pushed inward in the radial direction to protrude, as shown in FIG. Note that the oil guiding plate 17eb is not limited to being formed by a cut-and-raised piece, but may be formed by a protruding piece that protrudes radially inward from the end side of the discharge hole 17ea in the rotational direction of the rotor 5a. In addition, although the example in which one 1st discharge part 17e was formed was shown here, the number of objects of the 1st discharge part 17e may be two or more.

As shown in FIG. 5, a second discharge portion 17d is formed on a peripheral surface portion 17b of the first balance weight 15 on the side of a weight portion 15b, which will be described later. The second discharge portion 17d is a portion for discharging the refrigerant gas within the first cup-shaped member 17. The second discharge portion 17d is a through hole that radially penetrates the peripheral surface portion 17b. The second discharge portion 17d is formed at a position opposite to the other downstream end of a radial passage hole 15c provided in the first balance weight 15, which will be described later. The second discharge portions 17d are provided corresponding to the radial flow passage holes 15c, and since there are two radial flow passage holes 15c here, two second discharge portions 17d are also provided.

The first balance weight 15 is arranged in the internal space 17S of the first cup-shaped member 17. The first balance weight 15 is arranged in contact with the surface of the bottom surface portion 17a of the first cup-shaped member 17 on the side opposite to the rotor 5a side. The first balance weight 15 has an arc-shaped lightweight portion 15a and an arc-shaped weight portion 15b that is heavier than the lightweight portion 15a. The lightweight portion 15a and the heavy portion 15b have a semicircular arc shape, and the lightweight portion 15a and the heavy portion 15b are connected circumferentially to form an annular shape as a whole.

The lightweight portion 15a has an axial height lower than the heavy portion 15b and a radial thickness smaller than the heavy portion 15b, so that the lightweight portion 15a is lighter than the heavy portion 15b. The lightweight portion 15a is configured to avoid the through-flow passage 5f provided in the rotor 5a so as not to overlap the through-flow passage 5f when viewed in the axial direction. Hereinafter, among the plurality of through-flow passages 5f, the through-flow passage 5f located in the area overlapping with the heavy part 15b when viewed in the axial direction is referred to as the heavy-portion side through-flow passage 5fb, and the other through-flow passages are referred to as the light-weight part side through-flow. It's called Road 5fa. Here, an example is shown in which the lightweight portion 15a is shaped so as to avoid the lightweight portion side through-flow passage 5fa so as not to overlap with the lightweight-portion side through-flow passage 5fa when viewed in the axial direction. Good too. The lightweight portion 15a may have a first weight-side passage hole that communicates with the lightweight-portion side through-flow passage 5fa and penetrates in the axial direction. In short, the lightweight portion 15a only needs to have a configuration that allows the lightweight portion side through flow path 5fa to communicate with the internal space 17S of the first cup-shaped member 17.

The weight part 15b is formed with a radial flow passage hole 15c whose one end on the upstream side communicates with the weight part side through flow passage 5fb and the other end on the downstream side communicates with the outer circumferential surface 15bb of the weight part 15b. The radial passage hole 15c changes the flow direction of the refrigerant gas that has passed through the heavy section side through passage 5fb from the axial direction to the radial direction. The radial flow passage hole 15c extends radially outward from a portion facing the weight part side through flow passage 5fb on the contact surface 15ba with the bottom surface part 17a of the first cup-shaped member 17, and connects to the outer circumferential surface 15bb of the weight part 15b. It is formed by a groove that passes through the The radial passage hole 15c is not limited to the above-mentioned groove, but may be formed by a hole. In short, the radial passage hole 15c may be formed in the weight part 15b so that the flow direction of the refrigerant gas that has passed through the weight part side through passage 5fb can be changed from the axial direction to the radial direction. The radial flow passage holes 15c are provided corresponding to the weight section side through flow passages 5fb, and here, since there are two weight part side through flow passages 5fb, two radial flow passage holes 15c are also provided. ing.

A fastener hole 15d through which the fastener 20 passes is formed in the lightweight portion 15a and the heavy portion 15b. The fastener hole 15d is formed to face the fastener hole 5c formed in the rotor 5a. Two fastener holes 15d are formed in the lightweight part 15a and two fastener holes are formed in the heavy part 15b.

As shown in FIG. 1, the second cup-shaped member 18 has a disc-shaped bottom part 18a and a cylindrical peripheral part 18b, and is formed into a bottomed cylindrical shape having an internal space 18S. The second cup-shaped member 18 is configured such that the drive shaft 6 is passed through a through hole 18aa provided in the bottom part 18a, the bottom part 18a contacts the lower surface of the rotor 5a, and the opening part 18c faces downward. It is fixed to the lower surface of the rotor 5a. In addition to the through hole 18aa, the bottom surface portion 18a of the second cup-shaped member 18 includes a second cup-side flow passage hole 18ab that serves as a flow path for the refrigerant, and a fastener hole (not shown) for passing the fastener 20. ) and are formed. The second cup-side flow passage holes 18ab are provided in the same number as the through-flow passages 5f of the rotor 5a, and are formed at positions facing the through-flow passages 5f. The fastener holes (not shown) are provided in the same number as the fastener holes 5c formed in the rotor 5a, and are formed at positions facing the fastener holes 5c.

The second balance weight 16 is arranged in the internal space 18S of the second cup-shaped member 18. The second balance weight 16 is arranged in contact with the surface of the bottom surface portion 18a of the second cup-shaped member 18 on the side opposite to the rotor 5a side. The second balance weight 16 is formed in an arc shape. The second balance weight 16 is arranged at a position overlapping the lightweight portion 15a of the first balance weight 15 when viewed in the axial direction. The second balance weight 16 is disposed at a diagonally eccentric position relative to the weight portion 15b of the first balance weight 15.

The second balance weight 16 is formed with a second weight-side passage hole 16a that serves as a flow path for the refrigerant, and a fastener hole (not shown) through which the fastener 20 passes. The second weight-side flow passage hole 16a is formed to communicate with the light-weight part side through-flow passage 5fa and penetrate in the axial direction. The second balance weight 16 does not have the second weight side flow passage hole 16a, and has a shape that avoids the light weight part side through flow passage 5fa so as not to overlap with the light weight part side through flow passage 5fa when viewed in the axial direction. It may be configured as follows. Two fastener holes are provided, the same number as the fastener holes formed in the lightweight part 15a of the first balance weight 15, and the fastener holes formed in the lightweight part 15a of the first balance weight 15 and the rotor 5a are connected to each other. They are formed at positions facing each other.

As a result, as shown in FIG. 1, a light-weight part-side through passage 40 that penetrates in the axial direction is formed on the light-weight part 15a side when the rotor integral body is viewed in the axial direction. The lightweight part side through flow path 40 includes, in order from the upstream side in the flow direction of the refrigerant gas, the second weight side flow path hole 16a of the second balance weight 16, and the second cup side flow path hole 18ab of the second cup-shaped member 18. , the light-weight part-side through passage 5fa of the rotor 5a, and the first cup-side passage hole 17ab of the first cup-shaped member 17 are formed in communication with each other.

Further, when the rotor integral body is viewed in the axial direction, on the weight part 15b side, there is formed a weight part side through flow path 50 that passes through the rotor body except for the first balance weight 15. The weight part side through flow path 50 includes, in order from the upstream side in the flow direction of the refrigerant gas, the second cup side flow path hole 18ab of the second cup-shaped member 18, the weight part side through flow path 5fb of the rotor 5a, and the first through flow path 5fb of the rotor 5a. The first cup-side channel holes 17ab of the cup-shaped member 17 are formed in communication with each other. The weight section side through passage 50 communicates with the radial passage hole 15c of the first balance weight 15, and is connected to the first cup-shaped member 17 facing the other downstream end of the radial passage hole 15c. The first cup-shaped member 17 communicates with the outside through the second discharge portion 17d formed therein. The weight section side through flow path 50, the radial flow path hole 15c, and the second discharge portion 17d form a flow path whose flow direction is changed from the axial direction to the radial direction.

Next, the operation of scroll compressor 100 according to the first embodiment will be explained.
When starting up and operating the scroll compressor 100, refrigerant is sucked through the suction pipe 13 and enters the compression chamber 1f. The rocking scroll 2 driven by the electric motor 5 performs an eccentric rotation movement by the eccentric shaft portion 6a of the drive shaft 6. Specifically, the swinging scroll 2 is prevented from rotating by the Oldham mechanism 9 and revolves. As a result, the volume of the compression chamber 1f gradually decreases, and the suction refrigerant in the compression chamber 1f is compressed. This compression stroke puts the suction refrigerant at high pressure. In the compression stroke, the refrigerant gas at an intermediate pressure during compression is guided from the bleed hole 2g of the oscillating scroll 2 through the communication hole 3e of the compliant frame 3 to the frame lower space 4b, and is introduced into the frame lower space 4b. A medium pressure atmosphere is maintained.

The refrigerant gas, which has become highly pressurized through the compression stroke, is discharged from the discharge port 1d of the fixed scroll 1 into the upper space 10a of the closed container 10. The refrigerant gas discharged into the upper space 10a contains refrigerating machine oil, and is a mixed gas of refrigerant gas and refrigerating machine oil. This refrigerant gas containing refrigerating machine oil is a refrigerant that is composed of a first flow path 4f provided on the outer periphery of the compression mechanism section 14 and a second flow path 5g provided on the outer periphery of the stator 5b of the electric motor 5. It passes through the flow path 30 and is guided to the space below the electric motor 5, that is, to the bottom of the closed container 10. During the flow of the refrigerant gas led from the upper space 10a to the bottom of the closed container 10, part of the refrigerating machine oil contained in the refrigerant gas is separated, and the refrigerating machine oil is transmitted along the inner peripheral surface of the closed container 10, etc. The oil is stored in an oil reservoir 10b at the bottom of the closed container 10. The refrigerant gas from which a portion of the refrigerating machine oil has been separated flows into the internal space 18S of the second cup-shaped member 18 from the opening 18c of the second cup-shaped member 18. Next, FIG. 7 shows the flow of the refrigerant gas after it flows into the internal space of the second cup-shaped member 18.

FIG. 7 is an explanatory diagram of the flow of refrigerant gas in the scroll compressor 100 according to the first embodiment. In FIG. 7, dotted arrows indicate the flow of refrigerant gas or refrigerating machine oil.
A part of the refrigerant gas that has flowed into the internal space 18S of the second cup-shaped member 18 passes through the lightweight part side through flow path 40 and flows into the internal space 17S of the first cup-shaped member 17. Further, the remainder of the refrigerant gas that has entered the internal space 18S of the second cup-shaped member 18 passes through the weight section side through flow path 50 and flows into the internal space of the first cup-shaped member 17. Hereinafter, the flow of the refrigerant gas will be explained separately into the flow of the refrigerant gas that has passed through the light section side through flow path 40 and the flow of the refrigerant gas that has passed through the heavy section side through flow path 50.

(Flow of refrigerant gas that has passed through the lightweight part side through flow path 40)
In the refrigerant gas that has passed through the light-weight part side through-flow path 40, part of the refrigerating machine oil is separated during the process of passing through the light-weight part side through-flow path 40, and the separated refrigerating machine oil and a part of the refrigerating machine oil are separated. and the refrigerant gas flow into the internal space 17S of the first cup-shaped member 17. Here, the refrigerating machine oil that has flowed into the internal space 17S of the first cup-shaped member 17 is subjected to centrifugal force due to the rotation of the rotor 5a during the process of passing through the lightweight part side through flow path 40. Therefore, the refrigerating machine oil that has flowed into the internal space 17S of the first cup-shaped member 17 is blown away toward the peripheral surface portion 17b of the first cup-shaped member 17 while rotating in the rotational direction of the rotor 5a, and is blown away toward the peripheral surface portion 17b of the first cup-shaped member 17. adhere to.

Refrigerating machine oil adhering to the peripheral surface portion 17b reaches the first discharge portion 17e while flowing along the peripheral surface portion 17b, and is discharged to the outside of the first cup-shaped member 17 from the discharge hole 17ea of the first discharge portion 17e. Note that some of the refrigerating machine oil that has flowed along the peripheral surface portion 17b tends to remain in the internal space 17S because it is flowed in the rotational direction by the centrifugal force caused by the rotation of the rotor 5a. Such refrigerating machine oil adheres to the outer surface of the oil guiding plate 17eb whose tip portion protrudes toward the internal space 17S, flows along this outer surface, and is discharged to the outside of the first cup-shaped member 17. That is, the refrigerating machine oil that tends to remain in the internal space 17S is guided to the outside of the first cup-shaped member 17 by the oil guiding plate 17eb and is discharged.

Since the centrifugal force due to the rotation of the first cup-shaped member 17 is acting on the refrigerating machine oil discharged from the discharge hole 17ea of the first discharge part 17e, the inside of the closed container 10 is directed radially outward from the discharge hole 17ea. blown away. Refrigerating machine oil blown radially outward from the discharge hole 17ea is guided to the bottom of the airtight container 10 through a second flow path 5g provided on the outer periphery of the stator 5b, and is stored in the oil reservoir 10b. be done.

The refrigerant gas that has passed through the light-weight part side through-flow path 40 and flowed into the internal space 17S of the first cup-shaped member 17 is similarly blown away toward the peripheral surface 17b of the first cup-shaped member 17. Then, the refrigerant gas collides with the peripheral surface portion 17b, and due to this collision, a part of the refrigerating machine oil contained in the refrigerant gas is separated, and the separated refrigerating machine oil is discharged from the discharge hole 17ea of the first discharge part 17e to the first cup. It is discharged to the outside of the shaped member 17. On the other hand, the refrigerant gas from which the refrigerating machine oil has been separated flows out from the opening 17c of the first cup-shaped member 17 and flows into the discharge cover 19 from the opening 19b of the discharge cover 19. The refrigerant that has flowed into the discharge cover 19 flows out from the opening 19a of the discharge cover 19, and then is discharged to the outside from the discharge pipe 12 via the first discharge flow path 4g.

(Flow of refrigerant gas that has passed through the heavy section side through flow path 50)
The refrigerant gas that has passed through the weight section side through-flow path 50 is separated from the refrigerant gas in which a portion of the refrigerating machine oil is separated during the process of passing through the weight section side through-flow path 50. The refrigerating machine oil flows into the internal space 17S of the first cup-shaped member 17. The refrigerating machine oil that has flowed into the internal space 17S of the first cup-shaped member 17 collides with the inner wall of the radial passage hole 15c provided in the weight part 15b of the first balance weight 15, and flows from the axial direction to the radial outside. The flow direction is changed and the liquid is discharged to the outside from the second discharge portion 17d of the first cup-shaped member 17.

Refrigerating machine oil discharged from the second discharge part 17d to the outside of the first cup-shaped member 17 is guided to the bottom of the airtight container 10 through a second flow path 5g provided on the outer circumference of the stator 5b, and the oil is It is stored in the reservoir 10b. In this way, since the flow direction of the refrigerating machine oil is changed from the axial direction to the radial direction by the radial passage hole 15c, the refrigerant gas is allowed to flow in the axial direction and exit from the opening 17c of the first cup-shaped member 17. The amount of refrigerating machine oil taken out can be reduced compared to the case where it is discharged.

Similarly, the refrigerant gas that has flowed into the internal space 17S of the first cup-shaped member 17 collides with the inner wall of the radial passage hole 15c, and the flow direction is changed from the axial direction to the radial outside, and the refrigerant gas flows into the first cup-shaped member. It is discharged to the outside from the second discharge part 17d of No. 17. Here, when the refrigerant gas collides with the inner wall of the radial passage hole 15c, a part of the refrigerating machine oil contained in the refrigerant gas is separated. Therefore, the amount of refrigerating machine oil taken out can be further reduced. In addition, the speed of the refrigerant gas is reduced by colliding with the inner wall of the radial passage hole 15c. Therefore, the time from when the refrigerant gas collides with the inner wall of the radial passage hole 15c until it is discharged to the outside of the first cup-shaped member 17 becomes longer, and the time during which the refrigerating machine oil is separated from the refrigerant gas becomes longer. As a result, the amount of refrigerating machine oil taken out can be reduced.

Here, assuming that the amount of refrigerating machine oil flowing into the first cup-shaped member 17 of Embodiment 1 is the same as the amount of refrigerating machine oil flowing into the balance weight of Patent Document 1 as a comparative example, the refrigerating machine oil Compare the amounts taken out.

FIG. 8 is a perspective view showing a balance weight 300 of a comparative example.
The balance weight 300 of the comparative example has a weight part 301 that is filled with metal approximately half the circumference, and the part other than the weight part 301 is an arcuate wall part 302 that forms a semi-cylindrical internal space 300S. ing. A first discharge portion 303 is formed in the arcuate wall portion 302 for discharging refrigerating machine oil accumulated in the internal space 300S. The first discharge portion 303 is formed of a through hole that penetrates the arcuate wall portion 302 in the radial direction. A shaft hole 304 through which a drive shaft (not shown) passes is formed in the center of the balance weight 300.

In the balance weight 300 of such a comparative example, the refrigerating machine oil passes through the gap between the shaft hole 304 and the drive shaft (not shown) inserted into the shaft hole 304 and flows into the internal space 300S. Some of the refrigerating machine oil that has flowed into the internal space 300S flows from the internal space 300S toward the first discharge part 303, and some of the refrigerating machine oil flows from the internal space 300S in the axial direction and is discharged to the outside of the balance weight 300. The refrigerating machine oil that flows in the axial direction from the internal space 300S and is discharged to the outside of the balance weight 300 is discharged to the outside of the compressor, leading to an increase in the amount of the refrigerating machine oil taken out.

On the other hand, in Embodiment 1, the refrigerating machine oil that flows into the first cup-shaped member 17 flows separately from the light section side through passage 5fa and the heavy section side through passage 5fb. The amount of refrigerating machine oil that passes through the light section side through flow path 5fa and flows into the internal space 17S of the first cup-shaped member 17, and the amount of refrigerating machine oil that passes through the heavy section side through flow path 5fb and flows into the radial flow path hole 15c. The amount of refrigerating machine oil is considered to be approximately the same amount. Therefore, the amount of refrigerating machine oil that passes through the light-weight part side through flow path 5fa and flows into the internal space 17S of the first cup-shaped member 17 is approximately half the amount of refrigerating machine oil that flows into the internal space 300S of the comparative example. . To give a specific example, it is assumed that the amount of refrigerating machine oil flowing into the first cup-shaped member 17 of the first embodiment and the amount of refrigerating machine oil flowing into the balance weight of the comparative example are both A. At this time, the amount of refrigerating machine oil flowing into the internal space 17S of the first cup-shaped member 17 is "A/2" each from the lightweight part side through passage 5fa and the lightweight part side through passage 5fa. .

Here, for the purpose of simplifying the explanation, the same is true for the case where the refrigerating machine oil that has passed through the lightweight part side through flow path 5fa and flowed into the internal space 17S of the first cup-shaped member 17 has flowed into the internal space 300S of the comparative example. Assume that the flow is as follows. That is, it is assumed that several percent of the refrigerating machine oil that has passed through the lightweight part side through-flow path 5fa and flowed into the internal space 17S of the first cup-shaped member 17 flows in the axial direction and is discharged to the outside of the balance weight. In the first embodiment, the amount (A/2) of the refrigerating machine oil that flows into the internal space 17S through the light-weight part side through flow path 5fa is the same as the amount (A/2) of the refrigerating machine oil that flows into the internal space 300S of the comparative example. It is half of A). Therefore, even if several percent of the refrigerating machine oil flows in the axial direction and is discharged to the outside of the balance weight, it is only a few percent relative to (A/2), so the amount can be reduced compared to several percent relative to (A).

Furthermore, as described above, the refrigerating machine oil that flows into the first cup-shaped member 17 through the heavy section side through-flow path 5fb is discharged radially outward from the first discharge part 17e of the first cup-shaped member 17. After that, it returns to the oil reservoir section 10b. That is, approximately half (A/2) of the refrigerating machine oil flowing into the first cup-shaped member 17 returns to the oil reservoir portion 10b.

As described above, in the first embodiment, the amount of refrigerating machine oil taken out can be reduced compared to the comparative example.

In addition, in the above, it is assumed that the refrigerating machine oil that has passed through the lightweight part side through flow path 5fa and flowed into the internal space 17S of the first cup-shaped member 17 follows the same flow as when it flows into the internal space 300S of the comparative example. I assumed that. However, in the first embodiment, the first discharge part 17e has an oil guide plate 17eb instead of having a simple through-hole configuration as in the comparative example, and by the action of the oil guide plate 17eb, the refrigerating machine oil is transferred to the first discharge part 17e. It can be guided to the outside of the cup-shaped member 17. When refrigerating machine oil accumulates in the first cup-shaped member 17, the accumulated refrigerating machine oil is caught in the flow of refrigerant gas that has flowed into the first cup-shaped member 17, and the refrigeration oil accumulates in the axial direction from the first cup-shaped member 17. There is a possibility that the liquid may leak out and be taken out of the closed container 10. Therefore, it is preferable that no refrigerating machine oil accumulates inside the first cup-shaped member 17. In the first embodiment, the refrigerating machine oil in the first cup-shaped member 17 can be actively discharged by the action of the oil guide plate 17eb, and from this point as well, the amount of refrigerating machine oil taken out can be reduced compared to the comparative example.

Further, the balance weight 300 of the comparative example has a configuration that has both a function as a balancer and a function for reducing the amount of refrigerating machine oil taken out. The balance weight 300 of the comparative example has a shape that is difficult to manufacture by forcing it to have two functions. Specifically, the balance weight 300 of the comparative example needs to have a height in the drive shaft direction that projects further toward the compression mechanism than the end of the end coil of the stator of the electric motor. For this reason, the difference in weight and strength becomes large between a portion that is thick in the radial direction like the weight portion 301 and a portion that is thin in the radial direction like the arcuate wall portion 202. It is difficult to punch and mold, and even if molding is possible, it is difficult to ensure precision. In order to ensure accuracy, it may be necessary to adopt a labor-intensive manufacturing method.

In contrast, in Embodiment 1, the function as a balancer and the function for reducing the amount of refrigerating machine oil taken out are provided in separate members, so that they can be manufactured using manufacturing methods suitable for each. Therefore, it is possible to reduce manufacturing costs while ensuring accuracy.

As described above, the scroll compressor 100 of the first embodiment includes the first balance weight 15 fixed to the rotor 5a of the electric motor 5, and the first balance weight 15 fixed to the rotor 5a surrounding the outer periphery of the first balance weight 15. A first cup-shaped member 17 having a cylindrical peripheral surface portion 17b. The first balance weight 15 has an arc-shaped lightweight portion 15a and an arc-shaped weight portion 15b that is heavier than the lightweight portion 15a. The rotor 5a includes a plurality of through passages 5f formed by through holes extending in the axial direction of the drive shaft 6. Among the plurality of through-flow passages 5f, when the through-flow passage 5f located in the region overlapping with the heavy portion 15b when viewed in the axial direction is referred to as the heavy-portion side through-flow passage 5fb, and the others are referred to as the light-weight portion side through-flow passage 5fa, The lightweight part side through flow path 5fa communicates with the internal space of the first cup-shaped member 17. The peripheral surface portion 17b of the first cup-shaped member 17 has a first discharge portion 17e for discharging the refrigerating machine oil in the first cup-shaped member 17 on the lightweight portion 15a side. The weight part 15b of the first balance weight 15 is a hole in which one end on the upstream side communicates with the weight part side through flow path 5fb and the other end on the downstream side communicates with the outer circumferential surface 5bb of the weight part 15b. It has a radial passage hole 15c that changes the flow direction of the refrigerant containing refrigerating machine oil that has passed through the side through passage 5fb from the axial direction to the radial direction. The circumferential surface portion 17b of the first cup-shaped member 17 is a hole that radially penetrates the circumferential surface portion 17b at a position facing the other downstream end of the radial flow path hole 15c. It has a second discharge part 17d that discharges the refrigerant flowing out of the first cup-shaped member 17 to the outside of the first cup-shaped member 17.

As a result, the flow direction of the refrigerant gas that has passed through the heavy section side through flow path 5fb is changed from the axial direction to the radial direction by the radial flow path hole 15c. Therefore, compared to the case where the refrigerant gas flows in the axial direction and is discharged to the outside from the opening 17c of the first cup-shaped member 17, the amount of refrigerating machine oil taken out can be reduced.

The first discharge portion 17e has a discharge hole 17ea that radially penetrates the circumferential surface portion 17b of the first cup-shaped member 17, and an oil guide plate 17eb that guides refrigerating machine oil to the discharge hole 17ea.

Thereby, more refrigerating machine oil can be discharged to the outside from the internal space 17S of the first cup-shaped member 17, and as a result, the amount of refrigerating machine oil taken out can be reduced.

The oil guide plate 17eb has a first notch 17eb1 extending in the axial direction in the circumferential surface portion 17b of the first cup-shaped member 17, and a second notch 17eb2 extending in the rotational direction of the drive shaft 6 from both ends of the first notch 17eb1. It is formed by cutting and raising the surface portion 17b. The oil guide plate 17eb has a shape in which the tip of the cut and raised portion is pushed inward in the radial direction and protrudes.

In this way, since the oil guide plate 17eb can be constructed from a cut and raised piece, it is easy to manufacture.

Embodiment 2.
The second embodiment differs from the first embodiment in the radial passage hole 15c of the first balance weight 15. Hereinafter, the differences between the second embodiment and the first embodiment will be mainly explained, and the configurations not explained in the second embodiment are the same as the first embodiment.

FIG. 9 is a schematic plan view of the rotor 5a, the first balance weight 15, and the first cup-shaped member 17 of the scroll compressor 100 according to the second embodiment. FIG. 2 is a schematic plan view showing the first balance weight 15 and the structure around it.
In the first embodiment described above, the radial flow passage holes 15c were individually provided corresponding to each of the weight section side through flow passages 5fb provided in the rotor 5a. On the other hand, the second embodiment has a configuration in which one radial flow passage hole 15c is commonly provided in each of the weight section side through flow passages 5fb.

According to the second embodiment, the same effects as in the first embodiment can be obtained, and the shape of the radial passage hole 15c can be simplified. Therefore, it is possible to obtain a scroll compressor that is easier to manufacture and has a lower manufacturing cost. In addition, since the second embodiment has a configuration in which two radial flow passage holes 15c that were previously separated are connected to form one large radial flow passage hole 15c, this can be adopted if there is no problem in terms of strength. Needless to say.

Embodiment 3.
Embodiment 3 differs from Embodiment 1 in a second discharge portion 17d of first cup-shaped member 17. Hereinafter, the differences between the third embodiment and the first embodiment will be mainly explained, and the configurations not explained in the third embodiment are the same as the first embodiment.

FIG. 10 is a schematic plan view of the rotor 5a, the first balance weight 15, and the first cup-shaped member 17 of the scroll compressor 100 according to the third embodiment.
In the first embodiment described above, the second discharge portions 17d are individually provided in the first cup-shaped member 17 corresponding to each of the radial flow passage holes 15c provided in the weight portion 15b of the first balance weight 15. was. In contrast, Embodiment 3 has a configuration in which one second discharge portion 17d is provided in common to a plurality of radial flow passage holes 15c. Specifically, the second discharge portion 17d extends from one circumferential end of one of the two radial passage holes 15c in the circumferential surface portion 17b of the first cup-shaped member 17 to the two radial passage holes. It is formed in a circumferential range up to the other circumferential end of the other one of 15c.

According to the third embodiment, the same effects as the first embodiment can be obtained, and the shape of the second discharge portion 17d of the first cup-shaped member 17 can be simplified. Therefore, it is possible to obtain a scroll compressor that is easier to manufacture and has a lower manufacturing cost. In addition, since the third embodiment has a configuration in which the two second discharge parts 17d which were separated from each other are connected to form one large second discharge part 17d, it goes without saying that it can be adopted when there is no problem in terms of strength. .

Embodiment 4.
The fourth embodiment differs from the first embodiment in the second discharge portion 17d of the first cup-shaped member 17 and the radial passage hole 15c of the first balance weight 15. Embodiment 4 corresponds to a configuration that is a combination of Embodiment 2 and Embodiment 3, so to speak. Hereinafter, the differences between the fourth embodiment and the first embodiment will be mainly explained, and the configuration not explained in the fourth embodiment is the same as the first embodiment.

FIG. 11 is a schematic plan view of the rotor 5a, the first balance weight 15, and the first cup-shaped member 17 of the scroll compressor 100 according to the fourth embodiment.
In the first embodiment described above, the radial flow passage holes 15c were individually provided corresponding to each of the weight section side through flow passages 5fb provided in the rotor 5a. On the other hand, the fourth embodiment has a configuration in which one radial flow passage hole 15c is provided in common to the plurality of heavy section side through flow passages 5fb. Embodiment 4 has a configuration in which one second discharge portion 17d is formed in the circumferential surface portion 17b of the first cup-shaped member 17 at a position facing the radial passage hole 15c when viewed in the radial direction. .

According to the fourth embodiment, the same effects as the second and third embodiments can be obtained.

By the way, in the fourth embodiment, since one second discharge part 17d is provided in common to the plurality of radial flow passage holes 15c, the opening area of each second discharge part 17d becomes large. Therefore, depending on the size of the opening area, the strength of the first cup-shaped member 17 may not be maintained. In this case, there is a possibility that the first cup-shaped member 17 cannot be formed during processing. Further, when the first cup-shaped member 17 collides with high-temperature refrigerant gas and refrigerating machine oil 11 during rotation of the rotor 5a, there is a possibility that the first cup-shaped member 17 cannot withstand the collision and deforms.

Based on these considerations, in Embodiment 4, one second discharge portion 17d is naturally provided with a design that can sufficiently maintain the strength of the first cup-shaped member 17. From a different perspective, in the first and second embodiments, the second discharge portions 17d are separately provided corresponding to each of the weight section side through-flow channels 5fb, so that the first cup-shaped member 17 strength can be maintained. Therefore, the shape of the second discharge portion 17d may be determined as appropriate, taking into account the effect of simplifying the shape and maintaining the strength.

Further, the same can be said of the radial passage hole 15c of the first balance weight 15. That is, in the fourth embodiment, since one radial flow passage hole 15c is provided in common to the plurality of heavy section side through flow passages 5fb, the volume of each radial flow passage hole 15c is large. Become. Therefore, depending on the size of the volume, the strength of the first balance weight 15 may not be maintained. However, in the fourth embodiment, as a matter of course, one radial passage hole 15c is provided in a design that can sufficiently maintain the strength of the first balance weight 15. From a different perspective, in the first and third embodiments, the radial passage holes 15c are individually provided corresponding to each of the weight section side through passages 5fb, so that the first balance weight 15 is Can maintain strength. Therefore, the shape of the radial passage hole 15c may be determined as appropriate, taking into account the effect of simplifying the shape and maintaining the strength.

Embodiment 5.
The fifth embodiment differs from the first embodiment in a lightweight portion 15a of the first balance weight 15. Hereinafter, the differences between the fifth embodiment and the first embodiment will be mainly explained, and the configuration not explained in the fifth embodiment is the same as the first embodiment.

FIG. 12 is a diagram showing the rotor 5a, the first balance weight 15, and the first cup-shaped member 17 of the scroll compressor 100 according to the fifth embodiment. FIG. 12A is a schematic plan view of the rotor 5a, the first balance weight 15, and the first cup-shaped member 17. FIG. 12(b) is a schematic vertical cross-sectional view taken along the line AA in FIG. 12(a).

In the first embodiment, the lightweight portion 15a of the first balance weight 15 has a semicircular arc shape, but in the fifth embodiment, it is formed into two circumferentially divided arc shapes. In this way, the lightweight portion 15a may be divided in the circumferential direction. Even in this case, the scroll compressor 100 of the fifth embodiment can obtain the same effects as described above.

More specifically, the lightweight portion 15a of the fifth embodiment is a portion in which the fastener hole 15d is not formed in the lightweight portion 15a of the first embodiment, in other words, a portion unnecessary for fixing the lightweight portion 15a to the rotor 5a. It has a configuration in which parts have been deleted. Furthermore, the lightweight portion 15a of the fifth embodiment has an arc shape with a uniform length in the radial direction.

This configuration facilitates manufacturing for the following reasons. In the first embodiment described above, as shown in FIG. 5, the lightweight portion 15a has a shape that avoids the lightweight portion side through flow passage 5fa, so that the shape is complicated, with a mixture of long and short portions in the radial direction. It has a shape. On the other hand, in the fifth embodiment, since the lightweight portion 15a has an arc shape with a uniform radial length, a scroll compressor 100 that is easy to manufacture and inexpensive to manufacture can be obtained. Furthermore, in the first embodiment, the lightweight portion 15a of the first balance weight 15 had a semicircular arc shape, but in the fifth embodiment, the lightweight portion 15a was formed into two circular arc shapes divided in the circumferential direction. It is the heavy part 15b that mainly maintains the balance, and the light part 15a has a small influence on the balance. Therefore, by forming the lightweight portion 15a into two circular arc shapes divided in the circumferential direction as in the fifth embodiment, the amount of material used can be reduced compared to the first embodiment, and the manufacturing cost of the scroll is low. A compressor 100 can be obtained.

Embodiment 6.
Embodiment 6 differs from Embodiment 1 in a second discharge portion 17d of first cup-shaped member 17. Hereinafter, the differences between the sixth embodiment and the first embodiment will be mainly explained, and the configurations not explained in the sixth embodiment are the same as the first embodiment.

FIG. 13 is a diagram showing the rotor 5a, first balance weight 15, and first cup-shaped member 17 of the scroll compressor 100 according to the sixth embodiment. FIG. 13A is a schematic plan view of the rotor 5a, the first balance weight 15, and the first cup-shaped member 17. FIG. 13(b) is a schematic vertical cross-sectional view taken along the line AA in FIG. 13(a).
In the sixth embodiment, the distance L1 and the distance L2 have a relationship of L1<L2. The distance L1 is the distance from the tip of the oil guide plate 17eb of the first discharge portion 17e of the first cup-shaped member 17 to the center O of the first cup-shaped member 17. The distance L2 is the distance from the inner periphery of the weight portion 15b of the first balance weight 15 to the center O of the first cup-shaped member 17.

Among the refrigerating machine oil inside the first cup-shaped member 17, particulate oil droplets adhere to the peripheral surface portion 17b and flow along the peripheral surface portion 17b. However, the particulate oil droplets float in the internal space 17S of the first cup-shaped member 17 without adhering to the peripheral surface portion 17b. Since the distance L1 and the distance L2 have the relationship L1<L2, the particulate oil droplets floating in the internal space 17S of the first cup-shaped member 17 come into contact with the outer surface of the oil guide plate 17eb and are discharged. It is discharged to the outside from the hole 17ea. Therefore, in the sixth embodiment, the amount of refrigerating machine oil that remains in the internal space 17S of the first cup-shaped member 17 can be reduced, and as a result, the amount of refrigerating machine oil taken out can be significantly reduced. Furthermore, in the sixth embodiment, since the amount of refrigerating machine oil that remains in the internal space 17S of the first cup-shaped member 17 can be reduced, the amount of refrigerating machine oil that circulates within the closed container can be ensured.

According to Embodiment 6, the same effects as Embodiment 1 can be obtained, and by having the relationship L1<L2, the amount of refrigerating machine oil taken out can be reduced, and the refrigerating machine oil circulating in the sealed container can be reduced. amount can be secured. As a result, it is possible to obtain a highly reliable scroll compressor that can prevent the risk of a decrease in the amount of oil supplied to the bearings and sliding members.

Although each embodiment of the scroll compressor has been described above, the embodiments of the present disclosure can also be combined as appropriate. For example, each of Embodiments 2 to 4 and Embodiment 5 may be combined, and in the configurations of FIGS. 9 to 11, the shape of the lightweight portion 15a of the first balance weight 15 may be changed to the shape of FIG. 12. Furthermore, by combining each of Embodiments 2 to 4 and Embodiment 6, in the configurations shown in FIGS. 9 to 11, the first discharge portion 17e of the first cup-shaped member 17 is configured to have a relationship of L1<L2. You can also use it as

Embodiment 7.
Embodiment 7 relates to a refrigeration cycle device such as an air conditioner equipped with the scroll compressor 100 of any one of Embodiments 1 to 6.

FIG. 14 is a schematic configuration diagram of a refrigeration cycle device 200 according to the seventh embodiment.
The refrigeration cycle device 200 switches the flow of refrigerant from the scroll compressor 100, the suction muffler 101 connected to the suction side of the scroll compressor 100, and the scroll compressor 100 connected to the discharge side of the scroll compressor 100. A four-way switching valve 103 is provided. The refrigeration cycle device 200 further includes an outdoor heat exchanger 104, a pressure reducer 105 such as an electric expansion valve, and an indoor heat exchanger 106. In the refrigeration cycle apparatus 200, these devices are sequentially connected via piping to form a refrigeration circuit. In general, in the refrigeration cycle device 200, the indoor heat exchanger 106 is installed in an indoor device, and the remaining scroll compressor 100, four-way switching valve 103, outdoor heat exchanger 104, and pressure reducer 105 are installed in outdoor devices. It is installed in.

In heating operation when the refrigeration cycle device 200 is applied to an air conditioner, the four-way switching valve 103 is connected to the solid line side in FIG. 14. The high-temperature, high-pressure refrigerant compressed by the scroll compressor 100 flows into the indoor heat exchanger 106, exchanges heat with indoor air, condenses, and liquefies, and then flows into the pressure reducer 105. The refrigerant that has flowed into the pressure reducer 105 is depressurized and becomes a two-phase state of low temperature and low pressure, and then flows into the outdoor heat exchanger 104 . The refrigerant that has flowed into the outdoor heat exchanger 104 is evaporated by heat exchange with the outside air, gasified, and returned to the scroll compressor 100 through the four-way switching valve 103. That is, in the heating operation, the refrigerant circulates as shown by the solid arrow in FIG. 14 . Through this circulation, the refrigerant exchanges heat with outside air and absorbs heat in the outdoor heat exchanger 104, which is an evaporator, and the refrigerant that has absorbed heat is sent to the indoor heat exchanger 106, which is a condenser, and exchanges heat with the outside air. Heats the indoor air by exchanging heat.

In cooling operation when the refrigeration cycle device 200 is applied to an air conditioner, the four-way switching valve 103 is connected to the broken line side in FIG. 14. The high-temperature, high-pressure refrigerant compressed by the scroll compressor 100 flows into the outdoor heat exchanger 104, exchanges heat with the outside air, condenses and liquefies, and then flows into the pressure reducer 105. The refrigerant that has flowed into the pressure reducer 105 is depressurized into a two-phase state of low temperature and low pressure, and then flows into the indoor heat exchanger 106 . The refrigerant that has flowed into the indoor heat exchanger 106 is evaporated by heat exchange with indoor air, gasified, and returned to the scroll compressor 100 through the four-way switching valve 103. That is, in the cooling operation, the refrigerant circulates as shown by the broken line arrow in FIG. Through this circulation, the refrigerant exchanges heat with indoor air in the indoor heat exchanger 106, which is an evaporator, and cools the indoor air by absorbing heat from the indoor air. The refrigerant that has absorbed heat is sent to the outdoor heat exchanger 104, which is a condenser, where it exchanges heat with the outside air and radiates heat to the outside air.

Examples of the refrigerant used in the refrigeration circuit include R410A refrigerant, R32 refrigerant, and R290 refrigerant.

The refrigeration cycle device 200 configured in this manner includes the scroll compressor 100 of any one of the first to sixth embodiments, and therefore has the same effects as the scroll compressor 100 described above.

Note that the refrigeration cycle device 200 can also be applied to a refrigerator, a freezer, or the like in addition to an air conditioner.

1 Fixed scroll, 1a Base plate part, 1b Plate spiral teeth, 1c Oldham guide groove, 1d Discharge port, 1e Suction port, 1f Compression chamber, 1g Suction check valve, 2 Oscillating scroll, 2a Base plate part, 2b Plate Spiral tooth, 2c Oldham guide groove, 2d Boss, 2e Swing bearing, 2f Thrust surface, 2g Bleeding hole, 2k Space around base plate, 2n Space outside boss, 3 Compliant frame, 3a Thrust bearing, 3c Main Bearing, 3d Auxiliary main bearing, 3e Communication hole, 3f Communication hole, 3g Intermediate pressure adjustment valve, 3h Intermediate pressure adjustment valve holder, 3k Intermediate pressure adjustment spring, 3n Intermediate pressure adjustment valve space, 3p Upper cylindrical surface, 3s Lower cylindrical surface , 3t thrust bearing opening, 4 guide frame, 4a frame upper space, 4b frame lower space, 4c upper cylindrical surface, 4d lower cylindrical surface, 4f first flow path, 4g first discharge flow path, 5 electric motor, 5a rotor , 5b stator, 5c fastener hole, 5f through flow path, 5fa light weight part side through flow path, 5fb heavy part side through flow path, 5g second flow path, 5h lead wire, 6 drive shaft, 6a eccentric shaft part, 6b Main shaft part, 6c Subshaft part, 6d Intermediate shaft part, 6e Oil supply path, 6f Oil supply port, 6g Oil supply hole, 6h Main shaft balance weight, 7a Ring-shaped sealing material, 7b Ring-shaped sealing material, 8 Sub-frame, 8a Sub-bearing , 8b inflow hole, 9 Oldham mechanism, 9a fixed side key, 9b swinging side key, 9c Oldham mechanism annular part, 10 airtight container, 10a upper space, 10b oil reservoir, 10c glass terminal, 11 refrigerating machine oil, 12 discharge pipe , 13 suction pipe, 14 compression mechanism section, 15 first balance weight, 15a lightweight section, 15b heavy section, 15ba contact surface, 15bb outer peripheral surface, 15c radial passage hole, 15d fastener hole, 16 second balance weight, 16a 2nd weight side channel hole, 17 1st cup-shaped member, 17S internal space, 17a bottom part, 17aa through hole, 17ab 1st cup side channel hole, 17b peripheral surface part, 17c opening part, 17d 2nd discharge part , 17e first discharge part, 17ea discharge hole, 17eb oil guide plate, 17eb1 first notch, 17eb2 second notch, 18 second cup-shaped member, 18S internal space, 18a bottom part, 18aa through hole, 18ab second cup side Channel hole, 18b peripheral surface, 18c opening, 19 discharge cover, 19a opening, 19b opening, 19c second discharge channel, 20 fastener, 30 refrigerant channel, 40 lightweight part side through channel, 50 weight 100 scroll compressor, 101 suction muffler, 103 four-way switching valve, 104 outdoor heat exchanger, 105 pressure reducer, 106 indoor heat exchanger, 200 refrigeration cycle device, 202 arc-shaped wall section, 300 Balance weight, 300S internal space, 301 weight part, 302 arc-shaped wall part, 303 first discharge part, 304 shaft hole, D inner diameter, L1 distance, L2 distance, O center, d inner diameter.

Claims (11)

an airtight container;
a compression mechanism unit disposed in the airtight container and compressing the refrigerant;
an electric motor having a rotor and a stator and driving the compression mechanism;
a drive shaft that transmits the rotational force of the rotor to the compression mechanism section;
a first balance weight disposed between the compression mechanism section and the electric motor and fixed to the rotor;
a first cup-shaped member fixed to the rotor and having a cylindrical peripheral surface surrounding an outer periphery of the first balance weight;
The first balance weight has an arc-shaped lightweight portion and an arc-shaped weight portion that is heavier than the lightweight portion,
The rotor includes a plurality of through passages formed by through holes extending in the axial direction of the drive shaft, and a region of the plurality of through passages that overlaps with the weight portion when viewed in the axial direction is provided in the rotor. When the located through-flow channel is referred to as a heavy section-side through-flow channel, and the other through-flow channels are referred to as a light-weight section-side through-flow channel, the light-weight section side through-flow channel communicates with the internal space of the first cup-shaped member,
The peripheral surface portion of the first cup-shaped member has a first discharge portion on the lightweight portion side that discharges refrigerating machine oil in the first cup-shaped member,
The weight part of the first balance weight is a hole whose one upstream end communicates with the weight part side through flow path and whose other downstream end communicates with the outer circumferential surface of the weight part; It has a radial passage hole that changes the flow direction of the refrigerant including refrigerant oil that has passed through the side through passage from the axial direction to the radial direction,
The circumferential surface portion of the first cup-shaped member is a hole that penetrates the circumferential surface portion in the radial direction at a position opposite to the other downstream end of the radial flow path hole, and the radial flow path A scroll compressor having a second discharge part that discharges refrigerant flowing out from the holes to the outside of the first cup-shaped member. It has a plurality of said weight part side through flow passages, a plurality of said radial flow passage holes are provided corresponding to said plurality of said weight part side through flow passages, and said second discharge part has a plurality of said radial passage holes corresponding to said plurality of said weight part side through flow passages. The scroll compressor according to claim 1, wherein a plurality of directional flow passage holes are provided corresponding to the directional flow passage holes. It has a plurality of said weight part side through passages, one radial flow passage hole is provided in common to the plurality of said weight part side through passages, and said second discharge part has a plurality of said weight part side through passages. 2. The scroll compressor according to claim 1, wherein a plurality of scroll compressors are provided corresponding to the part-side through flow passages. It has a plurality of said weight part side through flow passages, a plurality of said radial flow passage holes are provided corresponding to said plurality of said weight part side through flow passages, and said second discharge part has a plurality of said radial passage holes corresponding to said plurality of said weight part side through flow passages. The scroll compressor according to claim 1, wherein one directional flow passage hole is provided in common. It has a plurality of said weight part side through flow passages, one said radial flow passage hole is provided in common to the plurality of said weight part side through flow passages, and said second discharge part has a plurality of said radial flow passage holes. The scroll compressor according to claim 1, wherein one scroll compressor is provided corresponding to the passage hole. The first discharge portion includes a discharge hole that penetrates the peripheral surface portion of the first cup-shaped member in the radial direction, and an oil guide plate that guides the refrigerating machine oil to the discharge hole. 5. The scroll compressor according to any one of 5. The oil guiding plate includes a first notch extending in the axial direction in the peripheral surface portion of the first cup-shaped member, and a second notch extending in the rotational direction of the drive shaft from both ends of the first notch. 7. The scroll compressor according to claim 6, wherein the scroll compressor has a shape that is cut and raised from the surface portion, and a tip portion of the cut and raised portion is pushed inward in the radial direction and projects. The distance from the tip of the oil guide plate of the first discharge part to the center of the first cup-shaped member is L1, and from the inner periphery of the weight part of the first balance weight to the center of the first cup-shaped member The scroll compressor according to claim 6 or 7, which has a relationship of L1<L2, where L2 is the distance between. The scroll compressor according to any one of claims 1 to 8, wherein the lightweight portion of the first balance weight is divided in the circumferential direction. 10. The scroll compressor according to claim 9, wherein the lightweight portion of the first balance weight has an arc shape with a uniform length in the radial direction. A refrigeration cycle device comprising the scroll compressor, an outdoor heat exchanger, a pressure reducer, and an indoor heat exchanger according to any one of claims 1 to 10.

Images