WO2021245754A1

WO2021245754A1 - Scroll compressor and refrigeration cycle device

Info

Publication number: WO2021245754A1
Application number: PCT/JP2020/021625
Authority: WO
Inventors: 修也福田; 浩二増本; 友寿松井; 祐司 ▲高▼村
Original assignee: 三菱電機株式会社
Priority date: 2020-06-01
Filing date: 2020-06-01
Publication date: 2021-12-09

Abstract

This scroll compressor comprises: a fixed scroll which has a fixed base plate and a fixed spiral protruding part formed on the fixed base plate; and an oscillating scroll which has an oscillating base plate and an oscillating spiral protruding part formed on the oscillating base plate, the oscillating spiral protruding part forming, in combination with the fixed spiral protruding part, a compression chamber. The scroll compressor further comprises a rotating shaft which is linked to the oscillating scroll and has an oil passage through which a lubricating oil flows, and an oscillation-side tip seal which is inserted into an oscillation-side groove formed in the tip end section of the oscillating spiral protruding part. The oscillating scroll is provided with a through hole for supplying, to the oscillation-side groove, the lubricating oil flowing out from the oil passage of the rotating shaft. The oscillation-side tip seal is pressed to the fixed base plate side by the lubricating oil supplied from the through hole to the oscillation-side groove.

Description

Scroll compressor and refrigeration cycle device

The present disclosure relates to a scroll compressor and a refrigerating cycle device used in an air conditioner, a refrigerator, a refrigerator, or the like.

The conventional scroll compressor includes a fixed scroll in which a fixed spiral protrusion is formed on a fixed base plate, and a swing scroll in which a swing spiral protrusion is formed on a rocking base plate. The fixed scroll and the swing scroll are combined so that the spiral protrusions mesh with each other to form a compression chamber. Then, when the oscillating scroll oscillates with respect to the fixed scroll, the refrigerant is sucked into the compression chamber from the radial outside of the spiral protrusion portion, and the refrigerant sucked into the compression chamber is compressed and the spiral protrusion portion. It is discharged from the discharge port opened in the center. This type of scroll compressor has a structure in which lubricating oil is supplied to the inside of the compression chamber in order to improve the lubricity between the swing scroll and the fixed scroll and the sealing property of the compression chamber.

In Patent Document 1, a through hole extending radially outward from the central portion of the swing base plate and opening on the surface of the swing base plate on the spiral protrusion forming side is formed in the swing base plate of the swing scroll. There is. The through hole is opened at a position on the outer side in the radial direction on the surface of the rocking base plate on the side where the spiral protrusion is formed, and the lubricating oil is supplied to the inside of the compression chamber through this opening.

Japanese Unexamined Patent Publication No. 2003-286976

In Patent Document 1, the opening on the downstream side of the through hole for supplying the lubricating oil to the compression chamber is opened on the radial outer side of the rocking base plate. Therefore, the lubricating oil flowing out from the through hole is sucked into the compression chamber together with the refrigerant from the radial outside of the spiral protrusion portion, and spreads throughout the compression chamber. That is, the lubricating oil flowing out from the through hole is not supplied aiming at an effective portion for improving the sealing property of the compression chamber. Therefore, it is doubtful whether the expected improvement in sealing performance can be obtained.

The present disclosure has been made to solve the above-mentioned problems, and an object of the present disclosure is to provide a scroll compressor and a refrigerating cycle device capable of improving the sealing property of a compression chamber by using a lubricating oil. ..

The scroll compressor according to the present disclosure has a fixed base plate and a fixed scroll having a fixed spiral protrusion formed on the fixed base plate, and a swing base plate and a swing spiral protrusion formed on the swing base plate. A oscillating scroll in which the oscillating spiral protrusion is combined with the fixed vortex protrusion to form a compression chamber, a rotating shaft connected to the oscillating scroll and having an oil passage through which lubricating oil flows, and a oscillating spiral protrusion. It is equipped with a swing-side tip seal inserted into the swing-side groove formed at the tip of the portion, and the swing scroll supplies lubricating oil flowing out of the oil passage of the rotating shaft to the swing-side groove. A through hole is provided, and the swing-side chip seal is pressed toward the fixed base plate side by the lubricating oil supplied from the through-hole to the swing-side groove portion.

According to the present disclosure, the lubricating oil flowing out from the oil passage of the rotating shaft is supplied to the swinging gutter through a through hole provided in the swinging scroll, and is arranged in the swinging gutter by the pressure of the lubricating oil. The rocking side tip seal is pressed against the fixed base plate of the fixed scroll. In other words, the lubricating oil is concentrated and supplied to the rocking side tip seal through the through hole with the aim of pressing the rocking side tip seal against the fixed base plate of the fixed scroll, so the lubricating oil is effectively used. Therefore, the sealing performance of the compression chamber can be improved.

It is a front view which showed the appearance of the scroll compressor which concerns on Embodiment 1. FIG. It is a schematic vertical sectional view which showed the internal structure of the scroll compressor which concerns on Embodiment 1. FIG. It is a figure which shows the outline of the structure of the compression mechanism part of Embodiment 1. It is a schematic cross-sectional view of the compression mechanism part of the scroll compressor which concerns on Embodiment 1. FIG. It is an enlarged view of the part surrounded by the dotted line A of FIG. It is a figure which shows the modification 1 of the scroll compressor which concerns on Embodiment 1. FIG. It is a figure which shows the modification 2 of the scroll compressor which concerns on Embodiment 1. FIG. It is a figure which shows the modification 3 of the scroll compressor which concerns on Embodiment 1. FIG. It is a figure which shows the refrigerant circuit of the refrigerating cycle apparatus which concerns on Embodiment 2. FIG.

Hereinafter, embodiments will be described with reference to the drawings. In each figure, the same or corresponding parts are designated by the same reference numerals, and the description thereof will be omitted or simplified as appropriate. In addition, the shape, size, arrangement, etc. of the configurations shown in each figure can be appropriately changed within the scope of the present disclosure.

Embodiment 1.
FIG. 1 is a front view showing the appearance of the scroll compressor according to the first embodiment. FIG. 2 is a schematic vertical sectional view showing the internal structure of the scroll compressor according to the first embodiment. FIG. 3 is a schematic vertical sectional view showing the internal structure of the compression chamber of the scroll compressor according to the first embodiment. FIG. 3 is a diagram showing an outline of the configuration of the compression mechanism portion of the first embodiment, and there is a part that does not strictly correspond to FIG. 2. FIG. 4 is a schematic cross-sectional view of the compression mechanism portion of the scroll compressor according to the first embodiment. The scroll compressor 100 according to the first embodiment is one of the components of a refrigerating cycle used in, for example, a refrigerator, a freezer, an air conditioner, a refrigerating device, a water heater, and the like.

The scroll compressor 100 sucks in the refrigerant circulating in the refrigeration cycle, compresses it, and discharges it in a high temperature and high pressure state. As shown in FIGS. 1 and 2, the scroll compressor 100 includes a shell 1 forming an outer shell, a main frame 2 fixed to the inner wall surface of the shell 1, a compression mechanism unit 3 for compressing a refrigerant, and a compression mechanism. It is provided with an electric motor 6 for driving the unit 3. Further, the scroll compressor 100 further includes a rotating shaft 7 for connecting the compression mechanism unit 3 and the electric motor 6. In the following description, the direction in which the rotating shaft 7 extends is referred to as an axial direction, and the direction perpendicular to the axial direction is referred to as a radial direction.

As shown in FIG. 1, the shell 1 is a conductive member such as metal, and is formed in a cylindrical shape having a closed space. Inside the shell 1, a main frame 2, a compression mechanism unit 3, an electric motor 6, and a rotating shaft 7 are housed.

The shell 1 is composed of a cylindrical main shell 1a, a substantially hemispherical upper shell 1b that closes the upper surface opening of the main shell 1a, and a substantially hemispherical lower shell 1c that closes the lower surface opening of the main shell 1a. .. The upper shell 1b and the lower shell 1c are respectively fixed to the main shell 1a by welding or the like. The shell 1 is supported by a fixing base 1d fixed to the lower shell 1c.

As shown in FIG. 3, the inner wall surface of the main shell 1a is formed below the large-diameter first inner wall surface 10a formed at the upper end portion and the first inner wall surface 10a, and is larger than the inner diameter of the first inner wall surface 10a. It has a second inner wall surface 10b having a small diameter. The step portion 11 formed by the lower end of the first inner wall surface 10a and the upper end of the second inner wall surface 10b functions as a positioning portion of the main frame 2.

As shown in FIGS. 1 and 2, the main shell 1a is provided with a suction pipe 13 for taking in a refrigerant inside the shell 1 and a feeding unit 19 for supplying power to the scroll compressor 100. .. The suction pipe 13 is connected to a hole formed in the side wall of the main shell 1a by brazing or the like with a part inserted. The suction pipe 13 communicates with the low pressure space 16b in the shell 1. The power feeding unit 19 includes a cover 19a, a power feeding terminal 19b, and a wiring 19c. The power feeding terminal 19b is a metal member, one end thereof is arranged so as to be surrounded by the cover 19a, and the other end is arranged inside the main shell 1a. One end of the wiring 19c is connected to the power feeding terminal 19b, and the other end is connected to the motor 6.

A discharge pipe 14 for discharging the compressed refrigerant from the shell 1 is connected to the upper shell 1b. The discharge pipe 14 is connected to a hole formed in the upper part of the upper shell 1b by brazing or the like with a part inserted. Further, an oil reservoir 18 for storing lubricating oil is provided on the inner bottom portion of the shell 1.

As shown in FIGS. 2 and 3, the main frame 2 is a cylindrical metal frame that gradually tapers downward, and supports the swing scroll 5 swingably. The central portion of the main frame 2 is a shaft hole through which the rotating shaft 7 passes. The outer peripheral surface of the main frame 2 is fixed to the inner wall surface of the main shell 1a by, for example, shrink fitting. An annular flat surface 20 is formed on the upper surface of the main frame 2. A ring-shaped thrust plate 25 made of a steel plate-based material such as valve steel is arranged on the flat surface 20. The thrust plate 25 functions as a thrust sliding surface of the main frame 2 and supports the thrust load of the compression mechanism portion 3.

Further, as shown in FIGS. 2 and 3, the accommodating portion 21 is formed inside the main frame 2. The main frame 2 includes a main bearing portion 22 that supports the rotating shaft 7. The accommodating portion 21 is formed on the upper side of the main frame 2. The main bearing portion 22 is provided on the lower side of the main frame 2.

As shown in FIGS. 2 and 3, the accommodating portion 21 is formed so that the inner diameter gradually decreases downward. As shown in FIG. 3, in the accommodating portion 21, the stepped portion located on the flat surface 20 side is the oldham accommodating portion 21a, and the stepped portion located on the main bearing portion 22 side is the bush accommodating portion 21b. Further, a pair of key grooves formed so as to face each other with the shaft hole of the main frame 2 interposed therebetween are provided in a part of the Oldam accommodating portion 21a and the flat surface 20.

Further, as shown in FIG. 2, the main frame 2 is formed with an oil return hole 23 penetrating inside and outside. The oil return hole 23 communicates with the bush accommodating portion 21b. An oil return pipe 24 is inserted and fixed in the oil return hole 23. The oil return pipe 24 is provided to return the lubricating oil accumulated in the accommodating portion 21 to the oil reservoir 18 provided in the lower shell 1c. The oil return hole 23 and the oil return pipe 24 are not limited to one, and a plurality of oil return holes 23 may be provided.

As shown in FIGS. 2 and 3, the fixed scroll 4 has a disk-shaped fixed base plate 4a and a fixed spiral protrusion portion 4b formed on the lower surface of the fixed base plate 4a. The swing scroll 5 has a disk-shaped swing base plate 5a and a swing spiral protrusion 5b formed on the upper surface of the swing base plate 5a and meshing with the fixed spiral protrusion 4b. The swing scroll 5 is installed so as to be eccentric with respect to the fixed scroll 4. The fixed spiral protrusion 4b of the fixed scroll 4 and the swing spiral protrusion 5b of the swing scroll 5 are combined to form a compression chamber 30 for compressing the refrigerant.

The fixed scroll 4 is made of a metal such as cast iron. The fixed scroll 4 is fixed by fastening the fixed base plate 4a to the upper part of the main frame 2, for example, by bolting.

A discharge port 40 for discharging a compressed, high-temperature and high-pressure refrigerant is formed in the central portion of the fixed base plate 4a. On the upper surface of the fixed scroll 4, a chamber 15 having a discharge hole 15a communicating with the discharge port 40 is arranged. The chamber 15 is provided with a discharge valve 17 screwed to open and close the discharge hole 15a according to the pressure of the refrigerant. The discharge valve 17 opens the discharge hole 15a when the refrigerant in the compression chamber 30 communicating with the discharge port 40 reaches a predetermined pressure. The compressed high-temperature and high-pressure refrigerant is discharged from the discharge port 40 into the high-pressure space 16a above the fixed scroll 4, passes through the discharge pipe 14, and is discharged to the outside of the shell 1. Further, as shown in FIG. 3, a fixed side groove portion 42 is formed at the tip of the fixed spiral protrusion portion 4b along the spiral direction, and the fixed side groove portion 42 is formed with, for example, a fixed side tip made of hard plastic. The seal 41 is inserted. The radial width of the fixed-side groove portion 42 (left-right direction in FIG. 3) is larger than the radial width of the fixed-side chip seal 41.

The swing scroll 5 is made of a metal such as aluminum. As shown in FIG. 2, the swing scroll 5 revolves with respect to the fixed scroll 4 without rotating with respect to the fixed scroll 4 by the old dam ring 54 for blocking the rotation. The surface (lower surface in the case of the illustrated example) on the side of the rocking base plate 5a on which the swinging spiral protrusion 5b is not formed acts as a swinging scroll thrust bearing surface.

A cylindrical boss portion 51 is provided at the center of the swing scroll thrust bearing surface. On the inner peripheral surface of the boss portion 51, a swing bearing that rotatably supports the slider 80 of the bush 8 described later is provided. The plain bearing is a so-called journal bearing. The oscillating bearing is provided so that the central axis is parallel to the central axis of the rotating shaft 7. The oscillating scroll 5 revolves on the thrust sliding surface of the main frame 2 by rotating the eccentric shaft portion 71, which will be described later, of the rotating shaft 7 inserted into the boss portion 51.

Further, as shown in FIG. 3, a swing gutter 55 is formed at the tip of the swing spiral protrusion 5b along the spiral direction, and the swing gutter 55 is made of, for example, hard plastic. The rocking side tip seal 52 is movably inserted in the axial direction (vertical direction in FIG. 3). The radial width of the swing-side groove portion 55 (left-right direction in FIG. 3) is larger than the radial width of the swing-side tip seal 52.

As shown in FIG. 2, the swing scroll thrust bearing surface is provided with a pair of old dam grooves 53 formed so as to face each other with the boss portion 51 interposed therebetween. The old dam groove 53 is an oval key groove. The pair of Oldham grooves 53 are arranged so that the lines connecting them are orthogonal to the lines connecting the key grooves of the main frame 2.

As shown in FIG. 2, the oldam ring 54 includes a ring portion 54a and a key portion 54b. The ring portion 54a is annular and is provided in the old dam accommodating portion 21a of the main frame 2. Two key portions 54b are provided on the lower surface and the upper surface of the ring portion 54a. The key portion 54b provided on the lower surface of the ring portion 54a is housed in the key groove of the main frame 2, and the key portion 54b provided on the upper surface of the ring portion 54a is housed in the old dam groove 53 of the swing scroll 5. Has been done. By aligning the old dam groove 53 of the swing scroll 5 with the key portion 54b of the old dam ring 54, the position of the swing spiral protrusion portion 5b of the swing scroll 5 in the rotational direction is determined. That is, the old dam ring 54 positions the swing scroll 5 with respect to the main frame 2, and determines the phase of the swing spiral protrusion 5b with respect to the main frame 2.

In the compression chamber 30, the fixed-side tip seal 41 provided at the tip of the fixed spiral protrusion 4b and the rocking base plate 5a come into contact with each other, and the swing-side tip seal provided at the tip of the swinging spiral protrusion 5b. The 52 and the fixed base plate 4a are in contact with each other to be sealed. The compression chamber 30 is composed of a plurality of compression chambers 30 whose volume decreases from the outside to the inside in the radial direction of the scroll.

As the refrigerant, for example, a halogenated hydrocarbon having a carbon double bond, a halogenated hydrocarbon having no carbon double bond, a natural refrigerant, or a mixture containing them can be used in the composition. Examples of the halogenated hydrocarbon having a carbon double bond include _{HFO refrigerants such as R1234yf (CF 3} CF = CH ₂ ), R1234ze (CF ₃ CH = CHF) or R1233zd (CF ₃ CH = CHCl). The halogenated hydrocarbons having no carbon double bond are R32 (CH ₂ F ₂ ), R 41 (CH ₃ F), R125 (C ₂ HF ₃ ), R134a (CH ₂ FCF ₂ ), R143a (CF ₃ CH). ₃ ), HFC refrigerants such as R410A (R32 / R125) or R407C (R32 / R125 / R134a) can be mentioned. An example is a refrigerant mixed with R32 (difluoromethane), R41, etc. represented by CH ₂ F _2. Natural refrigerants are ammonia (NH ₃ ), carbon dioxide (CO ₂ ), propane (C ₃ H ₈ ), propylene (C ₃ H ₆ ), butane (C ₄ H ₁₀ ) or isobutane (CH (CH ₃ ) ₃ ). And so on. The refrigerant is preferably a low GWP refrigerant having an ozone depletion potential of zero.

As shown in FIG. 2, the electric motor 6 drives the compression mechanism unit 3 connected via the rotating shaft 7. The electric motor 6 has an annular stator 6a fixedly supported on the inner wall surface of the shell 1 by shrink fitting or the like, and a rotor 6b rotatably attached to face the inner side surface of the stator 6a. The stator 6a has a structure in which windings are wound around an iron core formed by laminating a plurality of electrical steel sheets, for example, via an insulating layer, and is formed in a ring shape in a plan view. The rotor 6b has a structure in which a permanent magnet is built in an iron core formed by laminating a plurality of electromagnetic steel sheets, and has a through hole penetrating in the vertical direction in the center.

As shown in FIGS. 2 and 3, the rotating shaft 7 is a metal rod-shaped member. The rotating shaft 7 includes a spindle portion 70 and an eccentric shaft portion 71. The spindle portion 70 is an axis constituting the main portion of the rotating shaft 7, and is arranged in the shell 1 so that the central axis thereof coincides with the central axis of the main shell 1a. The spindle portion 70 is fixed to the through hole at the center of the rotor 6b by shrink fitting or the like. The spindle portion 70 is rotated by a main bearing portion 22 provided in the central portion of the main frame 2 and an auxiliary bearing portion 90 provided in the central portion of the subframe 9 fixed to the lower part of the shell 1 by welding or the like. It is supported freely.

The eccentric shaft portion 71 is provided at the upper end portion of the spindle portion 70 so that the central shaft thereof is eccentric with respect to the central axis of the spindle portion 70. The eccentric shaft portion 71 is connected to the swing scroll 5 via a bush 8 which is a metal member such as iron, and is rotatably supported by the boss portion 51 of the swing scroll 5. The rotary shaft 7 rotates with the rotation of the rotor 6b, and the swing scroll 5 is swiveled by the eccentric shaft portion 71. Further, inside the spindle portion 70 and the eccentric shaft portion 71, an oil passage 72 is provided along the axial direction and penetrates to both end faces in the axial direction of the rotating shaft 7.

As shown in FIGS. 2 and 3, the bush 8 includes a slider 80 and a balance weight 81a. The slider 80 is a tubular member on which a collar is formed, and is rotatably inserted into the boss portion 51. An eccentric shaft portion 71 is inserted inside the slider 80. That is, the slider 80 is interposed between the swing scroll 5 and the eccentric shaft portion 71, the swing radius of the swing scroll 5 is variable, and the swing scroll 5 is revolved in order to revolve the swing scroll 5. Is to be supported.

The balance weight 81a is provided to cancel the centrifugal force of the swing scroll 5 generated by the swing motion. The balance weight 81a is annular and is formed in a substantially C shape when viewed in a plane on the side opposite to the direction of the centrifugal force acting on the swing scroll 5. The scroll compressor 100 can reduce the pressure of the swinging spiral protrusion 5b against the fixed spiral protrusion 4b by the balance weight 81a. The balance weight 81a is fixed to the collar of the slider 80, for example, by shrink fitting or the like.

The subframe 9 is a metal frame. As shown in FIG. 2, the subframe 9 is provided with an auxiliary bearing portion 90 and an oil pump 91. The sub-bearing portion 90 is a ball bearing provided in the center of the sub-frame 9. The oil pump 91 is a pump for sucking up the lubricating oil stored in the oil reservoir 18 of the shell 1, and is provided under the auxiliary bearing portion 90.

Lubricating oil is stored in the oil reservoir 18. Lubricating oil is sucked up by the oil pump 91, passes through the oil passage 72 of the rotating shaft 7, and reduces wear between mechanically contacting parts such as the compression mechanism portion 3, temperature control of the sliding portion, and sealing performance. Make improvements. As the lubricating oil, an oil having excellent lubrication characteristics, electrical insulation, stability, refrigerant solubility, low temperature fluidity and the like, and having an appropriate viscosity is suitable. As the lubricating oil, for example, naphthenic, polyol ester (POE), polyvinyl ether (PVE) or polyalkylene glycol (PAG) oil can be used.

Next, the operation of the scroll compressor 100 will be described.
When the power feeding unit 19 is energized, the rotor 6b of the electric motor 6 rotates. Along with this, the rotary shaft 7 fixed to the rotor 6b is rotationally driven. When the rotation shaft 7 is rotationally driven, the swing scroll 5 of the compression mechanism unit 3 is restricted from rotating by the old dam ring 54 and swings.

Along with the drive of the compression mechanism unit 3, the refrigerant is sucked into the shell 1 through the suction pipe 13 and is taken into the compression chamber 30. The compression chamber 30 that has taken in the refrigerant reduces the volume while moving from the outer peripheral portion toward the center along with the rocking motion of the rocking scroll 5, and compresses the refrigerant. The refrigerant compressed in the compression chamber 30 is discharged from the discharge port 40 provided in the fixed scroll 4 into the high-pressure space 16a, and is discharged from the discharge pipe 14 to the outside of the shell 1.

During the operation of the scroll compressor 100, lubricating oil is supplied to each sliding portion of the compression mechanism portion 3. Specifically, when the rotary shaft 7 is rotationally driven, the lubricating oil stored in the oil reservoir 18 of the shell 1 is pumped up by the oil pump 91. The pumped lubricating oil flows in through the opening on the upstream side of the oil passage 72 formed in the rotary shaft 7, and flows out through the opening on the downstream side. The lubricating oil that has flowed out from the opening on the downstream side of the oil passage 72 flows into the inner space of the boss portion 51. A part of the lubricating oil that has flowed into the inner space of the boss portion 51 lubricates the swing bearing. A part of the lubricating oil that lubricates the oscillating bearing is supplied to the thrust plate 25 and then flows into the compression mechanism unit 3 to seal the compression chamber 30. The rest of the lubricating oil that lubricated the oscillating bearing lubricates the spindle portion and the like and returns to the oil reservoir 18.

Here, when the swing scroll 5 is swinging, the fixed-side tip seal 41 is pressed against the swing base plate 5a of the swing scroll 5 due to the pressure difference between the adjacent compression chambers and slides. do. Similarly, the rocking side tip seal 52 is pressed against the fixed base plate 4a of the fixed scroll 4 due to the pressure difference between the adjacent compression chambers and slides. Specifically, this pressure difference will be described by focusing on the portion surrounded by the dotted line A in FIG. 3. The compression chamber 301 on the center side of the rocking scroll 5 and one radial direction from the compression chamber 301. It is a pressure difference with the outer compression chamber 302.

The fixed side tip seal 41 and the rocking side tip seal 52 are also pressed to the outside in the radial direction due to this pressure difference. Therefore, as shown in FIG. 3, the fixed-side chip seal 41 is radially outward in the fixed-side groove portion 42, and the radial outer side surface 41a of the fixed-side chip seal 41 is the same as the fixed-side groove portion 42. It is in contact with the side surface on the directional side. Similarly, the swing-side tip seal 52 is radially outward in the swing-side groove portion 55, and the radial outer side surface 52a of the swing-side tip seal 52 is on the same direction side of the swing-side groove portion 55. It is in contact with the side surface.

As described above, the compression chamber 30 is sealed by pressing the fixed side chip seal 41 and the rocking side chip seal 52 against the opposing base plates, and the leakage of the compressed refrigerant between the adjacent compression chambers is suppressed. Will be done. At this time, the larger the amount of the lubricating oil taken into the compression chamber 301 and the compression chamber 302, the better the sealing property.

The first embodiment has a structure in which the lubricating oil is efficiently used to further enhance the sealing property of the compression chamber 30. Hereinafter, this structure will be described with reference to FIG.

The swing scroll 5 is formed with a through hole 58 that communicates the space inside the boss portion 51 with the swing side groove portion 55 formed in the swing spiral protrusion portion 5b. As shown in FIG. 3, the through hole 58 has a vertical hole 57 provided in the swing spiral protrusion 5b and a horizontal hole 56 provided in the swing base plate 5a. As shown in FIGS. 3 and 4, two vertical holes 57 are provided symmetrically about the eccentric shaft portion 71 on the radial outer portion of the swing spiral protrusion portion 5b. The vertical hole 57 communicates with the swing gutter 55. The horizontal hole 56 is provided corresponding to each vertical hole 57, and communicates the vertical hole 57 with the space inside the boss portion 51. Similar to the vertical hole 57, two horizontal holes 56 are provided symmetrically about the eccentric shaft portion 71 as shown in FIGS. 3 and 4. The lateral hole 56 is opened on the outer peripheral surface of the rocking base plate 5a, and this opening is closed by the set screw 59.

The operation of the through hole 58 configured in this way will be described with reference to FIG. 5 below. FIG. 5 is an enlarged view of the portion surrounded by the dotted line A in FIG. In FIG. 5, the dotted arrow indicates the flow of lubricating oil.

As described above, the lubricating oil that has flowed out from the opening on the downstream side of the oil passage 72 flows into the space inside the boss portion 51. A part of the lubricating oil that has flowed into the space inside the boss portion 51 passes through the horizontal hole 56 and the vertical hole 57 of the through hole 58 as shown by the dotted line arrow in FIG. It is supplied to 52. Since the set screw 59 (see FIG. 3) is provided in the radially outer opening of the horizontal hole 56, the lubricating oil that has flowed into the horizontal hole 56 does not flow out from this opening but flows into the vertical hole 57. ..

By supplying the lubricating oil to the rocking side chip seal 52 in this way, the pressure in the direction of the solid arrow in FIG. 5 acts on the rocking side chip seal 52. Due to this pressure, the swing-side tip seal 52 rises from the swing-side groove portion 55 and is pressed against the fixed base plate 4a. Here, a gap 303 having a size equal to or less than the thickness of the swing-side tip seal 52 is provided between the tip surface of the swing spiral protrusion 5b and the fixed base plate 4a. When the rocking-side chip seal 52 is pressed against the fixed base plate 4a, the gap 303 is closed by the rocking-side chip seal 52, so that the sealing performance of the compression chamber 30 is improved. As a result, it is possible to further suppress the leakage of the refrigerant from the compression chamber 301 to the compression chamber 302 through the gap 303. Then, the lubricating oil supplied to the swing-side groove portion 55 and causing the swing-side tip seal 52 to rise is the radial inner side surface 52b of the swing-side tip seal 52 and the side surface in the same direction of the swing-side groove portion 55. It is ejected into the compression chamber 301 from the gap between the two.

As described above, in the first embodiment, since the swing scroll 5 is provided with the through hole 58, the lubricating oil flowing out from the oil passage 72 of the rotating shaft 7 flows through the swing hole 58 to the swing gutter portion. It is concentrated and supplied to the rocking side chip seal 52 of 55. The hydraulic pressure of the lubricating oil supplied to the swing-side tip seal 52 acts as a force for pressing the swing-side tip seal 52 against the fixed base plate 4a. As a result, compared to the conventional structure in which the opening on the downstream side of the through hole 58 is provided on the radial outer peripheral side of the rocking base plate 5a, in the first embodiment, the rocking side tip seal 52 is attached to the fixed base plate 4a. The pressing force can be increased and the sealing performance can be improved. Further, in the first embodiment, since two vertical holes 57 of the through hole 58 are provided at symmetrical positions about the eccentric shaft portion 71, a well-balanced pressing force is applied to the swing-side tip seal 52. Can act.

Here, the flow velocity of the lubricating oil ejected from the swing gutter 55 to the compression chamber 301 can be adjusted by the diameter of the vertical hole 57. For example, the smaller the diameter of the vertical hole 57, the faster the flow velocity of the lubricating oil ejected from the vertical hole 57 through the swing gutter portion 55. As the flow velocity of the lubricating oil increases, the force for pressing the rocking side tip seal 52 against the fixing base plate 4a becomes stronger, and the sealing property can be improved.

By the way, it is said that the vertical hole 57 is formed in the radial outer portion of the swinging spiral protrusion 5b, and the reason and the more detailed position of the vertical hole 57 will be described below. Since the space inside the boss portion 51 is a part of the low pressure space 16b, the pressure in the space inside the boss portion 51 is lower than the pressure in the compression chamber 30. The pressure in the compression chamber 30 increases as it approaches the vicinity of the center of the swing scroll 5. Therefore, the pressure difference between the pressure of the compression chamber 30 near the center of the swing scroll 5 and the pressure of the space inside the boss portion 51 is the pressure of the compression chamber 30 outside the radial direction of the swing scroll 5 and the pressure inside the boss portion 51. It is higher than the pressure difference with the pressure in the space. Therefore, if the position of the vertical hole 57 is set near the center of the spiral in the swing spiral protrusion 5b, the pressure of the compression chamber (hereinafter referred to as the communication compression chamber) through which the vertical hole 57 communicates through the swing gutter 55 is increased. It becomes higher than the pressure of the space in the boss portion 51 with a large difference. Then, the lubricating oil in the communication compression chamber may flow back toward the space inside the boss portion 51 via the through hole 58. Therefore, the position of the vertical hole 57 is set to the radial outer portion in the oscillating spiral protrusion 5b so as not to cause the backflow of the lubricating oil.

To prevent backflow of lubricating oil, the position of the vertical hole 57 is set so that the pressure in the communication compression chamber is lower than the pressure of the lubricating oil supplied from the vertical hole 57 to the rocking side chip seal 52. do it. The pressure difference between the pressure in the communication compression chamber and the pressure in the boss portion 51 becomes smaller as the position of the vertical hole 57 is radially outward from the center of the spiral. Therefore, when setting the position of the vertical hole 57, a compression chamber 30 having a pressure smaller than the pressure of the lubricating oil ejected from the vertical hole 57 to the communication compression chamber via the swing side groove portion 55 is specified and specified. It may be outside the compression chamber 30 in the radial direction. FIG. 4 shows an example in which a vertical hole 57 is provided at a winding end portion of the swing spiral protrusion 5b and a position symmetrical with respect to the eccentric shaft portion 71 at the winding end portion.

Although the number of vertical holes 57 is set to two in FIG. 4, the number of vertical holes 57 is not limited to two. Any number of vertical holes 57 may be provided in the swing scroll 5 as long as the backflow of the lubricating oil is not caused. As the number of vertical holes 57 increases, the amount of lubricating oil supplied to the inside of the compression chamber 30 increases, so that the sealing property is improved. However, if the number of vertical holes 57 is too large, the amount of lubricating oil supplied to the inside of the compression chamber 30 increases too much, and the amount of lubricating oil taken out from the scroll compressor 100 increases. When the amount of lubricating oil taken out from the scroll compressor 100 increases, the amount of lubricating oil flowing into the heat exchanger arranged downstream of the scroll compressor 100 in the refrigeration cycle increases, and the heat exchange efficiency in the heat exchanger increases. May decrease. Further, if the number of the vertical holes 57 is increased, the processing cost may be increased accordingly. Therefore, the number of vertical holes 57 may be set to an appropriate number in consideration of the amount of lubricating oil and the processing cost.

Next, the relationship between the operating frequency of the scroll compressor 100 and the sealing property of the rocking side chip seal 52 will be described. The sealing property of the rocking side tip seal 52 depends on the amount of lubricating oil sucked up by the oil pump 91. Specifically, the larger the amount of lubricating oil, the better the sealing property, and the smaller the amount of lubricating oil, the lower the sealing property. Therefore, when the operating frequency of the scroll compressor 100 is low and the amount of lubricating oil sucked up is reduced, the diameter of the vertical hole 57 of the through hole 58 is reduced. Specifically, for example, the diameter of the vertical hole 57 is made smaller than the diameter of the horizontal hole 56. As a result, the flow velocity of the lubricating oil ejected from the vertical hole 57 to the compression chamber 301 through the swing side groove portion 55 becomes high, and the force for pressing the swing side tip seal 52 against the fixed base plate 4a increases to improve the sealing performance. can.

On the other hand, when the operating frequency of the scroll compressor 100 is high and the amount of lubricating oil sucked up is large, the force for pressing the rocking side tip seal 52 against the fixed base plate 4a works sufficiently to ensure the sealing property. Here, in the first embodiment, the lubricating oil in the vertical hole 57 is configured to be ejected into the compression chamber 30 through the swing gutter portion 55. Therefore, even if the operating frequency is high and a large amount of lubricating oil is supplied into the vertical hole 57, the lubricating oil is ejected into the compression chamber 30 through the swing gutter portion 55 and does not stay in the vertical hole 57.

If the lubricating oil stays in the vertical hole 57, specifically, the rocking gutter 52 does not rise from the rocking gutter 55, the following problems may occur when the operating frequency is high. .. That is, when the operating frequency is high, the amount of lubricating oil supplied into the vertical hole 57 increases, and the lubricating oil stays in the vertical hole 57 so that the lubricating oil can be applied to the fixing base plate 4a of the rocking side tip seal 52. The pressing force may be excessive. In this case, the swing-side tip seal 52 is worn. However, in the first embodiment, the rocking side tip seal 52 floats up from the rocking side groove portion 55, and the lubricating oil in the vertical hole 57 is ejected to the compression chamber 30 through the rocking side groove portion 55. There is no concern about wear of the rocking side chip seal 52.

From the above viewpoint, it is desirable that the lubricating oil in the vertical hole 57 is ejected to the compression chamber 30 through the swing side groove portion 55, but depending on the usage mode, the swing side tip may be used in a range where the operating frequency is not high. No wear of the seal 52 occurs. Therefore, the present disclosure also includes a configuration in which the lubricating oil in the vertical hole 57 is not ejected into the compression chamber 30 through the swing gutter portion 55.

The scroll compressor 100 of the present disclosure is not limited to the structure shown in FIGS. 1 to 5, and can be modified as follows, for example, within the range not deviating from the gist of the present disclosure. Is.

(Deformation Example 1 and Deformation Example 2: Position of the vertical hole 57 in the thickness direction of the swinging spiral protrusion 5b)
FIG. 6 is a diagram showing a modification 1 of the scroll compressor according to the first embodiment. FIG. 7 is a diagram showing a modification 2 of the scroll compressor according to the first embodiment.
The position of the vertical hole 57 in the thickness direction of the swinging spiral protrusion 5b was the central portion in the thickness direction of the swinging spiral protrusion 5b in FIG. 3 and the like above, but as shown in FIG. 6, it deviates from the central portion. May be. FIG. 6 shows an example in which a vertical hole 57 is provided at a position on the radial side of the central portion, in other words, on the side where the rocking side tip seal 52 approaches during operation. In this way, by providing the vertical hole 57 closer to the side where the swing-side tip seal 52 is closer during operation, the lubricating oil that has passed through the vertical hole 57 can be more concentrated and supplied to the swing-side tip seal 52. can. As a result, the pressing force of the swing-side tip seal 52 against the fixed base plate 4a can be further improved.

Further, as shown in FIG. 7, the vertical hole 57 may be provided so as to be inclined with respect to the axial direction. In FIG. 7, a vertical hole 57 is provided so as to incline outward in the radial direction from the upstream side to the downstream side of the vertical hole 57, in other words, to incline toward the swinging side tip seal 52 during operation. An example is shown. Further, in FIG. 7, the facing surface 52c of the swing-side tip seal 52 with the vertical hole 57 is a vertical surface perpendicular to the axial direction of the vertical hole 57. As a result, the pressure due to the lubricating oil flowing out from the vertical hole 57 is applied vertically to the facing surface 52c. As a result, the pressing force of the swing-side tip seal 52 against the fixed base plate 4a can be further improved.

(Deformation example 3: Combination with a refueling hole for refueling the thrust surface)
FIG. 8 is a diagram showing a modification 3 of the scroll compressor according to the first embodiment.
In the modified example 3, in addition to the configuration shown in FIG. 3, a lubrication hole 62 is further formed in the rocking base plate 5a. The lubrication hole 62 is a hole for supplying lubricating oil to the thrust surface of the swing scroll 5, and has a conventional configuration. In the example of FIG. 8, since the thrust plate 25 is arranged on the thrust surface of the swing scroll 5, the lubrication hole 62 specifically supplies the lubricating oil to the thrust plate 25. The refueling hole 62 has a horizontal hole 60 and an oblique hole 61.

When the through hole 58 of the first embodiment is applied to the scroll compressor provided with such a refueling hole 62, the through hole 58 is provided independently of the refueling hole 62 as shown in FIG. prepare. If the horizontal hole 60 of the refueling hole 62 is shared with the horizontal hole 56 of the through hole 58, the lubricating oil flowing into the horizontal hole 60 will flow preferentially to the diagonal hole 61 and will flow to the vertical hole 57 of the through hole 58. This is because it disappears.

According to this configuration, in addition to the effect of improving the sealing property by the through hole 58, it is possible to obtain the effect of being able to supply sufficient lubricating oil to the thrust plate 25.

As described above, the scroll compressor 100 of the first embodiment has a fixed scroll 4 having a fixed base plate 4a and a fixed spiral protrusion 4b formed on the fixed base plate 4a, a swing base plate 5a, and a rocking base plate 4a. It has a swinging spiral protrusion 5b formed on the moving table plate 5a, and includes a swinging scroll 5 in which the swinging spiral protrusion 5b is combined with the fixed spiral protrusion 4b to form a compression chamber 30. The scroll compressor 100 is further connected to the swing scroll 5 and inserted into a rotary shaft 7 having an oil passage 72 through which lubricating oil flows and a swing gutter portion 55 formed at the tip of the swing spiral protrusion 5b. The rocking side chip seal 52 is provided. The swing scroll 5 is provided with a through hole 58 for supplying the lubricating oil flowing out from the oil passage 72 of the rotary shaft 7 to the swing side groove portion 55. The swing-side tip seal 52 is pressed toward the fixed base plate 4a by the lubricating oil supplied from the through hole 58 to the swing-side groove portion 55.

As a result, the lubricating oil is concentrated and supplied to the rocking side chip seal 52 through the through hole 58 with the aim of pressing the rocking side chip seal 52 against the fixed base plate 4a of the fixed scroll 4, so that lubrication is performed. The oil can be effectively used to improve the sealing performance of the compression chamber 30.

Further, the scroll compressor 100 of the first embodiment is provided on the surface of the rocking base plate 5a on the side opposite to the surface on which the rocking spiral protrusion 5b is formed, and the eccentric shaft portion 71 of the rotating shaft 7 is inserted. A cylindrical boss portion 51 is provided. The space inside the boss portion 51 communicates with the oil passage 72 of the rotating shaft 7. The through hole 58 is a vertical hole 57 formed in the swing spiral protrusion portion 5b and communicating with the swing side groove portion 55, and a horizontal hole formed in the swing base plate 5a and communicating the vertical hole 57 and the space in the boss portion 51. Has 56.

As described above, the through hole 58 for supplying the lubricating oil flowing out from the oil passage 72 of the rotary shaft 7 to the swing gutter portion 55 is formed in the vertical hole 57 and the swing base plate 5a formed in the swing spiral protrusion portion 5b. It can be configured by the formed lateral hole 56.

The swing-side chip seal 52 is movably arranged in the swing-side groove portion 55 in the axial direction of the rotary shaft 7, and the swing-side chip seal 52 is provided with the lubricating oil supplied from the vertical hole 57 to the swing-side chip seal 52. The pressure of the communicating compression chamber, which is the compression chamber 30 through which the vertical hole 57 communicates, is lower than the pressure of the lubricating oil supplied from the vertical hole 57 to the rocking side chip seal 52. , The position of the vertical hole 57 is set.

Thereby, the rocking side tip seal 52 can be stably pressed against the fixed base plate 4a of the fixed scroll 4 by the lubricating oil.

The vertical hole 57 is provided in the swinging spiral protrusion 5b closer to the outer side in the radial direction than the central portion in the thickness direction. Alternatively, the vertical hole 57 is provided in the swinging spiral protrusion 5b so as to be inclined toward the outside in the radial direction from the upstream side to the downstream side of the flow of the lubricating oil.

As a result, the pressing force of the swing-side tip seal 52 against the fixed base plate 4a can be further improved.

In the rocking base plate 5a, a lubrication hole 62 for supplying the lubricating oil flowing out from the oil passage 72 of the rotating shaft 7 to the thrust surface of the rocking scroll 5 is formed independently of the through hole 58.

As a result, in addition to the effect of improving the sealing property by the through hole 58, it is possible to obtain the effect of being able to supply sufficient lubricating oil to the thrust surface of the swing scroll 5.

Two vertical holes 57 are provided at symmetrical positions about the eccentric shaft portion 71, and two horizontal holes 56 are provided corresponding to each vertical hole 57.

As a result, the pressing force can be applied to the swinging side tip seal 52 in a well-balanced manner.

Embodiment 2.
The second embodiment relates to a refrigeration cycle apparatus provided with the scroll compressor 100 of the first embodiment.

FIG. 9 is a diagram showing a refrigerant circuit of the refrigeration cycle device according to the second embodiment.
The refrigerating cycle device 110 includes the scroll compressor 100 of the first embodiment, a condenser 111, an expansion valve 112 as a depressurizing device, and an evaporator 113. The gas refrigerant discharged from the scroll compressor 100 flows into the condenser 111, exchanges heat with the air passing through the condenser 111, and flows out as a high-pressure liquid refrigerant. The high-pressure liquid refrigerant flowing out of the condenser 111 is depressurized by the expansion valve 112 to become a low-pressure gas-liquid two-phase refrigerant, and flows into the evaporator 113. The low-pressure gas-liquid two-phase refrigerant flowing into the evaporator 113 exchanges heat with the air passing through the evaporator 113 to become a low-pressure gas refrigerant, and is sucked into the scroll compressor 100 again.

The refrigerating cycle device 110 configured in this way is provided with the scroll compressor 100 of the first embodiment, so that the amount of lubricating oil discharged from the scroll compressor 100 together with the refrigerant at high speed can be adjusted to an appropriate amount. Therefore, the inconvenience that the heat exchange efficiency is lowered in the condenser 111 can be suppressed, and the refrigeration cycle device 110 having high heat exchange efficiency can be configured.

The refrigerating cycle device 110 can be applied to an air conditioner, a refrigerator, a refrigerator, or the like.

1 shell, 1a main shell, 1b upper shell, 1c lower shell, 1d fixed base, 2 main frame, 3 compression mechanism, 4 fixed scroll, 4a fixed base plate, 4b fixed spiral protrusion, 5 swing scroll, 5a swing Base plate, 5b swinging spiral protrusion, 6 electric motor, 6a stator, 6b rotor, 7 rotating shaft, 8 bush, 9 subframe, 10a first inner wall surface, 10b second inner wall surface, 11 steps, 13 suction pipe, 14 discharge pipe, 15 chamber, 15a discharge hole, 16a high pressure space, 16b low pressure space, 17 discharge valve, 18 oil reservoir, 19 power supply part, 19a cover, 19b power supply terminal, 19c wiring, 20 flat surface, 21 accommodation part, 21a Oldham accommodating part, 21b bush accommodating part, 22 main bearing part, 23 oil return hole, 24 oil return pipe, 25 thrust plate, 30 compression chamber, 40 discharge port, 41 fixed side chip seal, 42 fixed side groove part, 51 boss part, 52 swinging side chip seal, 52a facing surface, 52c facing surface, 53 oldam groove, 54 oldam ring, 54a ring part, 54b key part, 55 swinging side groove part, 56 horizontal hole, 57 vertical hole, 58 through hole, 59 set screw , 60 horizontal hole, 61 diagonal hole, 62 refueling hole, 70 spindle part, 71 eccentric shaft part, 72 oil passage, 80 slider, 81a balance weight, 90 auxiliary bearing part, 91 oil pump, 100 scroll compressor, 110 refrigeration cycle Equipment, 111 condenser, 112 expansion valve, 113 evaporator, 301 compression chamber, 302 compression chamber, 303 gap.

Claims

A fixed base plate and a fixed scroll having a fixed spiral protrusion formed on the fixed base plate,
A swing scroll having a swing base plate and a swing spiral protrusion formed on the swing base plate, and the swing spiral protrusion is combined with the fixed spiral protrusion to form a compression chamber.
A rotating shaft connected to the swing scroll and having an oil passage through which lubricating oil flows,
It is provided with a swinging side tip seal inserted into the swinging side groove formed at the tip of the swinging spiral protrusion.
The swing scroll is provided with a through hole for supplying the lubricating oil flowing out from the oil passage of the rotary shaft to the swing gutter portion.
The rocking side tip seal is a scroll compressor that is pressed toward the fixed base plate side by the lubricating oil supplied from the through hole to the rocking side groove portion.
The rocking base plate is provided on a surface opposite to the surface on which the swinging spiral protrusion is formed, and has a cylindrical boss portion into which the eccentric shaft portion of the rotating shaft is inserted.
The space inside the boss portion communicates with the oil passage of the rotating shaft.
The through hole is a vertical hole formed in the swinging spiral protrusion portion and communicating with the swinging gutter portion, and a horizontal hole formed in the swinging base plate and communicating between the vertical hole and the space in the boss portion. The scroll compressor according to claim 1.
The swing-side chip seal is movably arranged in the swing-side groove portion in the axial direction of the rotation shaft, and the swing-side chip seal is provided with lubricating oil supplied from the vertical hole to the swing-side tip seal. The position of the vertical hole so that the pressure of the compression chamber through which the vertical hole communicates becomes lower than the pressure of the lubricating oil supplied from the vertical hole to the rocking side chip seal by floating from the swing side groove portion. The scroll compressor according to claim 2, wherein is set.
The scroll compressor according to claim 2 or 3, wherein the vertical hole is provided in the swinging spiral protrusion portion radially outside the central portion in the thickness direction.
The scroll compressor according to claim 2 or 3, wherein the vertical hole is provided at the swinging spiral protrusion portion so as to be inclined toward the outside in the radial direction from the upstream side to the downstream side of the flow of the lubricating oil.
The aspect according to any one of claims 2 to 5, wherein two vertical holes are provided at symmetrical positions about the eccentric shaft portion, and two horizontal holes are provided corresponding to each vertical hole. Scroll compressor.
The claim that the rocking base plate is formed with a lubrication hole for supplying the lubricating oil flowing out from the oil passage of the rotating shaft to the thrust surface of the rocking scroll independently of the through hole. The scroll compressor according to any one of claims 1 to 6.
A refrigeration cycle device provided with the scroll compressor according to any one of claims 1 to 7.