WO2022059195A1

WO2022059195A1 - Scroll compressor

Info

Publication number: WO2022059195A1
Application number: PCT/JP2020/035569
Authority: WO
Inventors: 修也福田; 浩二増本; 友寿松井; 浩平達脇
Original assignee: 三菱電機株式会社
Priority date: 2020-09-18
Filing date: 2020-09-18
Publication date: 2022-03-24
Also published as: JP7313570B2; JPWO2022059195A1

Abstract

This scroll compressor is provided with a shell, a frame, a fixed scroll, an orbiting scroll, a rotational shaft, and a thrust plate provided between the frame and the orbiting scroll. A movement-regulating recess is formed in a surface of the frame in contact with the thrust plate. The thrust plate comprises a movement-regulating projection projecting toward the frame side and inserted into the movement-regulating recess to regulate movement of the thrust plate.

Description

Scroll compressor

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

The conventional scroll compressor is equipped with a shell, a frame fixed to the inner wall surface of the shell, and a compression mechanism for compressing the refrigerant. The compression mechanism is a fixed scroll having a fixed base plate provided with a first spiral protrusion, and a swing provided with a second spiral protrusion that is swingably supported by the frame and meshes with the first spiral protrusion. It is equipped with a swing scroll having a base plate. The compression mechanism portion meshes the first spiral protrusion portion with the second spiral protrusion portion to form a compression chamber for compressing the refrigerant between the first spiral protrusion portion and the second spiral protrusion portion. The frame is provided with a thrust plate for receiving the thrust load of the swing scroll generated during the swing motion. The thrust plate is fixed to the frame by a fixing member at a position outside the swing scroll in order to suppress the rotation of the thrust plate.

Japanese Unexamined Patent Publication No. 2018-91219

By the way, as a method of increasing the compression efficiency of the scroll compressor, a method of expanding the capacity of the compression chamber can be considered. To increase the capacity of the compression chamber, the outer diameter of the swing scroll may be increased. However, in Patent Document 1, a fixing member for suppressing the rotation of the thrust plate is installed on the outside of the swing scroll, and the fixing member is installed between the outer periphery of the swing scroll and the inner peripheral surface of the shell. It is necessary to secure space. Therefore, there is a problem that the size of the swing scroll is limited and the capacity of the compression chamber cannot be expanded.

The present disclosure has been made to solve the above-mentioned problems, and provides a scroll compressor capable of expanding the capacity of the compression chamber without the need for a member for suppressing the rotation of the thrust plate. The purpose is.

The scroll compressor according to the present disclosure includes a shell, a frame fixed to the inner wall surface of the shell, a fixed scroll having a fixed base plate fixed to the inner wall surface of the shell and provided with a first spiral protrusion, and a frame. The oscillating scroll has a oscillating base plate that is oscillatingly supported and provided with a second vortex protrusion that meshes with the first vortex protrusion, and forms a compression chamber that compresses the refrigerant between the fixed scroll and the oscillating scroll. A rotating shaft connected to the oscillating scroll to cause the oscillating scroll to oscillate, and a thrust plate provided between the frame and the oscillating scroll. A movement-restricting recess is formed, and the thrust plate is provided with a movement-restricting convex portion that is formed so as to project toward the frame side and is inserted into the movement-restricting recess to regulate the movement of the thrust plate.

According to the present disclosure, the movement of the thrust plate can be restricted by inserting the movement-restricting convex portion provided on the thrust plate into the movement-restricting concave portion provided on the frame, so that a member for suppressing the rotation of the thrust plate is unnecessary. As a result, the capacity of the compression chamber can be expanded.

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. FIG. 3 is a schematic perspective view showing a main part of the scroll compressor according to the first embodiment in an exploded manner. It is a schematic vertical sectional view of the compression mechanism part of the scroll compressor which concerns on Embodiment 1. FIG. FIG. 4 is an enlarged view of a portion surrounded by a circle in FIG. It is a schematic diagram of the thrust plate of the scroll compressor which concerns on Embodiment 1. FIG. It is a figure which shows the modification of the movement regulation convex part and the movement regulation concave part of the scroll compressor which concerns on Embodiment 1. FIG. It is a schematic diagram which looked at the rocking scroll of the scroll compressor which concerns on Embodiment 2 from the lower side. FIG. 3 is a schematic cross-sectional view (1/3) showing the positional relationship between the oscillating scroll of the scroll compressor according to the second embodiment and the thrust plate. It is a schematic cross-sectional view (2/3) which showed the positional relationship between the rocking scroll of the scroll compressor which concerns on Embodiment 2 and a thrust plate. FIG. 3 is a schematic cross-sectional view (3/3) showing the positional relationship between the oscillating scroll of the scroll compressor according to the second embodiment and the thrust plate. FIG. 3 is a schematic vertical cross-sectional view showing the positional relationship between the oscillating scroll and the thrust plate in the state of FIG. 10 in the scroll compressor according to the second embodiment. It is a schematic diagram of the thrust plate of the scroll compressor which concerns on Embodiment 3. FIG. It is a schematic diagram of the thrust plate of the scroll compressor which concerns on Embodiment 4. FIG. FIG. 3 is a schematic perspective view of a thrust plate and a frame in the scroll compressor according to the fourth embodiment. FIG. 5 is a schematic cross-sectional view (1/5) showing the positional relationship between the oscillating scroll of the scroll compressor according to the fourth embodiment and the thrust plate. FIG. 5 is a schematic cross-sectional view (2/5) showing the positional relationship between the oscillating scroll of the scroll compressor according to the fourth embodiment and the thrust plate. FIG. 3 is a schematic cross-sectional view (3/5) showing the positional relationship between the oscillating scroll of the scroll compressor according to the fourth embodiment and the thrust plate. FIG. 5 is a schematic cross-sectional view (4/5) showing the positional relationship between the oscillating scroll of the scroll compressor according to the fourth embodiment and the thrust plate. FIG. 5 is a schematic cross-sectional view (5/5) showing the positional relationship between the oscillating scroll of the scroll compressor according to the fourth embodiment and the thrust plate.

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, and the like of the configurations shown in each figure can be appropriately changed.

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 perspective view showing a main part of the scroll compressor according to the first embodiment in an exploded manner. 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 frame 2, a compression mechanism unit 3 having a fixed scroll 4 and a swing scroll 5, an electric motor 6, and a compression mechanism. A rotating shaft 7 for connecting the portion 3 and the electric motor 6 is provided.

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 frame 2, a compression mechanism unit 3, an electric motor 6, and a rotating shaft 7 are housed. 1 and 2 show a so-called vertical scroll compressor used in a state where the rotation axis 7 is in the direction of gravity, but a horizontal scroll compressor may be used.

The shell 1 has 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 includes a large-diameter first inner wall surface 10a formed at the upper end portion, a second inner wall surface 10b formed below the first inner wall surface 10a, and a second inner wall surface 10b. It has a third inner wall surface 10c formed below the second inner wall surface 10b. The first inner wall surface 10a, the second inner wall surface 10b, and the third inner wall surface 10c are configured so that the inner diameters become smaller in this order. The first step portion 11a 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 fixed scroll 4. The second step portion 11b formed by the lower end of the second inner wall surface 10b and the upper end of the third inner wall surface 10c functions as a positioning portion of the 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 frame 2 is a cylindrical metal frame that gradually tapers downward, and supports the swing scroll 5 swingably. The outer peripheral surface of the frame 2 is fixed to the inner wall surface of the main shell 1a by, for example, shrink fitting. As shown in FIG. 3, an annular flat surface 20 is formed on the upper surface of the frame 2. The flat surface 20 is provided with a ring-shaped thrust plate 25 made of a steel plate-based material such as valve steel. The thrust plate 25 functions as a thrust sliding surface of the frame 2 and supports the thrust load of the compression mechanism portion 3. The thrust plate 25 is formed so as to have an outer diameter slightly smaller than the inner diameter of the first inner wall surface 10a of the main shell 1a.

Further, as shown in FIG. 3, the inside of the cylinder of the frame 2 is composed of a housing portion 21 and a main bearing portion 22 for supporting the rotating shaft 7. The accommodating portion 21 is provided on the upper side of the frame 2. The main bearing portion 22 is provided on the lower side of the frame 2.

As shown in FIG. 3, the accommodating portion 21 is formed so that the inner diameter gradually decreases downward. 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 first Oldham grooves 21c formed so as to face each other with a shaft hole interposed therebetween are provided in a part of the Oldham accommodating portion 21a and the flat surface 20. The first old dam groove 21c is a key groove into which the first key portion 54b of the old dam ring 54 described later is fitted.

Further, as shown in FIG. 2, the oil return pipe 24 is inserted into and fixed to the oil return hole 23 formed through the inside and outside of the frame 2 in the frame 2. The oil return hole 23 communicates with the bush accommodating portion 21b. 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.

Further, as shown in FIG. 3, the frame 2 is provided with a suction port 26 which is a path for the refrigerant, and the thrust plate 25 is provided with a notch 251 having a size that does not block the suction port 26. There is. The refrigerant sucked from the suction pipe 13 passes through the suction port 26 and is taken into the compression chamber described later.

The compression mechanism unit 3 has a function of compressing the refrigerant sucked from the suction pipe 13 by being driven by the electric motor 6. The compression mechanism unit 3 includes a fixed scroll 4 and a swing scroll 5. As shown in FIGS. 2 and 3, the fixed scroll 4 has a disk-shaped fixed base plate 4a and a first spiral protrusion 4b provided on the lower surface of the fixed base plate 4a. The swing scroll 5 has a disk-shaped swing base plate 5a and a second spiral protrusion 5b provided on the upper surface of the swing base plate 5a and meshing with the first spiral protrusion 4b. The swing scroll 5 is installed eccentrically with respect to the fixed scroll 4. The first spiral protrusion 4b of the fixed scroll 4 and the second spiral protrusion 5b of the swing scroll 5 are meshed with each other to form a plurality of compression chambers 30 for compressing the refrigerant.

The fixed scroll 4 is made of a metal such as cast iron. The fixed scroll 4 is fixed to the first inner wall surface 10a by shrink fitting or the like in a state where the outer peripheral surface of the fixed base plate 4a is supported by the first step portion 11a of the main shell 1a.

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. A chamber 15 having a discharge hole 15a communicating with the discharge port 40 is provided on the upper surface of the fixed scroll 4. 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, a groove is formed at the tip of the first spiral protrusion 4b, and a tip seal 41 made of, for example, hard plastic is provided in the groove.

The swing scroll 5 is made of a metal such as aluminum. As shown in FIGS. 2 and 3, the swing scroll 5 revolves without rotating with respect to the fixed scroll 4 by the old dam ring 54 for blocking the rotation. The surface of the rocking base plate 5a on the side where the second spiral protrusion 5b is not formed (lower surface in the case of the illustrated example) acts as a rocking scroll thrust bearing surface. Further, a hollow cylindrical boss portion 51 is provided at the center of the swing scroll thrust bearing surface. A swing bearing is provided on the inner peripheral surface of the boss portion 51. The oscillating bearing rotatably supports the slider 80 of the bush 8 described later. 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. As the eccentric shaft portion 71 of the rotating shaft 7 inserted into the boss portion 51 rotates, the swing scroll 5 revolves on the thrust sliding surface of the frame 2.

Further, a groove is formed at the tip of the second spiral protrusion 5b, and a tip seal 52 made of, for example, hard plastic is provided in this groove. Further, the swing scroll thrust bearing surface is provided with a pair of second Oldham grooves 53 formed so as to face each other with the boss portion 51 interposed therebetween. The second Oldham groove 53 is an oval-shaped key groove into which the second key portion 54c of the Oldham ring 54, which will be described later, is fitted. The pair of second Oldham grooves 53 are arranged so that the lines connecting the pair of second Oldam grooves 53 are orthogonal to the lines connecting the pair of first Oldam grooves 21c.

The Oldham ring 54 includes a ring portion 54a, a first key portion 54b, and a second key portion 54c. The ring portion 54a is annular and is arranged in the old dam accommodating portion 21a of the frame 2. The first key portion 54b is provided on the lower surface of the ring portion 54a. The first key portion 54b is composed of a pair and is accommodated in each pair of first old dam grooves 21c of the frame 2. The second key portion 54c is provided on the upper surface of the ring portion 54a. The second key portion 54c is composed of a pair and is housed in each pair of the second oldham grooves 53 of the swing scroll 5. By aligning the second Oldham groove 53 of the swing scroll 5 with the second key portion 54c of the Oldam ring 54, the position of the second 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 frame 2, and determines the phase of the second spiral protrusion 5b with respect to the frame 2.

The compression chamber 30 is formed by engaging the first spiral protrusion 4b of the fixed scroll 4 and the second spiral protrusion 5b of the swing scroll 5 with each other. The compression chamber 30 is sealed by a tip seal 41 and a swing base plate 5a provided at the tip of the first spiral protrusion 4b, and a tip seal 52 and a fixed base plate 4a provided at the tip of the second spiral protrusion 5b. Has been done. The compression chamber 30 is composed of a plurality of compression chambers 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. R32 (difluoromethane), R41 and the like represented by CH ₂ F ₂ are exemplified as the mixed refrigerant. 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 includes 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 configuration 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 has a ring shape in a plan view, that is, in the axial direction of the rotating shaft 7. It is formed. 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 FIG. 2, 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 the central axis thereof is arranged so as to coincide 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 rotary shaft 7 is rotatable by a main bearing portion 22 provided in the central portion of the 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. Is supported by.

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 eccentric shaft portion 71 causes the swing scroll 5 to revolve and swivel, which is a swing motion. Further, inside the main shaft portion 70 and the eccentric shaft portion 71, an oil passage hole 72 is provided so as to penetrate vertically along the axial direction.

As shown in FIGS. 2 and 3, the bush 8 includes a slider 80 and a balance weight 81. 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 in the slide surface of the slider 80. That is, the slider 80 is inserted between the swing scroll 5 and the eccentric shaft portion 71. The slider 80 is provided to make the swing radius of the swing scroll 5 variable and to make the swing scroll 5 revolve and turn.

The balance weight 81 is provided to cancel the centrifugal force of the swing scroll 5 generated by the revolution turning motion. The balance weight 81 has an annular shape, and is provided with a substantially C-shaped weight portion 81a 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 second spiral protrusion 5b against the first spiral protrusion 4b by the balance weight 81. The balance weight 81 is fitted, for example, to the collar of the slider 80 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.

As shown in FIG. 2, the lubricating oil is stored in the oil reservoir 18. Lubricating oil is sucked up by the oil pump 91, passes through the oil passage hole 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, a naphthene-based oil, a polyol ester (POE), a polyvinyl ether (PVE) or a polyalkylene glycol (PAG) oil can be used.

Next, the relationship between the frame 2 and the thrust plate 25 will be described in detail with reference to FIGS. 1 to 3 with reference to FIGS. 4 and 5. FIG. 4 is a schematic vertical sectional view of the compression mechanism portion of the scroll compressor according to the first embodiment. FIG. 5 is an enlarged view of a portion surrounded by a circle in FIG. FIG. 6 is a schematic view of the thrust plate of the scroll compressor according to the first embodiment.

As shown in FIGS. 3 and 4, a movement restricting recess 27 is provided on the flat surface 20 of the frame 2 and the contact surface 20a of the frame 2 with the thrust plate 25. The movement restricting recess 27 has a circular shape in a plan view, and the cross-sectional shape along the axial direction is rectangular. The thrust plate 25 is provided with a movement restricting convex portion 252 formed so as to project toward the flat surface 20 side of the frame 2. The movement restricting convex portion 252 has a circular shape in a plan view, and the cross-sectional shape along the axial direction is a semicircular shape. The movement restricting convex portion 252 is inserted into the movement restricting concave portion 27 to restrict the movement of the thrust plate 25. The movement restricting convex portion 252 is formed, for example, by press working.

As shown in FIG. 3, the thrust plate 25 needs to be positioned on the frame 2 so that the notch 251 faces the suction port 26 of the frame 2. When installing the thrust plate 25 on the frame 2, the movement restricting convex portion 252 is inserted into the movement restricting recess 27. By inserting the movement restricting convex portion 252 into the movement restricting concave portion 27, the position of the thrust plate 25 with respect to the frame 2 is also determined. Therefore, the movement restricting convex portion 252 and the movement restricting concave portion 27 function not only as the movement restricting portion but also as the positioning portion.

The following gaps are provided between the movement restricting concave portion 27 and the movement restricting convex portion 252. As shown in FIG. 5, a first gap C is provided between the opening edge portion 27a of the movement restricting recess 27 and the root edge portion 252a of the movement restricting convex portion 252. Further, a second gap S is provided between the bottom surface 27b of the movement restricting recess 27 and the tip surface 252b on the protruding side of the movement restricting convex portion 252. By providing the first gap C and the second gap S, the thrust plate 25 is prevented from rising from the flat surface 20 of the frame 2 in a state where the movement restricting convex portion 252 is inserted into the movement restricting recess 27. .. If the first gap C and the second gap S are not provided, the root edge portion 252a of the movement restricting convex portion 252 is caught by the opening edge portion 27a of the movement restricting recess 27, and the thrust plate 25 has a flat surface 20. May rise from. In order to prevent this floating, a first gap C and a second gap S are provided between the movement restricting concave portion 27 and the movement restricting convex portion 252. The first gap C is preferably as small as possible in order to prevent the thrust plate 25 from rattling during operation.

As described above, the movement of the thrust plate 25 can be restricted by inserting the movement restriction convex portion 252 into the movement restriction recess 27. Therefore, it is possible to prevent the thrust plate 25 from rotating due to the swinging motion of the swinging scroll 5. Further, since the movement of the thrust plate 25 can be restricted by inserting the movement regulation convex portion 252 into the movement regulation recess 27, the conventional fixing member for suppressing the rotation of the thrust plate 25 becomes unnecessary. Therefore, the scroll compressor 100 can expand the outer diameter of the swing scroll 5 to the position of the suction port 26 provided in the frame 2. Specifically, the outer diameter of the swing scroll can be expanded to the very limit of the suction port 26 provided on the flat surface 20 of the frame 2. As a result, the capacity of the compression chamber can be expanded. In addition, the cost can be reduced because the fixing member is not required.

Further, as described above, the outer diameter of the thrust plate 25 is formed to be slightly smaller than the inner diameter of the first inner wall surface 10a of the main shell 1a. Therefore, during the swinging motion of the swinging scroll 5, the outer peripheral surface of the thrust plate 25 comes into contact with the first inner wall surface 10a of the main shell 1a, and the radial movement of the thrust plate 25 can be restricted. Therefore, in the first embodiment, the movement of the thrust plate 25 in the radial direction can be restricted in addition to the rotation suppression by the movement regulation convex portion 252, and the movement of the thrust plate 25 in the main shell 1a can be substantially suppressed.

In the above, the shape of the movement restricting concave portion 27 and the movement restricting convex portion 252 in a plan view is circular, but the shape of the movement restricting concave portion 27 and the movement restricting convex portion 252 does not have to be circular. The shape of the movement restricting concave portion 27 and the movement restricting convex portion 252 may be any shape as long as the movement restricting convex portion 252 can be inserted into the movement restricting concave portion 27, and the shapes can be appropriately changed in consideration of ease of processing. As a specific example of another shape, for example, the following FIG. 7 may be used.

FIG. 7 is a diagram showing a modified example of the movement restricting convex portion and the movement restricting concave portion of the scroll compressor according to the first embodiment.
In FIG. 7, the bottom surface 27b of the movement restricting recess 27 has a shape along the tip surface 252b on the protruding side of the movement restricting convex portion 252. Even with such a shape, the movement of the thrust plate 25 can be restricted.

As described above, the scroll compressor of the first embodiment is between the shell 1, the frame 2, the fixed scroll 4, the swing scroll 5, the rotation axis 7, and the frame 2 and the swing scroll 5. The thrust plate 25 provided in the above is provided. In the frame 2, a movement restricting recess 27 is formed on the contact surface 20a with the thrust plate 25. The thrust plate 25 is provided with a movement restricting convex portion 252 that is formed so as to project toward the frame 2 side and is inserted into the movement restricting recess 27 to restrict the movement of the thrust plate 25.

In this way, the movement restriction protrusion 252 provided on the thrust plate 25 is inserted into the movement restriction recess 27 provided on the frame 2 to restrict the movement of the thrust plate 25, so that the rotation of the thrust plate 25 can be suppressed. It is possible to eliminate the need for a fixing member. Since the fixing member for suppressing the rotation of the thrust plate 25 can be eliminated, the capacity of the compression chamber 30 can be expanded as a result.

Further, a first gap C is formed between the opening edge portion 27a of the movement restricting recess 27 and the root edge portion 252a of the movement restricting convex portion 252, and the bottom surface 27b of the movement restricting recess 27 and the movement restricting convex portion 252. A second gap S is formed between the surface and the tip surface 252b on the protruding side of the above.

This makes it possible to prevent the thrust plate 25 from floating from the flat surface 20 in a state where the movement restricting convex portion 252 is inserted into the movement restricting recess 27.

Embodiment 2.
FIG. 8 is a schematic view of the swing scroll of the scroll compressor according to the second embodiment as viewed from below. 9 to 11 are schematic cross-sectional views showing the positional relationship between the oscillating scroll of the scroll compressor according to the second embodiment and the thrust plate.

The hatched portion in FIG. 8 shows the thrust surface of the rocking scroll 5, and the thrust surface is provided with an intermittent oil supply passage 55 composed of recesses. The position of the intermittent oil supply passage 55 is d <when the distance from the outer peripheral portion 56 of the rocking base plate 5a to the outer peripheral portion of the intermittent oil supply passage 55 is d and the diameter of the movement restricting convex portion 252 of the thrust plate 25 is D. It is set to the position that becomes D. By setting the intermittent refueling passage 55 at a position where d <D, the movement restricting convex portion 252 is used not only for suppressing the rotation of the thrust plate 25 but also as a part of the intermittent refueling mechanism as described below. be able to.

Next, the operation of the scroll compressor according to the second embodiment will be described with reference to FIGS. 9 to 11. The swing scroll 5 swings on the thrust plate 25 due to the rotation of the rotation shaft 7. Therefore, the positional relationship between the intermittent oil supply passage 55 provided in the swing scroll 5 and the movement restricting convex portion 252 provided in the thrust plate 25 changes depending on the position of the swing scroll 5.

When the swing scroll 5 swings due to the rotation of the rotation shaft 7, the intermittent oil supply passage 55 overlaps the movement restricting convex portion 252, and the state shown in FIG. 9 is obtained. When the rotary shaft 7 further rotates from the state of FIG. 9, both the outer peripheral portion 56 of the rocking base plate 5a and the intermittent oil supply passage 55 overlap the movement restricting convex portion 252, and the state of FIG. 10 is obtained.

When the rotary shaft 7 further rotates from the state of FIG. 10, the intermittent oil supply passage 55 is separated from the movement restricting convex portion 252, and only the outer peripheral portion 56 of the rocking base plate 5a overlaps with the movement restricting convex portion 252. Become. When the rotation shaft 7 further rotates from the state shown in FIG. 11, the outer peripheral portion 56 of the rocking base plate 5a separates from the movement restricting convex portion 252. After that, when the rotation shaft 7 further rotates, the intermittent oil supply passage 55 gradually approaches the movement restricting convex portion 252 and returns to the state shown in FIG.

FIG. 12 is a schematic vertical cross-sectional view showing the positional relationship between the oscillating scroll and the thrust plate in the state of FIG. 10 in the scroll compressor according to the second embodiment.
In the case of the state of FIG. 10, that is, in the case of the positional relationship in which the outer peripheral portion 56 of the rocking base plate 5a and the intermittent oil supply passage 55 both overlap the movement restricting convex portion 252, the oil passage passage indicated by the arrow in FIG. 57 is formed. The movement restricting convex portion 252 is recessed on the side opposite to the protruding side, and the recessed portion forms an internal space 253. Therefore, the intermittent oil supply passage 55 and the outer space 56a of the swing scroll 5 communicate with each other through the internal space 253, and the oil passage 57 is formed. The outer space 56a of the swing scroll 5 is specifically the outer space 56a of the outer peripheral portion 56 of the swing base plate 5a.

By forming such an oil passage 57, the lubricating oil accumulated in the intermittent oil passage 55 is ejected to the side surface of the rocking scroll 5 through the oil passage 57. The lubricating oil ejected on the side surface of the rocking scroll 5 is sucked into the compression chamber 30 together with the refrigerant. That is, when the positional relationship shown in FIG. 10 is established, the oil passage 57 is formed, and the lubricating oil in the intermittent oil supply passage 55 is positively supplied into the compression chamber 30 through the oil passage 57. Since the positional relationship of FIG. 10 is established for a certain period of time while the rotating shaft 7 makes one rotation, refueling is intermittently performed using the intermittent oil supply passage 55 while the rotating shaft 7 is rotating. It will be.

The amount of refueling into the compression chamber 30 can be adjusted by the size of the intermittent refueling passage 55 and the movement regulation convex portion 252. For example, when the size of the intermittent oil supply passage 55 is expanded, the time during which the positional relationship shown in FIG. 10 is established while the rotation shaft 7 makes one rotation, that is, the time during which the oil passage passage 57 is formed (hereinafter referred to as communication time). ) Becomes longer. As the communication time becomes longer, the amount of lubricating oil supplied into the compression chamber 30 through the oil passage 57 increases. On the other hand, if the size of the intermittent oil supply passage 55 is reduced, the communication time is shortened and the amount of lubricating oil supplied into the compression chamber 30 is reduced. The size of the movement restricting convex portion 252 and the amount of lubricating oil supplied into the compression chamber 30 have the same relationship. Since the size of the intermittent oil supply passage 55 and the movement regulation convex portion 252 and the amount of lubricating oil supplied into the compression chamber 30 have the above-mentioned relationship, the intermittent oil supply passage 55 and the movement according to the target oil supply amount. The size of the regulation convex portion 252 may be determined.

By the way, the position of the intermittent refueling passage 55 is set to the position where d <D, but the reason is as follows. That is, when d ≧ D, the range in which the intermittent refueling passage 55 overlaps with the movement restricting convex portion 252 is too narrow or does not overlap, and the intermittent refueling passage 55 does not function as a refueling hole.

Although FIGS. 8 to 11 show an example in which the diameter of the intermittent oil supply passage 55 is larger than the width of the second Oldham groove 53, the diameter of the intermittent oil supply passage 55 may be the same as the width of the second Oldham groove 53. .. When the diameter of the intermittent oil supply passage 55 is the same as the width of the second Oldham groove 53, the second Oldham groove 53 may be extended radially outward, and the extended portion thereof may be the intermittent oil supply passage 55.

Further, in order to smooth the flow of oil in the oil passage 57, as shown by the dotted line in FIG. 12, the radial outer end of the inner surface forming the intermittent oil supply passage 55 may be formed in a slope shape. ..

As described above, the scroll compressor of the second embodiment has an intermittent oil supply passage 55 composed of a movement restricting recess 27 on the thrust surface of the swing scroll 5. The intermittent refueling passage 55 is a refueling passage that intermittently communicates with the internal space 253 of the movement restricting convex portion 252 by the rotation of the rotating shaft 7. The intermittent oil supply passage 55 communicates with the outer space 56a of the swing scroll 5 via the internal space 253 of the movement restricting convex portion 252 for a certain period of one rotation of the rotation shaft 7, and forms the oil passage 57.

In this way, the oil passage 57 is formed for a certain period of one rotation of the rotary shaft 7, and the lubricating oil in the intermittent oil supply passage 55 can be positively supplied into the compression chamber 30. Therefore, the compression chamber 30 can be used. Can be lubricated and sealed.

Embodiment 3.
FIG. 13 is a schematic view of the thrust plate of the scroll compressor according to the third embodiment. Hereinafter, the configuration in which the third embodiment is different from the first embodiment will be mainly described, and the configurations not described in the third embodiment are the same as those in the first embodiment.

In the first embodiment, the movement restricting recess 27 provided in the frame 2 and the movement restricting convex portion 252 provided in the thrust plate 25 are one set. On the other hand, in the third embodiment, two sets of the movement restricting concave portion 27 and the movement restricting convex portion 252 are provided. One of the two sets and the other set are provided at symmetrical positions with respect to the center O of the thrust plate 25.

In the third embodiment, by forming two sets of the movement restricting concave portion 27 and the movement restricting convex portion 252, in addition to suppressing the movement of the thrust plate 25 in the rotation direction, the movement in the radial direction is also suppressed. Is possible. Therefore, it is not necessary to regulate the radial movement of the thrust plate 25 by the first inner wall surface 10a of the main shell 1a as described above. Therefore, it is possible to set the outer diameter of the thrust plate 25 to a size that does not come into contact with the first inner wall surface 10a of the main shell 1a. As a result, it is possible to prevent the first inner wall surface 10a from being damaged due to the thrust plate 25 coming into contact with the first inner wall surface 10a of the main shell 1a during operation.

As described above, since the scroll compressor of the third embodiment includes two sets of the movement restricting concave portion 27 and the movement restricting convex portion 252, in addition to suppressing the movement of the thrust plate 25 in the rotation direction. , The radial movement of the thrust plate 25 can also be suppressed.

Although the configuration in which the above-described first embodiment and the present embodiment 3 are combined has been described here, a configuration in which the above-described second embodiment and the third embodiment may be combined may be used. That is, the intermittent oil supply passage 55 of the second embodiment may be provided in the scroll compressor of the third embodiment. In this case, as in the second embodiment, the movement regulation convex portion 252 can be used as a part of the intermittent refueling mechanism. Then, by providing the intermittent oil supply passage 55 corresponding to each set, the lubricating oil can be positively supplied into the compression chamber 30 as compared with the second embodiment.

Here, an example in which one set and the other set of the two sets of the movement control concave portion 27 and the movement control convex portion 252 are provided at symmetrical positions with respect to the center O of the thrust plate 25. Although shown, it is not limited to this position. In short, one set and the other set may be provided at a position where the effect of suppressing the radial movement of the thrust plate 25 can be obtained. Further, although the example in which the set of the movement restricting concave portion 27 and the movement restricting convex portion 252 is two sets is shown here, three or more sets may be used. However, since the effect of suppressing the radial movement of the thrust plate 25 can be sufficiently obtained with two sets, two sets are desirable.

Embodiment 4.
FIG. 14 is a schematic view of the thrust plate of the scroll compressor according to the fourth embodiment. FIG. 15 is a schematic perspective view of a thrust plate and a frame in the scroll compressor according to the fourth embodiment. 16 to 18 are schematic cross-sectional views showing the positional relationship between the oscillating scroll of the scroll compressor according to the fourth embodiment and the thrust plate. Hereinafter, the configuration in which the present embodiment 4 is different from the above-described embodiment 1 will be mainly described, and the configurations not described in the present embodiment 4 are the same as those in the embodiment 1-3.

As shown in FIGS. 14 and 15, in the fourth embodiment, two sets of the movement restricting convex portion 252 and the movement restricting concave portion 27 are provided as in the third embodiment. Further, two intermittent oil supply passages 55 are provided in the same number as the set of the movement regulation convex portion 252 and the movement regulation concave portion 27.

Here, as shown in FIG. 14, the center O of the thrust plate 25 is the origin, the axis passing through the origin and the notch 251 is the Y axis, and the axis passing through the origin and orthogonal to the Y axis is the X axis. At this time, the movement-restricted convex portion 252 whose X coordinate is in the negative position is the first movement-restricted convex portion 252-1 and the movement-restricted convex portion 252 whose X-coordinate is in the positive position is the second movement-restricted convex portion 252-2. And. The first movement restricting convex portion 252-1 and the second movement restricting convex portion 252-2 are located on opposite sides of each other with respect to a straight line passing through the center O (here, the Y axis).

Of the two movement-restricted recesses 27 provided, the movement-restricted recess 27 into which the first movement-restricted convex portion 252-1 is inserted is designated as the first movement-restricted recess 27-1, and the second movement-restricted convex portion 252-2 is designated as the first movement-restricted recess 27-1. The movement restricting recess 27 to be inserted is referred to as a second movement restricting recess 27-2. Of the two intermittent refueling passages 55, the intermittent refueling passage 55 that forms a continuous passage together with the first movement regulation convex portion 252-1 is referred to as the first intermittent refueling passage 55-1 (see FIG. 16). Further, of the two intermittent refueling passages 55, the intermittent refueling passage 55 forming a continuous passage together with the second movement restricting convex portion 252-2 is designated as the second intermittent refueling passage 55-2 (not shown, for convenience, the reference numeral. Is attached).

The outer shape of each of the first movement regulation convex portion 252-1 and the second movement regulation convex portion 252-2 is a shape extending in the Y-axis direction as shown in FIG. 14 in a plan view. Specifically, the outer shape of the first movement regulation convex portion 252-1 is specified by a pair of straight lines facing each other at intervals and a pair of arcs in which both ends of the pair of straight lines are connected in an arc shape. It is a shape to be made. The second movement regulation convex portion 252-2 has the same shape.

The center position of each of the first movement regulation convex portion 252-1 and the second movement regulation convex portion 252-2 in the Y-axis direction is set to a position shifted in the positive direction of the Y axis from the center O. Further, the arc portions 252c of the first movement restricting convex portion 252-1 and the second movement restricting convex portion 252-2 are set to a size and position that do not interfere with the outer peripheral portion 56 of the rocking base plate 5a during operation. ing. Here, "does not interfere" means that the outer peripheral portion 56 of the rocking base plate 5a does not overlap the arc portion 252c in the axial direction of the rotating shaft 7.

The shape of the first movement restricting recess 27-1 and the second movement restricting recess 27-2 in a plan view is the same as that of the first movement restricting convex portion 252-1 and the second movement restricting convex portion 252-2. The cross-sectional shape of the first movement restricting recess 27-1 and the second movement restricting recess 27-2 may be rectangular or may be a shape along the tip surface on the protruding side of the movement restricting convex portion 252. The shape of the first intermittent refueling passage 55-1 and the second intermittent refueling passage 55-2 in a plan view is circular as in the second embodiment. The dotted line, dot portion, and θ in FIG. 14 will be described later.

Next, the operation of the scroll compressor according to the fourth embodiment will be described with reference to FIGS. 16 to 18. As in the first embodiment, the swing scroll 5 swings on the thrust plate 25 due to the rotation of the rotation shaft 7. Therefore, the positional relationship between the "first intermittent refueling passage 55-1 and the first movement regulation convex portion 252-1" and the "second intermittent refueling passage 55-2 and the second movement regulation convex portion 252-2" is , Varies depending on the position of the swing scroll 5.

When the swing scroll 5 swings due to the rotation of the rotation shaft 7, the outer peripheral portion 56 of the swing base plate 5a overlaps with the first movement restricting convex portion 252-1, and the state shown in FIG. 16 is obtained. When the rotary shaft 7 further rotates from the state of FIG. 16, both the outer peripheral portion 56 of the rocking base plate 5a and the first intermittent oil supply passage 55-1 overlap with the first movement restricting convex portion 252-1, and FIG. It becomes a state. In the state of FIG. 17, the first intermittent oil supply passage 55-1, the internal space 253 of the first movement restricting convex portion 252-1, and the outer space 56a of the swing scroll 5 communicate with each other to form an oil passage. Will be done. As described above, in the state of FIG. 17, the oil passage is formed, so that the lubricating oil accumulated in the first intermittent oil supply passage 55-1 is ejected through the oil passage to the side surface of the swing scroll 5 and compressed. It is supplied into the chamber 30 (see FIG. 2).

When the rotation shaft 7 further rotates from the state of FIG. 17, the first intermittent oil supply passage 55-1 separates from the first movement restricting convex portion 252-1, and only the outer peripheral portion 56 of the rocking base plate 5a has the first movement restricting convex portion. It overlaps with the part 252-1 and becomes the state of FIG. When the rotation shaft 7 further rotates from the state of FIG. 18, the outer peripheral portion 56 of the rocking base plate 5a separates from the first movement restricting convex portion 252-1. After that, when the rotation shaft 7 further rotates, the outer peripheral portion 56 of the rocking base plate 5a gradually approaches the first movement restricting convex portion 252-1 again, and returns to the state of FIG. Although not shown, the positional relationship between the second intermittent refueling passage 55-2 and the second movement restricting convex portion 252-2 is also the first intermittent refueling passage 55-1 and the first due to the oscillating motion of the oscillating scroll 5. The movement restriction changes in the same manner as the change in the positional relationship with the convex portion 252-1.

Due to the above operation, the first movement regulation convex portion 252-1 and the second movement regulation convex portion 252-2 are used as a part of the intermittent refueling mechanism as in the second and third embodiments.

It is desirable to adopt the following positional relationship so that the lubricating oil in each intermittent oil supply passage flows out from each positioning portion and then is easily supplied into the compression chamber 30. That is, it is desirable to set the position of the winding end of each of the spiral protrusions of the fixed scroll 4 and the swing scroll 5 within the dot region of FIG. The dot region is a region formed by two straight lines (dotted lines in FIG. 14) connecting the arcs on opposite sides of the first movement restricting convex portion 252-1 and the second movement restricting convex portion 252-2. .. By setting the position of the winding end of each of the spiral protrusions 4 of the fixed scroll 4 and the swing scroll 5 within the dot region, the position of the winding end of each spiral protrusion and each positioning portion become close to each other. Therefore, the lubricating oil flowing out from each positioning portion is easily taken into the compression chamber 30 from the winding end side of each spiral protrusion portion, and the amount of lubricating oil supplied to the compression chamber 30 can be increased.

Next, the communication time between the intermittent refueling passage 55 and the compression chamber 30 will be described. For example, when each of the movement restricting convex portion 252 and the intermittent refueling passage 55 is one as in the second embodiment, the communication time is determined by the size and positional relationship of the movement restricting convex portion 252 and the intermittent refueling passage 55, respectively. .. The positional relationship between the movement regulation convex portion 252 and the intermittent oil supply passage 55 changes due to the rattling of the thrust plate 25 during operation. Therefore, the communication time during one rotation of the rotating shaft 7 is not constant but changes. As the communication time changes, the amount of lubricating oil intermittently supplied to the compression chamber 30 during operation of the compressor also changes, so that the amount of lubricating oil supplied to the compression chamber 30 is insufficient or excessive. There is a concern that it will become.

In the scroll compressor according to the fourth embodiment, the variation in the communication time due to the rattling of the thrust plate 25 is suppressed. Hereinafter, the reason why the variation in the communication time due to the rattling of the thrust plate 25 can be suppressed will be described by citing three deviation patterns of the thrust plate 25 due to the rattling.

(When the thrust plate 25 is displaced in the X-axis direction)
When the thrust plate 25 is displaced in the positive direction of the X axis, the distance between the first movement restricting convex portion 252-1 and the first intermittent oil passage 55-1 is increased, so that the first movement restricting convex portion 252-1 and the first 1 The communication time with the intermittent refueling channel 55-1 is shortened. Here, as described above, the first movement regulation convex portion 252-1 and the second movement regulation convex portion 252-2 are located on opposite sides of each other with respect to the Y axis. Therefore, when the thrust plate 25 is displaced in the positive direction of the X axis, the distance between the second movement restricting convex portion 252-2 and the second intermittent oil supply passage 55-2 becomes closer, and the second movement restricting convex portion 252-2 becomes the same. The communication time with the second intermittent refueling channel 55-2 becomes longer. That is, when the thrust plate 25 is displaced in the X-axis direction, the communication time between the first movement restricting convex portion 252-1 and the first intermittent oil supply passage 55-1 is shortened, while the second movement restricting convex portion 252-2. And the communication time with the second intermittent refueling channel 55-2 becomes longer. Therefore, the total of each communication time is almost the same as the total of each communication time before the deviation.

Further, even when the thrust plate 25 is displaced in the negative direction of the X-axis, the distance between the first movement restricting convex portion 252-1 and the first intermittent oil supply passage 55-1 becomes shorter, the communication time becomes longer, and the second movement. The distance between the regulation convex portion 252-2 and the second intermittent oil supply passage 55-2 is increased, and the communication time is shortened. Therefore, the total of each communication time is almost the same as the total of each communication time before the deviation.

(When the thrust plate 25 is displaced in the Y-axis direction)
As described above, the arc portions 252c of the first movement restricting convex portion 252-1 and the second movement restricting convex portion 252-2 are set to a size and position that do not interfere with the outer peripheral portion 56 of the rocking base plate 5a. ing. Therefore, even if the thrust plate 25 is displaced in the positive direction of the Y axis, the area shown by the shaded area in FIG. 17 (hereinafter referred to as the opening area) does not change, so that the communication time does not change either. Further, even when the thrust plate 25 is displaced in the negative direction of the Y axis, the opening area does not change, so that the communication time does not change.

(When the thrust plate 25 is displaced in the θ direction)
θ is the direction in which the thrust plate 25 rotates on its axis, and the counterclockwise direction is positive. 19 and 20 are schematic cross-sectional views showing the positional relationship between the oscillating scroll of the scroll compressor according to the fourth embodiment and the thrust plate. FIG. 19 shows the positional relationship between the first movement restricting convex portion 252-1 and the first intermittent oil supply passage 55-1 when the thrust plate 25 rotates and shifts in the positive direction in the θ direction. FIG. 20 shows the positional relationship between the first movement restricting convex portion 252-1 and the first intermittent oil supply passage 55-1 when the thrust plate 25 rotates and shifts in the negative direction in the θ direction.

When the thrust plate 25 rotates and shifts in the positive direction in the θ direction, the positional relationship between the first movement restricting convex portion 252-1 and the first intermittent oil supply passage 55-1 changes as shown in FIG. The opening area (hatched portion in FIG. 19) formed by the first movement restricting convex portion 252-1 and the first intermittent oil supply passage 55-1 becomes smaller. Therefore, the communication time between the first movement regulation convex portion 252-1 and the first intermittent oil supply passage 55-1 is shortened. On the other hand, the positional relationship between the second movement regulation convex portion 252-2 and the second intermittent oil supply passage 55-2 also changes, and is formed by the second movement regulation convex portion 252-2 and the second intermittent oil supply passage 55-2. The opening area (not shown) becomes large. Therefore, the communication time between the second movement regulation convex portion 252-2 and the second intermittent oil supply passage 55-2 becomes long. Therefore, the communication time between the first movement regulation convex portion 252-1 and the first intermittent refueling passage 55-1 and the communication time between the second movement regulation convex portion 252-2 and the second intermittent refueling passage 55-2, The total of is almost the same as the total of each communication time before the deviation.

When the thrust plate 25 rotates and shifts in the negative direction in the θ direction, as shown in FIG. 20, the opening area formed by the first movement restricting convex portion 252-1 and the first intermittent oil supply passage 55-1 ( The shaded area in FIG. 20) becomes larger. Therefore, the communication time between the first movement regulation convex portion 252-1 and the first intermittent oil supply passage 55-1 becomes long. On the other hand, the opening area (not shown) formed by the second movement restricting convex portion 252-2 and the second intermittent oil supply passage 55-2 becomes smaller. Therefore, the communication time between the second movement regulation convex portion 252-2 and the second intermittent oil supply passage 55-2 is shortened. Therefore, the communication time between the first movement regulation convex portion 252-1 and the first intermittent refueling passage 55-1 and the communication time between the second movement regulation convex portion 252-2 and the second intermittent refueling passage 55-2, The total of is almost the same as the total of each communication time before the deviation.

From the above, even if the thrust plate 25 is displaced in any of the X-axis direction, the Y-axis direction, and the θ direction during operation, the communication time is kept substantially constant. Therefore, it is possible to prevent the amount of lubricating oil supplied to the compression chamber 30 from fluctuating during the operation of the compressor.

As described above, the center positions of the first movement restricting convex portion 252-1 and the second movement restricting convex portion 252-2 in the Y-axis direction are shifted from the center O in the positive direction of the Y axis. Is set to. This positional relationship is used to obtain a form in which, as described here, when the thrust plate 25 is displaced in the θ direction, the communication time of one becomes shorter and the communication time of the other becomes longer. be. The center position of each of the first movement regulation convex portion 252-1 and the second movement regulation convex portion 252-2 in the Y-axis direction is a position shifted in the positive direction of the Y axis from the center O, but is negative. It may be set to a position shifted in the direction. Further, the shift direction has been described here as the Y-axis, but in short, it may be any direction as long as each pair of straight lines of the first movement restricting convex portion 252-1 and the second movement restricting convex portion 252-2 extends.

As described above, in the scroll compressor of the fourth embodiment, the movement restricting concave portion 27 and the movement restricting convex portion 252 have the following external shapes when viewed in the axial direction of the rotating shaft 7. The movement restricting concave portion 27 and the movement restricting convex portion 252 have a shape specified by a pair of straight lines facing each other at intervals and a pair of arcs in which both ends of the pair of straight lines are connected in an arc shape. Then, one of the two sets and the other set are located on opposite sides of each other with respect to a straight line passing through the center O of the thrust plate 25. Further, the center positions of the first movement restricting convex portion 252-1 and the second movement restricting convex portion 252-2 in the direction in which the pair of straight lines extend are such that the pair of straight lines extend from the center O of the thrust plate 25. It is set to a position shifted with respect to the direction.

This makes it possible to suppress variations in the communication time due to rattling of the thrust plate 25.

1 shell, 1a main shell, 1b upper shell, 1c lower shell, 1d fixed base, 2 frame, 3 compression mechanism, 4 fixed scroll, 4a fixed base plate, 4b first spiral protrusion, 5 swing scroll, 5a swing Base plate, 5b, 2nd spiral protrusion, 6 electric motor, 6a stator, 6b rotor, 7 rotating shaft, 8 bush, 9 subframe, 10a 1st inner wall surface, 10b 2nd inner wall surface, 10c 3rd inner wall surface, 11a first 1st stage, 11b 2nd stage, 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, 20a contact surface, 21 accommodating part, 21a oldham accommodating part, 21b bush accommodating part, 21c 1st oldam groove, 22 main bearing part, 23 oil return hole, 24 oil return pipe, 25 thrust plate , 26 suction port, 27 movement regulation recess, 27-1 first movement regulation recess, 27-2 second movement regulation recess, 27a opening edge, 27b bottom surface, 30 compression chamber, 40 discharge port, 41 chip seal, 51 boss Part, 52 Chip seal, 53 2nd Oldam groove, 54 Oldam ring, 54a ring part, 54b 1st key part, 54c 2nd key part, 55 intermittent oil passage, 55-1 1st intermittent oil passage, 55-2 first 2 intermittent oil supply passage, 56 outer peripheral part, 56a outer space, 57 oil passage, 70 spindle part, 71 eccentric shaft part, 72 oil passage hole, 80 slider, 81 balance weight, 81a weight part, 90 auxiliary bearing part, 91 oil Pump, 100 scroll compressor, 251 notch, 252 movement regulation convex part, 252-1 first movement regulation convex part, 252-2 second movement regulation convex part, 252a root edge part, 252b tip surface, 252c arc part, 253 Internal space.

Claims

With the shell
The frame fixed to the inner wall surface of the shell and
A fixed scroll fixed to the inner wall surface of the shell and having a fixed base plate provided with a first spiral protrusion,
It has a swing base plate that is swingably supported by the frame and is provided with a second spiral protrusion that meshes with the first spiral protrusion, and forms a compression chamber that compresses the refrigerant between the fixed scroll and the fixed scroll. Swirling scroll and
A rotation axis connected to the swing scroll and swinging the swing scroll,
A thrust plate provided between the frame and the swing scroll is provided.
In the frame, a movement restricting recess is formed on the contact surface with the thrust plate.
The scroll compressor is provided with a movement restricting convex portion formed on the thrust plate so as to project toward the frame side and inserted into the movement restricting recess to regulate the movement of the thrust plate.
It is composed of recesses formed on the thrust surface of the swing scroll, and has an intermittent oil supply passage that intermittently communicates with the internal space of the movement restricting convex portion by the rotation of the rotation shaft.
Claim 1 in which an oil passage in which the intermittent oil passage communicates with the outer space of the swing scroll through the internal space of the movement restricting convex portion is formed for a certain period of one rotation of the rotation axis. The scroll compressor described.
The scroll compressor according to claim 1 or 2, further comprising two sets of the movement restricting concave portion and the movement restricting convex portion.
The scroll compressor according to claim 3, wherein the intermittent refueling passages have the same number as the set and are subordinate to claim 2.
The movement-restricting concave portion and the movement-restricting convex portion are formed by connecting a pair of straight lines whose outer shapes seen in the axial direction of the rotation axis face each other at intervals and both ends of the pair of straight lines in an arc shape. The scroll compressor according to claim 3 or 4, which has a shape specified by a pair of arcs.
One of the two sets and the other set are located on opposite sides of each other with respect to a straight line passing through the center of the thrust plate.
The center position of each of the two sets of the movement restricting convex portions in the direction in which the pair of straight lines extends is set to a position shifted from the center of the thrust plate in the direction in which the pair of straight lines extend. The scroll compressor according to claim 5.
The positions of the winding ends of the first spiral protrusion of the fixed scroll and the second spiral protrusion of the rocking scroll are the movement-restricted convex portions of one of the two sets and the movement-restricted portion of the other. The scroll compressor according to claim 6, wherein the scroll compressor is set in a region formed by two straight lines connecting the arcs on opposite sides to the convex portion.
A first gap is formed between the opening edge of the movement-restricted recess and the root edge of the movement-restricted convex portion, and the bottom surface of the movement-restricted recess and the tip surface of the protruding side of the movement-restricted convex portion. The scroll compressor according to any one of claims 1 to 7, wherein a second gap is formed between the two.