JP7395004B2 - scroll compressor - Google Patents

Description

The present disclosure relates to scroll compressors.

In a scroll compressor, an oscillating scroll is supported by a frame fixed inside a closed chamber casing (shell), and a fixed scroll is provided opposite to the oscillating scroll. One method of fixing the fixed scroll inside the shell is to extend the peripheral wall of the frame in the direction of the fixed scroll, and fix the tip of the peripheral wall and the fixed scroll with bolts or the like.

In Patent Document 1, in order to maximize the compression chamber space formed by a fixed scroll and an oscillating scroll in a scroll compressor, a fixed scroll is fixed to a shell using a protrusion provided on the inner wall of the shell. A method has been disclosed in which a position for attaching the scroll is determined and the fixed scroll is directly fixed to the inner wall of the shell by shrink fitting or the like. In a scroll compressor with this structure, a peripheral wall of a frame for fixing the fixed scroll is not required, and the scroll can be designed to have a larger size than a general compressor structure.

International Publication 2018/078787

If the size of the scroll is made large in the structure described in Patent Document 1, the weight of the swinging scroll increases, and it is necessary to increase the size of the balancer disposed under the frame to balance it. If the balancer is expanded in the radial direction, the balancer cover that covers it will also need to be expanded. In this case, the flow of the refrigerant sucked in from the suction pipe inside the compressor changes, and the lubricating oil that is stirred by the rotation of the balancer or drive mechanism and is in the form of a mist inside the shell is rolled up, and the lubricating oil is drawn out of the compressor. (This kind of problem will be referred to as ``oil-up'' hereafter.) Since the expansion of the balancer in the radial direction is restricted, when it expands in the axial direction, the axial length of the main shaft becomes longer to avoid interference between the balancer and the balancer cover and the drive mechanism, and the compressor There was a problem with the height.

In addition, in order to suppress the weight increase due to the expansion of the oscillating scroll, if the size of the scroll is increased but the diameter of the base plate of the oscillating scroll is not made too large, the reaction force of the compressed gas between the scrolls can be supported. There was a problem with the thrust bearing seizing up and causing the compressor to malfunction.

This invention was made to solve the above-mentioned problems, and while securing the thrust bearing area to support the oscillating scroll, it also suppresses the increase in size of the balancer and oil flow, and reduces the height of the compressor. It is something to do.

A scroll compressor according to the present disclosure includes a shell having a protrusion on an inner wall surface, a suction pipe connected to the shell and introducing refrigerant into the shell, a base plate and scroll teeth, and the base plate is attached to the protrusion. It has a fixed scroll that is supported and fixed to the inner wall surface of the shell, a base plate and scroll teeth, a convex portion is formed on the surface opposite to the surface on which the scroll teeth are formed, and forms a compression chamber together with the fixed scroll. An oscillating scroll, a main shaft on which an oscillating bearing that supports the convex part of the oscillating scroll is arranged , a sub-frame fixed to the inner wall surface of the shell, and a sub-frame provided on the sub-frame into which the lower part of the main shaft is inserted. A bearing, a thrust bearing that has a hollow part into which the main shaft is inserted and slidably supports the sliding surface of the oscillating scroll, and a main bearing that supports the main shaft are arranged and introduced into the shell from the suction pipe. A scroll compressor that is perpendicular to the central axis of the main shaft, and includes a frame equipped with a suction port that takes in refrigerant and leads it to a compression chamber, and a discharge pipe that is connected to a shell and discharges the refrigerant compressed in the compression chamber. In the cross section, at least a portion of the swing bearing and the main bearing are arranged substantially on the same plane.

While securing the thrust bearing area to support the oscillating scroll, the size of the balancer is increased, oil spillage is suppressed, and the height of the compressor is reduced.

1 is a schematic cross-sectional view of a scroll compressor according to Embodiment 1. FIG. FIG. 3 is a schematic cross-sectional view of the vicinity of the compression mechanism according to the first embodiment. FIG. 3 is a top view of the frame according to the first embodiment. FIG. 3 is a schematic cross-sectional view of the vicinity of the compression mechanism according to the first embodiment. FIG. 3 is a schematic cross-sectional view of the vicinity of a drive mechanism section according to the second embodiment. FIG. 7 is a schematic cross-sectional view of the vicinity of the compression mechanism according to the third embodiment. FIG. 7 is a schematic cross-sectional view of the vicinity of a compression mechanism according to the fourth embodiment. FIG. 7 is a schematic cross-sectional view of the vicinity of a compression mechanism according to the fourth embodiment.

Embodiments of the present disclosure will be described below with reference to the accompanying drawings. In each figure, the same or corresponding parts are given the same reference numerals. Duplicate explanations will be simplified or omitted as appropriate. Note that the present disclosure is not limited to the embodiments described below. Further, in the drawings shown below, the scale of each component may be different from the actual scale.

Embodiment 1.
The configuration of the scroll compressor according to Embodiment 1 will be described below. FIG. 1 is a schematic cross-sectional view of a scroll compressor according to this embodiment. FIG. 2 is a schematic cross-sectional view of the vicinity of the compression mechanism of the scroll compressor shown in FIG. The compressor shown in FIG. 1 is a so-called vertical scroll compressor that is used with the central axis of the main shaft substantially perpendicular to the ground. Examples of refrigerants used in the compressor of the present disclosure include HFC refrigerants such as R410A and R32, HFO refrigerants such as R1234yf and R1234ze, and natural refrigerants such as CO2. Further, as the lubricating oil, for example, refrigeration oil containing ester-based synthetic oil is used. Naturally, the present invention is not limited to these, and other refrigerants and lubricating oils may be used.

As shown in FIG. 1, the scroll compressor according to the present embodiment includes a shell 1, a frame 2, a compression mechanism section 3, a drive mechanism section 4, a subframe 5, a main shaft 6, and a power supply section 8. and.

As shown, the shell 1 is composed of three parts: a main shell 101, an upper shell 102, and a lower shell 103. The main shell 101 has a cylindrical shape, and the suction pipe 10 is connected to its side wall by welding or the like. The suction pipe 10 is a pipe that introduces refrigerant into the shell 1 as suction gas, and communicates with the inside of the main shell 101 . The upper shell 102 has a substantially hemispherical shape, and a part of its side wall is connected to the upper end of the main shell 101 by welding or the like at or near the upper end thereof, and covers the upper opening of the main shell 101 . The discharge pipe 11 is connected to the upper part of the upper shell 102 by welding or the like. The discharge pipe 11 is a pipe that discharges the refrigerant to the outside of the shell 1, and communicates with the internal space of the upper shell 102. The lower shell 103 has a substantially hemispherical shape, and a portion of its side wall is connected by welding or the like to the lower end of the main shell 101 or in the vicinity thereof, and covers the lower opening of the main shell 101. Lubricating oil 9 is stored in the lower shell 103. Note that a connecting member may be added to join each part of the shell 1.

The frame 2 is a hollow metal frame with a cavity formed in the center, and is fixed to the inner wall surface of the main shell 101. The main shaft 6 is inserted into a hollow cylindrical portion formed in the center and having a vertically penetrating through hole, and the main shaft 6 is supported by a main bearing 21 located between the frame 2 and the main shaft 6. The main bearing 21 is realized, for example, by a mechanism such as a sliding bearing or a rolling bearing. An annular flat surface 201 is formed on the upper surface side of the frame 2, that is, the surface on which the bottom surface of the oscillating scroll 32 is placed. A thrust plate 22 is arranged. In this embodiment, the thrust plate 22 functions as a thrust bearing. The same applies to subsequent embodiments. Although not shown in FIGS. 1 and 2, in a portion of the frame 2 that does not overlap with the thrust plate 22, there is a suction port that sucks refrigerant gas into the compression chamber 33, and oil is supplied from a pumping hole inside the main shaft 6. A pipe is provided to return the lubricating oil.

An Oldham accommodating portion 202 is formed between the flat surface 201 and the main shaft 6 as a groove in which the Oldham ring 12 is accommodated in a direction from the flat surface 201 toward the bottom side of the compressor. Note that instead of a groove, as shown in FIG. 4, a step may be formed from the flat surface 201 toward the bottom of the compressor, and the Oldham ring 12 may be accommodated there.

FIG. 3 is a top view of the frame 2 according to this embodiment. For explanation, FIG. 3 shows a state in which the Oldham ring 12 is placed on the frame 2. The frame 2 in FIG. 3 includes a flat surface 201, an Oldham housing portion 202, a second Oldham groove 203, and a ring-shaped projecting wall formed at the outer end of the flat surface 201 of the frame 2 and protruding toward the upper shell 102. 204, in order to provide the main bearing 21 between the hollow portion into which the main shaft 6 is inserted and the Oldham housing portion 202, a wall 205 is formed that projects upward from the Oldham housing portion 202. The thrust plate 22 is arranged on the inner flat surface 201 of the projecting wall 204, and its ring width is represented by d. Note that the height of the projecting wall 204 from the flat surface 201 may be set smaller than the thickness of the thrust plate 22 in order to facilitate slidably supporting the bottom surface of the swinging scroll 32 with the thrust plate 22. Further, the thrust plate 22 and the projecting wall 204 may be formed with a convex portion or a concave portion (not shown), and rotation of the thrust plate 22 with respect to the flat surface 201 may be inhibited by engagement of these convex portions or concave portions.

The Oldham ring 12 includes a ring portion 121, a first key portion 122, and a second key portion 123, and the ring portion 121 is accommodated in the Oldham housing portion 202. The first key portion 122 protrudes upward from the ring portion 121 and is accommodated in a first Oldham groove 321 formed on the bottom side of the swinging scroll 32. The second key part 123 protrudes downward from the ring part 121, is disposed at a position shifted by 90 degrees with respect to the first key part 122, and is inserted into a second Oldham groove 203 formed at the bottom of the Oldham housing part 202. be accommodated. As a result, when the swinging scroll 32 revolves, the first key part 122 slides in the first Oldham groove 321 and the second key part 123 slides in the second Oldham groove 203, so that the Oldham ring 12 is rotated. The moving scroll 32 is prevented from rotating.

The compression mechanism section 3 is a mechanism for compressing refrigerant, and is provided at the upper part of the shell 1, as shown in FIG. The compression mechanism section 3 includes a fixed scroll 31 and an oscillating scroll 32. The fixed scroll 31 is made of metal such as cast iron, has scroll teeth on a disc-shaped base plate, and is arranged with the scroll teeth facing the bottom side of the compressor. The oscillating scroll 32 is made of metal such as cast iron, has a disk-shaped base plate that is movable in revolution, has scroll teeth, and is engaged with the scroll teeth of the fixed scroll 31 to form a compression chamber 33 .

A discharge port 311 is formed in the center of the fixed scroll 31 to penetrate in the vertical direction and discharge refrigerant gas. The compression chamber 33 communicates with the discharge port 311 at the center of the fixed scroll 31 . A muffler 34 having a discharge hole 341 is provided on the upper end side of the fixed scroll 31, and a discharge valve 35 is provided for opening and closing the discharge hole 341 in a predetermined manner to prevent backflow of refrigerant.

As shown in FIG. 2, the fixed scroll 31 is fixed by a protrusion 111 that protrudes from the inner wall surface of the shell 1 and determines the mounting position of the fixed scroll 31. The fixed scroll 31 is fixed to the inner wall surface of the shell 1 by shrink fitting or the like, with its outer peripheral edge being supported and positioned from below by the protrusion 111. In the configuration of a typical compressor, the peripheral wall of the frame 2 for fixing the fixed scroll 31 with screws is present on the side surface of the swinging scroll 32, and the expansion of the diameter of the swinging scroll 32 is restricted. However, with the above structure, the peripheral wall of the frame 2 is eliminated, so that the side surface of the base plate on which the scroll teeth of the oscillating scroll 32 are formed faces the inner wall surface of the shell 1. Therefore, the diameter of the base plate of the oscillating scroll 32 can be designed to be large, and the compression chamber 33 is enlarged. Note that, as shown in FIG. 2, in the method of fixing the fixed scroll 31, the outer peripheral edge of the base plate may be sandwiched between the upper shell 102 and the protrusion 111. This makes it possible to suppress vibrations of the fixed scroll 31 in the vertical direction.

The swinging scroll 32 has a first Oldham groove 321, a sliding surface 322, and a convex portion 323 on the bottom surface opposite to the top surface where the scroll teeth are formed. The sliding surface 322 is formed in an annular shape on the outer peripheral side of the convex portion 323 and comes into contact with the thrust plate 22 arranged on the flat surface 201 of the frame 2 . Thereby, the thrust plate 22 slidably supports the swing scroll 32 as a thrust bearing. The convex portion 323 protrudes downward from the bottom surface of the swing scroll 32, is inserted into a recess 62 provided in the eccentric portion 61 of the main shaft 6, and is supported by a swing bearing 63 disposed between the main shaft 6 and the swing scroll 32. be done. The swing bearing 63 is realized, for example, by a mechanism such as a sliding bearing or a rolling bearing.

The main shaft 6 is a long metal rod member. The central axis of the cylindrical rod-like portion 60 of the main shaft 6 (hereinafter referred to as the central axis of the main shaft 6) is arranged so as to coincide with the central axis of the main shell 101. On the other hand, the axis (broken line) of the recess 62 provided in the eccentric portion 61 of the main shaft 6 is provided eccentrically from the central axis (dotted chain line) of the main shaft 6, as shown in FIG. The eccentric part 61 is integrated with the rod-shaped part 60, and has a cylindrical shape with the recess 62 as a hollow part and closed on the lower side. Note that an oil pumping hole (not shown) is formed inside the main shaft 6 so that the lubricating oil 9 stored in the shell 1 is sucked up by an oil pump 52 and supplied to each bearing.

Next, the positional relationship between the main bearing 21 and the swing bearing 63 will be explained. The main bearing 21 disposed on the frame 2 supporting the main shaft 6 and the swing bearing 63 disposed on the main shaft 6 supporting the convex portion 323 of the swing scroll 32 are connected to the compressor perpendicular to the central axis of the main shaft 6. In the cross section, at least a portion thereof is arranged substantially on the same plane. This "in the cross section of the compressor perpendicular to the central axis of the main shaft 6, at least a part thereof is arranged on substantially the same plane" means that the main bearing and the swing bearing as disclosed in Patent Document 1 are In order to reduce the height of the compressor, at least a portion of the cross section of the compressor perpendicular to the central axis of the main shaft 6 of the compressor is substantially the same, rather than being arranged in upper and lower positions in the axial direction. This means that they are arranged in a plane, and does not mean that they are arranged in a strict same plane, which does not allow tolerances in design dimensions.

FIG. 4 illustrates a case where the main bearing 21 and the swing bearing 63 are provided at positions shifted from each other in the axial direction. In the figure, a plane A and a plane B are shown by dashed lines as an example of a cross section of the compressor perpendicular to the central axis of the main shaft 6. In a side view of the compressor, each plane is represented by a line. In plane A, the swing bearing 63 exists but the main bearing 21 does not exist. However, in another plane B, both bearings are present. Such a relationship between both bearings is such that since a plane such as plane B exists, at least a portion of the bearings are arranged on substantially the same plane in a cross section of the compressor perpendicular to the central axis of the main shaft 6. It can be said. Note that the lengths in the axial direction of the main bearing 21 and the swing bearing 63 do not need to be the same, and may be different.

When the main bearing 21 and the swing bearing 63 are arranged in such a positional relationship, the main bearing 21 is formed on the outer diameter of the hollow part of the frame 2 into which the main shaft 6 is inserted, and the main bearing 21 is formed between the Oldham housing part 202 and the main bearing 21. In order to stably support the bearing, the wall 205 is functionally required to have a certain thickness. Since the main bearing 21 is provided in the hollow part of the frame 2 and there is a wall 205 on the outer periphery of the main bearing 21, it is not possible to penetrate the second Oldham groove 203 to the hollow part into which the main shaft 6 of the frame 2 is inserted. The groove 203 will be formed on the outer peripheral side of the wall 205. That is, the second Oldham groove 203 is formed at least a predetermined distance from the hollow portion of the frame 2 . Such an interval is a necessary configuration to stably support the main bearing 21. However, since the second key part 123 slides in the second Oldham groove 203, compared to the case where the second Oldham groove 203 can be machined through the hollow part, at least the thickness of the wall 205 is removed by the Oldham ring in the radial direction. 12 size down is limited. As a result, the ring width d of the thrust plate 22 disposed on the flat surface 201 becomes smaller, and the bearing area thereof is reduced, which may reduce the reliability of the thrust bearing. In addition, in FIG. 4, the Oldham housing portion 202 is formed not as a groove but as a step, and the wall 205 is not present, but a second Oldham groove 203 is formed at a predetermined distance from the main bearing 21. This is no different from the configurations in FIGS. 1 and 2.

In the scroll compressor of the present disclosure, the swing bearing 63 and the main bearing 21 are arranged at least partially on the same plane in a cross section of the compressor perpendicular to the central axis of the main shaft 6, and the fixed scroll 31 is arranged in a shell. The fixed scroll 31 is positioned by a protrusion 111 provided on the shell 1, and the fixed scroll 31 is directly fixed to the inner wall surface of the shell 1. With this configuration, the diameter of the base plate of the swinging scroll 32 can be increased, and thereby the area of the flat surface 201 and the thrust plate 22 can also be increased. In other words, the area reduction of the thrust bearing due to the configuration in which the swing bearing 63 and the main bearing 21 are arranged at least partially on the same plane in the cross section of the compressor perpendicular to the central axis of the main shaft 6 is This is offset by the increase in the diameter of the base plate, and the problem of reduced reliability of thrust bearings is resolved. Furthermore, the configuration of the present disclosure allows the balancer 71 to be placed closer to the eccentrically rotating oscillating scroll 32 than when the main bearing 21 and the oscillating bearing 63 are arranged one above the other. It is also possible to suppress the increase in size of the balancer 71 itself.

The drive mechanism section 4 is arranged below the frame 2 of the compression mechanism section 3 and is fixed to the inner wall surface of the main shell 101. The drive mechanism section 4 includes a stator 41 and a rotor 42. The stator 41 is, for example, a ring-shaped stator formed by winding a winding wire through an insulating layer around an iron core formed by laminating a plurality of electromagnetic steel plates. The outer peripheral surface of the stator 41 is fixed to the inner wall surface of the main shell 101 by shrink fitting or the like. The rotor 42 has a built-in permanent magnet inside an iron core made of a plurality of laminated electromagnetic steel sheets, and has a cylindrical hollow part in the center having a through hole penetrating in the vertical direction, and has a cylindrical hollow part on the inner diameter side of the stator 41. placed in the hollow part of the The outer circumferential surface of the main shaft 6 is fixed in contact with the cylindrical hollow portion of the rotor 42 . The rotational power of the drive mechanism section 4 is transmitted to the swinging scroll 32 via the main shaft 6.

The subframe 5 is a metal frame, and is provided inside the shell 1 below the drive mechanism section 4. The subframe 5 is fixed to the inner wall surface of the main shell 101 by shrink fitting or the like. The subframe 5 includes a sub-bearing 51 and an oil pump 52. The sub-bearing 51 is a ball bearing provided above the central portion of the sub-frame 5, and has a hole vertically penetrating at the center. The oil pump 52 is provided below the center of the subframe 5, and is arranged so that at least a portion thereof is immersed in the lubricating oil 9 stored in the oil reservoir of the lower shell 103.

A balancer 71 is arranged above the drive mechanism section 4. The balancer 71 is attached to offset the unbalance caused by the swinging of the swinging scroll 32, and is a weight having a cylindrical shape with an open top and bottom. The balancer 71 is located as close as possible to the swing scroll 32, and in the first embodiment is fixed to the rod-shaped portion 60 of the main shaft 6 by welding or the like.

The balancer cover 72 has a shape that surrounds the top and side surfaces of the balancer 71 to prevent the lubricating oil from becoming a mist and scattering inside the shell 1 due to the rotation of the balancer 71, and covers the bottom of the frame 2. Alternatively, it is fixedly provided to the main shaft 6. The radial dimension of the upper surface of the balancer cover 72 is designed to be longer than the rotation locus of the upper surface of the balancer 71. Further, in order to cover the side surface of the balancer 71 in the axial direction, the outer peripheral edge of the upper surface of the balancer cover 72 is bent downward to form a cylindrical shape with an open bottom. Note that in forming the side surface of the balancer cover 72, the outer peripheral edge of the upper surface is bent downward, but it may be formed by joining a plurality of parts.

The power supply unit 8 is a power supply member that supplies power to the compressor, and is formed on the outer peripheral surface of the main shell 101 of the shell 1 . The power feeding section 8 includes a cover 81, a power feeding terminal 82, and wiring 83. The cover 81 is a cover member with a bottomed opening. The power supply terminal 82 is made of a metal member, and one side is provided inside the cover 81 and the other side is provided inside the shell 1. The wiring 83 has one end connected to the power supply terminal 82 and the other end connected to the stator 41 . In addition to power supply, the wiring 83 may also transmit signals for controlling the drive of the drive mechanism section 4.

Next, an overview of the overall operation of the compressor will be explained. When power is supplied to the stator 41 of the drive mechanism section 4 from an external power source, the rotor 42 rotates, and rotational power is transmitted to the swinging scroll 32 via the main shaft 6. The swinging scroll 32 is prevented from rotating by the Oldham ring 12 and begins to revolve. In the compression chamber 33 formed by the fixed scroll 31 and the swinging scroll 32, the refrigerant sucked in from the suction pipe 10 is continuously taken in, and after being suctioned and compressed, is discharged from the discharge pipe 11. This cycle of suction, compression, and exhalation is repeated. As the main shaft 6 rotates, the lubricating oil 9 stored in the lower shell 103 is sucked up by the oil pump 52 attached to the lower end of the main shaft 6, and is pumped through the main bearing 21, the thrust plate 22 as a thrust bearing, and the rocking bearing 63. After lubricating the bearing, the oil is returned to the location where it was stored in the lower shell 103.

As described above, the scroll compressor according to the present disclosure has a shell 1 having a protrusion on the inner wall surface, a base plate and scroll teeth, and the base plate is supported by the protrusion and fixed to the inner wall surface of the shell 1. A scroll 31, an oscillating scroll 32 having a base plate and scroll teeth, a convex portion 323 formed on a surface opposite to the surface on which the scroll teeth are formed, and forming a compression chamber 33 together with the fixed scroll 31; A thrust bearing that has a main shaft 6 in which a swing bearing 63 that supports the convex portion 323 of the scroll 32 is disposed, and a hollow portion into which the main shaft 6 is inserted and slidably supports the sliding surface 322 of the swing scroll 32. and a main bearing 21 that supports the main shaft 6, and a frame 2 in which the scroll compressor is arranged, and at least a portion of the swing bearing 63 and the main bearing 21 in a cross section of the scroll compressor perpendicular to the central axis of the main shaft 6. are arranged substantially on the same plane. With such a configuration, it is possible to secure the thrust bearing area for supporting the swinging scroll 32, suppress the increase in size of the balancer, and reduce the height of the compressor. Further, by suppressing the balancer from increasing in size, the expansion of the balancer cover 72 in the radial direction is also prevented, so an increase in oil flow due to an increase in the flow rate of the refrigerant is also suppressed. Furthermore, by suppressing the size of the balancer and shortening the shaft length, it is possible to reduce compressor failures by suppressing contact between the bearing pieces due to shaft deflection during operation and improving the reliability of the thrust bearing by increasing the thrust bearing area.

Embodiment 2.
In the scroll compressor according to the second embodiment, the radius of the upper surface of the balancer cover 72 is defined. The configuration of the second embodiment will be described using FIG. 5, but the description of the configuration of each part in the figure will be omitted because it overlaps with the first embodiment.

FIG. 5 is a schematic cross-sectional view of the drive mechanism section 4 and its vicinity. The radius of the upper surface of the balancer cover 72 is r, and the length in the axial direction is t. Here, the radius r is defined as the radial dimension from the central axis of the main shaft 6 to the side surface of the balancer cover 72, and the length t is defined as the dimension from the top surface to the bottom end of the balancer cover 72. Since the balancer cover 72 surrounds the top and side surfaces of the balancer 71, the radius r of the top surface of the balancer cover 72 must be at least longer than the outer diameter of the rotation locus of the balancer 71. Further, the axial length t of the balancer cover 72 must be at least longer than the rotation locus of the side surface of the balancer 71.

In order to reduce the height of the scroll compressor, it is more preferable to make the distance between the lower end of the balancer cover 72 and the drive mechanism section 4 as narrow as possible. Furthermore, narrowing the distance between the lower end of the balancer cover 72 and the drive mechanism section 4 also leads to suppression of oil spillage. However, in the structure of a compressor, there are often a plurality of wires 83 above the stator 41, which are conductive components that collect electric wires. There is a possibility of electrical leakage due to contact with the That is, in an arrangement where the distance between the lower end of the balancer cover 72 and the drive mechanism section 4 is made as narrow as possible, if the radius r of the upper surface of the balancer cover 72 is too large, there is a risk that the lower end of the balancer cover 72 may interfere with the wiring 83. .

Therefore, in order to narrow the distance between the lower end of the balancer cover 72 and the drive mechanism section 4, the radius r of the upper surface of the balancer cover 72 is defined so that the lower end of the balancer cover 72 does not interfere with the wiring 83 of the power supply section 8. It is necessary to Although the position of the wiring 83 connected to the stator 41 differs depending on the design of each compressor, among the connection positions of one or more wiring 83 connected to the stator 41, the position closest to the central axis of the main shaft 6 is In order to avoid interference with the wiring 83, it is necessary to design the distance shorter than the distance between the nearby connection position and the central axis of the main shaft 6. With this arrangement, the radius r of the upper surface of the balancer cover 72 is shorter than the distance between the connection position of the wiring 83 to the stator 41 and the central axis of the main shaft 6, so that interference with the wiring 83 of the balancer cover 72 may occur. is avoided, the distance between the lower end of the balancer cover 72 and the drive mechanism section 4 can be narrowed, and the lower end of the balancer cover 72 can be extended to a position near the drive mechanism section 4.

Furthermore, in the motor configuration, the wiring 83 is not connected to the rotor 42 side, so in order to avoid interference with the wiring 83, the parts of the drive mechanism section 4 facing the lower end of the balancer cover 72 must be connected to the rotor 42. preferable. In order to avoid interference with the wiring 83, it is preferable that the radius r of the upper surface of the balancer cover 72 be substantially equal to or smaller than the inner diameter of the stator 41. Here, "substantially" means that if the radius r of the top surface of the balancer cover 72 exceeds the inner diameter of the stator 41 even slightly, interference with the wiring 83 will not immediately occur; This means that the upper limit of the radius r of the upper surface of the balancer cover 72 should be approximately the same as the inner diameter of the stator 41 for the purpose of avoiding this.

Expansion of the balancer 71 and balancer cover 72 in the radial direction poses a problem of oil build-up, and expansion in the axial direction poses a problem of increasing the height of the compressor. Therefore, in order to solve both problems, in the second embodiment, the radius r of the upper surface of the balancer cover 72 is defined as described above, and the balancer 71 is expanded in the radial direction within that range.

As described above, in the scroll compressor according to the present disclosure, the radius of the upper surface of the balancer cover 72 is longer than the outer diameter of the rotation locus of the upper surface of the balancer 71 around the central axis of the main shaft 6, and the Alternatively, the distance between the connection position closest to the central axis of the main shaft 6 and the central axis of the main shaft 6 among the connection positions of the plurality of wirings 83 is configured to be shorter. Moreover, as a preferable form, the radius of the upper surface of the balancer cover 72 is longer than the outer diameter of the rotation locus of the upper surface of the balancer 71 about the central axis of the main shaft 6, and is substantially equal to or smaller than the inner diameter of the stator 41. ing. As a result, it is possible to suppress expansion of the balancer 71 and the balancer cover 72 in the axial direction, and to reduce the height of the compressor. By avoiding interference with the wiring 83, it becomes possible to reduce the distance between the lower end of the balancer cover 72 and the drive mechanism section 4 as much as possible, and oil spillage is also suppressed.

Embodiment 3
In the scroll compressor according to the third embodiment, a balancer 71 is arranged on the side surface of the eccentric portion 61. The configuration of Embodiment 3 will be explained using FIG. 6, but the explanation of the configuration of each part in the figure will be omitted since it overlaps with Embodiment 1.

FIG. 6 is a schematic cross-sectional view of the vicinity of the compression mechanism section 3 according to the third embodiment. Similar to the first embodiment, in the cross section of the compressor perpendicular to the central axis of the main shaft 6, at least a portion of the swing bearing 63 and the main bearing 21 are arranged substantially on the same plane. Thereby, the axial dimension of the frame 2 can be reduced in size compared to the case where the swing bearing 63 and the main bearing 21 are arranged one above the other. In the third embodiment, the axial dimension of the frame 2 is made shorter than the axial dimension of the eccentric portion 61 of the main shaft 6.

When arranging the balancer 71 so as to balance the centrifugal force caused by the eccentric revolution of the swinging scroll 32, it is more preferable to narrow the distance between the swinging scroll 32 and the balancer 71. Therefore, by arranging the balancer 71 on the side surface of the eccentric portion 61, further enlargement of the balancer is suppressed. By arranging the balancer 71 on the side surface of the eccentric portion 61, the rod-shaped portion 60 of the main shaft 6 can be shortened, so that the height of the compressor can be reduced.

As described above, in the scroll compressor according to the present disclosure, the axial dimension of the frame 2 is made shorter than the axial dimension of the eccentric part 61, and the balancer 71 is arranged below the frame 2 and on the side surface of the eccentric part 61. It is configured. This makes it possible to suppress the increase in size of the balancer and to reduce the height of the compressor.

Embodiment 4
In the scroll compressor according to the fourth embodiment, the balancer 71 and the main shaft 6 are integrated. The configuration of the fourth embodiment will be described using FIGS. 7 and 8, but the description of the configuration of each part in the figures will be omitted because it overlaps with the first embodiment.

7 and 8 are schematic cross-sectional views of the vicinity of the compression mechanism section 3 according to the fourth embodiment. As shown in the figure, it has a structure in which the main shaft 6 and the balancer 71 are integrated. Compared to a configuration in which the main shaft 6 and the balancer 71 are fixed by press fitting, shrink fitting, etc., the volume for the fixing function becomes unnecessary by integrating the main shaft 6 and the balancer 71. As a result, the size of the balancer 71 can be further reduced because it can be configured with only the volume of the pure balance function part. Furthermore, by reducing the size of the balancer 71, expansion of the balancer 71 and balancer cover 72 in the radial and axial directions can be suppressed, which contributes to reducing the height of the compressor and suppressing oil leakage. In FIGS. 7 and 8, the balancer 71 is arranged only on the side that balances the centrifugal force caused by the eccentric revolution of the oscillating scroll 32, but if necessary, it may be additionally placed on the opposite side as in other embodiments. It is also possible to arrange. In FIG. 7, the balancer 71 is fixed to the rod-shaped part 60 of the main shaft 6, but in FIG. 8, the balancer 71 is fixed to the side surface of the eccentric part 61 of the main shaft 6.

As described above, the scroll compressor according to the present disclosure has a configuration in which the balancer 71 and the main shaft 6 are integrated. This makes it possible to suppress the increase in size of the balancer, reduce the height of the compressor, and suppress oil leakage.

The configurations shown in the embodiments described above are examples of the contents of the present invention, and can be combined with other known techniques, and the configurations can be modified without departing from the gist of the present invention. It is also possible to omit or change the section.

1 shell, 101 main shell, 102 upper shell, 103 lower shell, 10 suction pipe, 11 discharge pipe, 111 protrusion, 12 Oldham ring, 121 ring part, 122 first key part, 123 second key part, 2 frame, 201 flat surface, 202 Oldham housing section, 203 second Oldham groove, 204 projecting wall, 205 wall, 21 main bearing, 22 thrust plate, 3 compression mechanism section, 31 fixed scroll, 311 discharge port, 32 swinging scroll, 321 first Oldham groove, 322 sliding surface, 323 convex portion, 33 compression chamber, 34 muffler, 341 discharge hole, 35 discharge valve, 4 drive mechanism section, 41 stator, 42 rotor, 5 subframe, 51 sub-bearing, 52 oil pump, 6 main shaft, 60 rod-shaped part, 61 eccentric part, 62 recess, 63 swing bearing, 71 balancer, 72 balancer cover, 8 power supply part, 81 cover, 82 power supply terminal, 83 wiring, 9 lubricating oil

Claims (7)

A scroll compressor,
a shell having a protrusion on an inner wall surface;
a suction pipe connected to the shell and introducing refrigerant into the shell;
a fixed scroll having a base plate and scroll teeth, the base plate being supported by the protrusion and fixed to the inner wall surface of the shell;
an oscillating scroll having a base plate and scroll teeth, a convex portion being formed on a surface opposite to the surface on which the scroll teeth are formed, and forming a compression chamber together with the fixed scroll;
a main shaft on which a swing bearing that supports the convex portion of the swing scroll is disposed;
a subframe fixed to the inner wall surface of the shell;
a sub-bearing provided in the sub-frame and into which a lower part of the main shaft is inserted;
A thrust bearing having a hollow portion into which the main shaft is inserted and slidably supporting the sliding surface of the oscillating scroll, and a main bearing supporting the main shaft are arranged, a frame including a suction port that sucks the refrigerant introduced into the compression chamber and guides the refrigerant to the compression chamber;
a discharge pipe connected to the shell and discharging the refrigerant compressed in the compression chamber;
A scroll compressor, wherein in a cross section of the scroll compressor perpendicular to a central axis of the main shaft, at least a portion of the swing bearing and the main bearing are arranged substantially in the same plane. The main shaft includes an eccentric part having a recess provided eccentrically from the central axis of the main shaft, and the swing bearing that supports the convex part of the swing scroll is provided in the recess of the eccentric part. The scroll compressor according to claim 1. An Oldham ring for preventing rotation of the oscillating scroll is provided on the inner diameter side of the thrust bearing,
The frame is formed with an Oldham accommodating portion for accommodating the Oldham ring, and an Oldham groove for accommodating a key portion protruding downward from the ring portion of the Oldham ring. The scroll compressor according to claim 1 or 2, wherein the scroll compressor is formed at least a predetermined distance from the hollow portion. It has a stator formed in a ring shape and fixed to the inner wall surface of the shell, and a rotor arranged in a hollow part on the inner diameter side of the stator and fixed to the outer peripheral surface of the main shaft, and the rotor is arranged below the frame. a drive mechanism section disposed in;
a balancer disposed above the drive mechanism section;
a balancer cover surrounding the top and side surfaces of the balancer;
The radius of the upper surface of the balancer cover is longer than the outer diameter of the rotation locus of the upper surface of the balancer around the central axis of the main shaft, and is within the connection position of one or more wirings connected to the stator. The scroll compressor according to any one of claims 1 to 3, wherein the distance is shorter than the distance between the connection position closest to the central axis of the main shaft and the central axis of the main shaft. 5. The radius of the upper surface of the balancer cover is longer than the outer diameter of the rotation locus of the upper surface of the balancer around the central axis of the main shaft, and is substantially equal to or less than the inner diameter of the stator. Scroll compressor as described. 5. The axial dimension of the frame is shorter than the axial dimension of the eccentric part of the main shaft, and the balancer is fixed to a side surface of the eccentric part below the frame. 5. The scroll compressor according to 5. The scroll compressor according to any one of claims 4 to 6, wherein the main shaft and the balancer are integrally constructed.

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