JP5773922B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor used as one component of a refrigeration cycle employed in, for example, an air conditioner or a refrigeration apparatus.

  Conventional scroll compressors generally have thrust bearings (thrust bearings) in which a reamer bolt hole is provided in the oscillating scroll thrust bearing surface into which the reamer bolt is inserted in order to ensure the slidability of the oscillating scroll thrust bearing surface. The bearing is arranged (see, for example, Patent Document 1). The thrust bearing is positioned by inserting the reamer bolt into the reamer bolt hole. A total of two reamer bolt holes are formed. One is formed in a circular round hole shape, and the other is formed in an oval long hole shape composed of two semicircles and two straight portions. The two reamer bolt holes are arranged asymmetrically with respect to the center of the thrust bearing in order to prevent misconfiguration.

  The reamer bolt hole is formed to have a predetermined clearance between the reamer bolt and the outer periphery of the head. The longitudinal clearance of the reamer bolt and the elongated hole shape reamer bolt hole is set to be larger than the clearance between the reamer bolt and the round hole shape reamer bolt hole, and the longitudinal direction of the elongated hole shape reamer bolt hole faces the center direction of the thrust bearing. Has been.

JP 2009-074477 (page 5-10, FIG. 2-3, etc.)

  In the scroll compressor configured as described in Patent Document 1, the longitudinal clearance between the reamer bolt and the elongated hole-shaped reamer bolt hole is larger than the clearance between the reamer bolt and the round hole-shaped reamer bolt hole. For this reason, there is a time when the thrust bearing is supported by only one reamer bolt positioned in the round reamer bolt hole during one rotation of the swing scroll in which the reamer bolt is inserted, and the maximum per reamer bolt is present. The support load was large. As a result, in order to ensure the reliability of the reamer bolt, it is necessary to use a reamer bolt having a large shape or a reamer bolt formed of a high strength material, which increases the cost accordingly.

  Further, in the scroll compressor having the configuration described in Patent Document 1, in order to reduce the centrifugal force of the thrust bearing supported by the reamer bolt, it is necessary to reduce the thrust bearing and to reduce the thrust bearing area. there were. This would increase the surface pressure of the thrust bearing. As a result, in order to ensure the reliability of the thrust bearing, it is necessary to use a thrust bearing formed of a material having more excellent sliding characteristics, which incurs an increase in cost.

  Furthermore, in the scroll compressor having the configuration described in Patent Document 1, two reamer bolt holes are arranged asymmetrically with respect to the center of the thrust bearing, and the longitudinal direction of the elongated reamer bolt hole is the center of the thrust bearing. It is suitable. Therefore, the longitudinal direction of the elongated hole-shaped reamer bolt hole does not coincide with the center direction of the round hole-shaped reamer bolt hole, and the deflection width of the thrust bearing relative to the reamer bolt during one rotation of the orbiting scroll is large. As a result, in order to suppress wear and dents caused by the contact between the thrust bearing and the reamer bolt, the clearance between the thrust bearing and the reamer bolt is controlled to be small, or the thrust bearing and reamer bolt made of a material having high wear characteristics and high strength are used. It was necessary to use it, which caused an increase in cost.

  The present invention has been made to solve at least one of the above-described problems, and an object of the present invention is to provide a scroll compressor having low cost and high reliability and performance.

  A scroll compressor according to the present invention includes a hermetic container, a fixed scroll fixed in the hermetic container, a swing scroll combined to swing with respect to the fixed scroll, and a swing scroll. A rotary drive means for moving, a plurality of insertion members inserted into a rocking scroll thrust bearing surface of the rocking scroll, and a number of insertion member holes corresponding to the number of the insertion members, and the rocking scroll A thrust bearing disposed on the thrust bearing surface side and supporting the orbiting scroll, wherein the insertion member hole is formed in a round hole shape, and is formed in a long hole shape. At least two of the insertion member holes formed in the shape of the elongated hole are arranged so that their longitudinal directions are different from each other. Aransu is characterized in that it is larger than the clearance between the insertion member and the insertion member hole formed in a round hole shape.

  According to the scroll compressor according to the present invention, the maximum support load per one insertion member can be reduced. Therefore, the insertion member can be made smaller, or the insertion member can be made of a less expensive material, the thrust bearing surface pressure can be lowered, and the thrust bearing can be improved in reliability and reduced in thrust bearing sliding loss. .

It is a longitudinal cross-sectional view which shows the cross-sectional structural example of the scroll compressor which concerns on Embodiment 1 of this invention. It is a perspective view which expands and shows the rocking | fluctuation scroll and thrust bearing of the scroll compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating the effect | action of the reamer bolt and thrust bearing of the scroll compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating the positional relationship of the reamer bolt hole formed in the thrust bearing of the scroll compressor which concerns on Embodiment 2 of this invention. It is explanatory drawing for demonstrating the positional relationship of the reamer bolt hole formed in the thrust bearing of the scroll compressor which concerns on Embodiment 3 of this invention. It is explanatory drawing for demonstrating the positional relationship of the reamer bolt hole formed in the thrust bearing of the scroll compressor which concerns on Embodiment 4 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1.
FIG. 1 is a longitudinal sectional view showing a cross-sectional configuration example of a scroll compressor 100 according to Embodiment 1 of the present invention. Based on FIG. 1, the structure and operation | movement of the scroll compressor 100 are demonstrated. The scroll compressor 100 is one of the components of a refrigeration cycle used in various industrial machines such as a refrigerator, a freezer, a vending machine, an air conditioner, a refrigeration apparatus, and a water heater. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one.

  The scroll compressor 100 sucks the refrigerant circulating in the refrigeration cycle, compresses it, and discharges it as a high-temperature and high-pressure state. The scroll compressor 100 includes a compression mechanism in which a fixed scroll 1 and an orbiting scroll 2 that swings with respect to the fixed scroll 1 are combined in an airtight container 24 including a center shell 7, an upper shell 22, and a lower shell 23. ing. In addition, the scroll compressor 100 is provided with a rotation driving means including an electric rotary machine or the like in the sealed container 24. As shown in FIG. 1, in the sealed container 24, the compression mechanism is disposed on the upper side, and the rotation driving means is disposed on the lower side.

  The sealed container 24 is configured by providing an upper shell 22 and a lower shell 23 on the upper and lower portions of the center shell 7. The lower shell 23 is an oil sump for storing lubricating oil. The center shell 7 is connected with a suction pipe 15 for sucking refrigerant gas. A discharge pipe 17 for discharging the refrigerant gas is connected to the upper shell 22. The inside of the center shell 7 is a low pressure chamber 18, and the inside of the upper shell 22 is a high pressure chamber 19.

  The fixed scroll 1 is composed of a fixed scroll base plate 1b and a fixed scroll spiral 1a which is a spiral projection standing on one surface of the fixed scroll base plate 1b. The orbiting scroll 2 is an orbiting scroll base plate 2b and an orbiting scroll that is provided on one surface of the orbiting scroll base plate 2b and is a spiral protrusion having substantially the same shape as the fixed scroll volute 1a. And the spiral 2a. The other surface of the swing scroll base plate 2b (the surface opposite to the surface on which the swing scroll spiral 2a is formed (back surface)) acts as the swing scroll thrust bearing surface 2c. Further, the center side of the swing scroll thrust bearing surface 2c of the swing scroll base plate 2b is a convex portion 2d protruding downward.

  Three reamer bolts 4 are inserted into the orbiting scroll thrust bearing surface 2c. When the scroll compressor 100 is assembled, the head of the reamer bolt 4 is positioned in the reamer bolt hole (insertion member hole) 26 formed in the thrust bearing 3 in a state where the reamer bolt 4 is inserted into the swing scroll thrust bearing surface 2c. The thrust bearing 3 is formed in a ring shape, and the convex portion 2d of the orbiting scroll 2 is located in the central portion (hereinafter referred to as the central space portion 3a for convenience). The lower surface of the thrust bearing 3 is positioned below the tip surface of the convex portion 2d. The reamer bolt 4 and the thrust bearing 3 will be described in detail with reference to FIGS.

  Here, a case where the reamer bolt 4 is provided in the swing scroll thrust bearing surface 2c and the reamer bolt hole 26 is provided in the thrust bearing 3 will be described as an example. However, the insertion member hole is provided in the swing scroll thrust bearing surface 2c, and the thrust bearing 3 is provided. An insertion member may be provided. By adopting such a configuration, the insertion member hole of the thrust bearing 3 is eliminated and the thrust area is further increased, so that the thrust surface pressure can be lowered and the reliability performance can be further improved. Moreover, since the reamer bolt itself can be eliminated, the number of parts can be reduced.

  The orbiting scroll 2 is configured such that a thrust bearing load generated during the operation of the compressor is supported by the frame 20 via the thrust bearing 3. If the frame 20 does not have sufficient hardness with respect to the thrust bearing load, a material having sufficient hardness with respect to the thrust bearing load is interposed between the thrust bearing 3 and the frame 20 as shown in FIG. It is good also as a structure which inserts the thrust plate 5 which consists.

  The orbiting scroll 2 and the fixed scroll 1 are mounted in an airtight container 24 by combining the orbiting scroll spiral 2a and the fixed scroll spiral 1a. In a state where the swing scroll 2 and the fixed scroll 1 are combined, the winding directions of the fixed scroll spiral 1a and the swing scroll spiral 2a are opposite to each other. A compression chamber 30 whose volume changes relatively is formed between the swing scroll spiral 2a and the fixed scroll spiral 1a. Note that the fixed scroll 1 and the orbiting scroll 2 have a front end surface (upper surface) of the fixed scroll swirl 1a and the orbiting scroll swirl 2a in order to reduce refrigerant leakage from the front end surfaces of the fixed scroll swirl 1a and the orbiting scroll swirl 2a. Seals 31 and 32 are disposed on the end surface and the lower end surface.

  The fixed scroll 1 is fixed to the frame 20 with bolts or the like not shown. A discharge port 16 is formed at the center of the fixed scroll base plate 1b of the fixed scroll 1 to discharge the compressed refrigerant gas having a high pressure. The compressed refrigerant gas having a high pressure is discharged into a high-pressure chamber 19 provided in the upper part of the fixed scroll 1. The refrigerant gas discharged to the high pressure chamber 19 is discharged to the refrigeration cycle via the discharge pipe 17. The discharge port 16 is provided with a discharge valve 33 for preventing the refrigerant from flowing backward from the high pressure chamber 19 to the discharge port 16 side.

  The oscillating scroll 2 performs a revolving orbiting motion (oscillating motion) without rotating about the fixed scroll 1 by an Oldham ring 14 for preventing the rotating motion. A hollow cylindrical boss 2e is formed at a substantially central portion of the surface of the swing scroll 2 opposite to the surface on which the swing scroll spiral 2a is formed. An eccentric shaft portion 8a provided at the upper end of the main shaft 8 is inserted into the boss portion 2e.

  The Oldham ring 14 is installed such that the Oldham claw is accommodated in an Oldham groove (Oldham groove 6a shown in FIG. 2) formed in the convex portion 2d of the swing scroll 2 and the swing scroll thrust bearing surface 2c. . The thrust bearing 3 is provided with an Oldham ring relief groove 6b. The Oldham ring relief groove 6b is formed in order to avoid interference with the Oldham groove 6a formed on the swing scroll thrust bearing surface 2c. The Oldham ring 14 may be installed on the swing scroll spiral 2a forming surface side of the swing scroll 2 of the swing scroll base plate 2b.

  The rotation driving means includes a rotor 11 fixed to the main shaft 8, a stator 10, a main shaft 8 that is a rotation shaft, and the like. The rotor 11 is shrink-fitted and fixed to the main shaft 8 and is driven to rotate when the energization of the stator 10 is started to rotate the main shaft 8. That is, the stator 10 and the rotor 11 constitute an electric rotating machine. The rotor 11 is disposed below the first balance weight 12 that is fixed to the main shaft 8 together with the stator 10 that is shrink-fitted and fixed to the center shell 7. The stator 10 is supplied with power via a power supply terminal 9 provided in the center shell 7.

  The main shaft 8 rotates with the rotation of the rotor 11 to turn the orbiting scroll 2. The upper portion of the main shaft 8 (in the vicinity of the eccentric shaft portion 8a) is supported by a main bearing 21 provided on the frame 20. On the other hand, the lower portion of the main shaft 8 is rotatably supported by the auxiliary bearing 35. The sub-bearing 35 is press-fitted and fixed in a bearing housing portion formed at the center of a sub-frame 34 provided at the lower part of the sealed container 24. Further, the sub-frame 34 is provided with a positive displacement oil pump (not shown). The lubricating oil sucked by the oil pump is sent to each sliding portion through an oil hole (not shown) formed inside the main shaft 8.

  In addition, a first balance weight 12 is provided on the upper portion of the main shaft 8 in order to cancel out an unbalance caused by the swing scroll 2 being mounted on the eccentric shaft portion 8a and swinging. A second balance weight 13 is provided at the lower part of the rotor 11 in order to cancel out imbalance caused by the swing scroll 2 being mounted on the eccentric shaft portion 8a and swinging. The first balance weight 12 is fixed to the upper part of the main shaft 8 by shrink fitting, and the second balance weight 13 is fixed to the lower part of the rotor 11 integrally with the rotor 11.

Next, the operation of the scroll compressor 100 will be described.
When the power supply terminal 9 is energized, a current flows through the electric wire portion of the stator 10 and a magnetic field is generated. This magnetic field acts to rotate the rotor 11. That is, torque is generated in the stator 10 and the rotor 11, and the rotor 11 rotates. When the rotor 11 rotates, the main shaft 8 is rotationally driven accordingly. When the main shaft 8 is driven to rotate, the orbiting scroll 2 whose rotation is suppressed by the Oldham ring 14 performs an orbiting motion.

  When the rotor 11 rotates, the swinging scroll 2 and the thrust bearing 3 are composed of a first balance weight 12 fixed to the upper part of the main shaft 8 and a second balance weight 13 fixed to the lower part of the rotor 11. Maintains a static and dynamic balance with respect to the eccentric revolving motion. As a result, the orbiting scroll 2 that is eccentrically supported on the upper portion of the main shaft 8 and whose rotation is suppressed by the Oldham ring 14 is swung to start revolving, and the refrigerant is compressed by a known compression principle.

  As a result, part of the refrigerant gas flows into the compression chamber 30 via the suction port (not shown) of the frame 20, and the suction process is started. Further, the remaining part of the refrigerant gas passes through the notch (not shown) of the steel plate of the stator 10 to cool the electric rotating machine and the lubricating oil. The compression chamber 30 moves to the center of the orbiting scroll 2 by the orbiting motion of the orbiting scroll 2, and the volume is further reduced. Through this process, the refrigerant gas sucked into the compression chamber 30 is compressed. The compressed refrigerant passes through the discharge port 16 of the fixed scroll 1, pushes the discharge valve 33 open, and flows into the high-pressure chamber 19. Then, it is discharged from the sealed container 24 through the discharge pipe 17.

  The thrust bearing load generated by the pressure of the refrigerant gas in the compression chamber 30 is received by the frame 20 that supports the thrust bearing 3. The reamer bolt 4 supports the resultant force of the frictional force between the thrust bearing 3 and the frame 20 generated by the thrust bearing load and the centrifugal force of the thrust bearing 3. Further, the main bearing 21 and the sub-bearing 35 receive the centrifugal force and the refrigerant gas load generated in the first balance weight 12 and the second balance weight 13 as the main shaft 8 rotates. Note that the low-pressure refrigerant gas in the low-pressure chamber 18 and the high-pressure refrigerant gas in the high-pressure chamber 19 are partitioned by the fixed scroll 1 and the frame 20 and are kept airtight. When the energization of the stator 10 is stopped, the scroll compressor 100 stops operating.

  FIG. 2 is an enlarged perspective view showing the orbiting scroll 2 and the thrust bearing 3. FIG. 3 is an explanatory diagram for explaining the operation of the reamer bolt 4 and the thrust bearing 3. The reamer bolt 4 and the thrust bearing 3 will be described in detail based on FIG. 2 and FIG.

  As shown in FIG. 2, three reamer bolts 4 are inserted into the orbiting scroll thrust bearing surface 2c. The reamer bolt 4 is inserted so that its head protrudes from the orbiting scroll thrust bearing surface 2c. The head of the reamer bolt 4 is inserted into the reamer bolt hole 26 of the thrust bearing 3. That is, the thrust bearing 3 is positioned on the orbiting scroll thrust bearing surface 2c by the reamer bolt hole 26 and the reamer bolt 4 formed in itself. Three reamer bolt holes 26 are formed according to the number of reamer bolts 4.

  As shown in FIG. 3, one of the three reamer bolt holes 26 is formed in a circular round hole shape (hereinafter referred to as a round hole 27). The remaining two of the three reamer bolt holes 26 are each formed in a long hole shape composed of two semicircles and two straight portions (hereinafter referred to as a long hole A28 and a long hole B29). The long hole A28 and the long hole B29 are formed so that the directions in the longitudinal direction are different. Further, the clearance in the longitudinal direction of the long hole A28 and the long hole B29 and the reamer bolt 4 is formed to be larger than the clearance between the reamer bolt 4 and the round hole 27. The orientation of the long hole A28 and the long hole B29 is determined in consideration of the fact that two or more reamer bolts 4 are always in contact with the inner wall surface of the reamer bolt hole 26 with respect to the rotation of the orbiting scroll 2.

  In the state where the thrust bearing 3 is installed on the orbiting scroll thrust bearing surface 2c, the positional relationship between the tip surface of the convex portion 2d of the orbiting scroll 2 and the lower surface of the thrust bearing 3 is as described above. Further, the end surface of the head of the reamer bolt 4 is located above the lower surface of the thrust bearing 3 in a state where the thrust bearing 3 is installed on the orbiting scroll thrust bearing surface 2c.

The configuration of the scroll compressor 100 is summarized below.
First, the thrust bearing 3 is positioned with respect to the orbiting scroll thrust bearing surface 2 c by using three reamer bolts 4.
Secondly, three reamer bolt holes 26 are formed as a round hole 27, a long hole A28, and a long hole B29, and the longitudinal direction of the long hole A28 and the longitudinal direction of the long hole B29 are set in different directions. I try to face it.
Third, the clearance between the longitudinal direction of the long hole A28 and the long hole B29 and the reamer bolt 4 is made larger than the clearance between the reamer bolt 4 and the round hole 27.

  With this configuration, it is possible to always support the thrust bearing 3 with two or more reamer bolts 4 during one rotation of the orbiting scroll 2. That is, since the two or more reamer bolts 4 are in contact with the inner wall surface of the reamer bolt hole 26 (in FIG. 3, the round hole 27 and the long hole B29), the two or more reamer bolts 4 are always in contact. The thrust bearing 3 can be supported by the above reamer bolt 4. Therefore, according to the scroll compressor 100, the maximum support load per one reamer bolt 4 can be reduced, and the reamer bolt 4 can be configured to be small, or the reamer bolt 4 can be configured with a less expensive material.

  Further, since the maximum support load per reamer bolt 4 can be reduced, the thrust bearing 3 can be enlarged and the thrust bearing area can be further increased. Therefore, according to the scroll compressor 100, it is possible to reduce the thrust bearing surface pressure, and it is possible to improve the reliability of the thrust bearing and increase the efficiency by reducing the thrust bearing sliding loss.

Embodiment 2. FIG.
FIG. 4 is an explanatory diagram for explaining the positional relationship of the reamer bolt holes 26 formed in the thrust bearing 3 of the scroll compressor according to the second embodiment of the present invention. Based on FIG. 4, the positional relationship of the reamer bolt hole 26 of the scroll compressor according to the second embodiment will be described. In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.

  In the second embodiment, the midpoint X of the line that satisfies the structural conditions of the first embodiment and connects the center of the round hole 27 and the center of the elongated hole A28 and the center O of the thrust bearing 3 are connected. The longitudinal direction of the long hole B29 is made to coincide with the direction of the ellipse. Similarly, in the second embodiment, the midpoint Y of the line that satisfies the configuration conditions of the first embodiment and connects the center of the round hole 27 and the center of the elongated hole B29, and the center O of the thrust bearing 3 The longitudinal direction of the long hole A28 is made to coincide with the direction of the line connecting. That is, in the second embodiment, the longitudinal directions of the long hole A28 and the long hole B29 are more specific than those in the first embodiment.

  With this configuration, the load direction applied to the reamer bolt 4 coincides with the longitudinal direction of the long hole A28, and the reamer bolt 4 located in the round hole 27 and the reamer bolt 4 located in the long hole B29 are two. When the thrust bearing 3 is supported, the support load applied to the two reamer bolts 4 can be made uniform. Similarly, the load direction applied to the reamer bolt 4 coincides with the longitudinal direction of the long hole B29, and the thrust bearing 3 is supported by the reamer bolt 4 located in the round hole 27 and the reamer bolt 4 located in the long hole A28. The supporting load applied to the two reamer bolts 4 can be made uniform when

  As a result, in addition to the effects of the first embodiment, the maximum support load per reamer bolt 4 can be further reduced, and the reamer bolt 4 can be made smaller, or the reamer bolt 4 can be made of a lower cost material. Play. Further, in addition to the effect of the first embodiment, the maximum support load per reamer bolt 4 can be further reduced, so that the thrust bearing 3 can be further increased and the thrust bearing area can be further increased. Therefore, according to the scroll compressor according to the second embodiment, the thrust bearing surface pressure can be further lowered, and higher efficiency can be achieved by further improving the reliability of the thrust bearing and further reducing the sliding loss of the thrust bearing. .

Embodiment 3 FIG.
FIG. 5 is an explanatory diagram for explaining the positional relationship of the reamer bolt holes 26 formed in the thrust bearing 3 of the scroll compressor according to the third embodiment of the present invention. Based on FIG. 5, the positional relationship of the reamer bolt hole 26 of the scroll compressor according to Embodiment 3 will be described. In the third embodiment, differences from the first and second embodiments will be mainly described, and the same parts as those in the first and second embodiments will be denoted by the same reference numerals and the description thereof will be omitted. It shall be.

  In the third embodiment, the configuration condition of the first embodiment is satisfied, and the direction of the line connecting the center of the round hole 27 and the center of the elongated hole A28 is matched with the longitudinal direction of the elongated hole A28. Yes. Similarly, in the third embodiment, the configuration condition of the first embodiment is satisfied, and the direction of the line connecting the center of the round hole 27 and the center of the elongated hole B29 is matched with the longitudinal direction of the elongated hole B29. I am doing so. That is, in the third embodiment, the longitudinal direction of the long hole A28 and the long hole B29 is more specific than that in the first embodiment.

  With such a configuration, since the longitudinal direction of the long holes (the long holes A28 and B29) and the swing width of the thrust bearing 3 with respect to the reamer bolt 4 in the long holes are orthogonal, the swing of the thrust bearing 3 with respect to the reamer bolt 4 The width is minimized. From the diagram shown in the lower part of FIG. 5, it can be seen that the arrow (1) is shorter than the arrow (2). Since this arrow (1) is the swing width of the thrust bearing 3 with respect to the reamer bolt 4, it can be seen that the swing width is minimized.

  As a result, in addition to the effects of the first embodiment, wear and dents caused by the contact between the thrust bearing 3 and the reamer bolt 4 can be suppressed, and the reliability can be further improved. 3 and the reamer bolt 4 can be configured, and the cost can be further reduced.

Embodiment 4 FIG.
FIG. 6 is an explanatory diagram for explaining the positional relationship of the reamer bolt holes 26 formed in the thrust bearing 3 of the scroll compressor according to the fourth embodiment of the present invention. Based on FIG. 6, the positional relationship of the reamer bolt hole 26 of the scroll compressor according to the fourth embodiment will be described. In the fourth embodiment, differences from the first to third embodiments will be mainly described, and the same parts as those in the first to third embodiments will be denoted by the same reference numerals and the description thereof will be omitted. It shall be.

  In the fourth embodiment, the midpoint X of the line that satisfies the configuration conditions of the first embodiment and connects the center of the round hole 27 and the center of the elongated hole A28 and the center O of the thrust bearing 3 are connected. The direction of the line (line (α1)), the longitudinal direction of the long hole B29 (line (α2)), the direction of the line connecting the center of the round hole 27 and the center of the long hole B29 (line (α3)), The three directions are matched. Similarly, in the fourth embodiment, the midpoint Y of the line that satisfies the configuration conditions of the first embodiment and connects the center of the round hole 27 and the center of the elongated hole B29, the center O of the thrust bearing 3, and Direction of the line (line (β1)), longitudinal direction of the long hole A28 (line (β2)), direction of the line connecting the center of the round hole 27 and the center of the long hole A28 (line (β3)) ), And the three directions are matched.

  That is, in the fourth embodiment, the longitudinal direction of the long hole A28 and the long hole B29 is more specific than that in the first embodiment. Specifically, in the fourth embodiment, the lines (β1), (β2), and (β3) are parallel so that the lines (α1), (α2), and (α3) are parallel to each other. Thus, the orientation and formation position of the reamer bolt hole 26 are determined.

  With this configuration, the maximum support load per reamer bolt 4 can be further reduced and the thrust bearing runout against the reamer bolt 4 in the long holes (the long hole A28 and the long hole B29) can be minimized. can do. Thereby, in addition to the effects of the first embodiment, it is possible to configure the thrust bearing 3 and the reamer bolt 4 with a less expensive material, and the cost can be further reduced.

  In the first to fourth embodiments, the case where the reamer bolt 4 is used as an insertion member necessary for positioning the thrust bearing 3 with respect to the orbiting scroll thrust bearing surface 2c has been described as an example. The member is not limited to the reamer bolt 4, and any member may be used as long as the thrust bearing 3 can be positioned with respect to the swing scroll thrust bearing surface 2c. Further, four or more reamer bolt holes 26 may be formed as long as the three reamer bolt holes 26 satisfy the contents described in any of the first to fourth embodiments.

  DESCRIPTION OF SYMBOLS 1 Fixed scroll, 1a Fixed scroll swirl, 1b Fixed scroll base plate, 2 Swing scroll, 2a Swing scroll swirl, 2b Swing scroll base plate, 2c Swing scroll thrust bearing surface, 2d Convex part, 2e Boss part, 3 Thrust bearing, 3a center space, 4 reamer bolt, 5 thrust plate, 6 Oldham groove, 6a Oldham groove, 6b Oldham ring relief groove, 7 Center shell, 8 Main shaft, 8a Eccentric shaft, 9 Power supply terminal, 10 Stator, 11 Rotor, 12 First balance weight, 13 Second balance weight, 14 Oldham ring, 15 Suction pipe, 16 Discharge port, 17 Discharge pipe, 18 Low pressure chamber, 19 High pressure chamber, 20 Frame, 21 Main bearing, 22 Upper shell, 23 Lower shell, 24 Airtight container, 26 Lee Bolt holes, 27 round hole, 28 long holes A, 29 slot B, 30 compression chamber, 31 seals, 32 seal, 33 discharge valve, 34 sub-frames, 35 auxiliary bearing, 100 a scroll compressor.

Claims (5)

A sealed container;
A fixed scroll fixed in the sealed container;
A swing scroll combined so as to swing with respect to the fixed scroll;
Rotational drive means for swinging the swing scroll;
A plurality of insertion members inserted into the orbiting scroll thrust bearing surface of the orbiting scroll;
A number of insertion member holes corresponding to the number of the insertion members, and a thrust bearing disposed on the rocking scroll thrust bearing surface side to support the rocking scroll,
The insertion member hole is
At least one formed in a round hole shape and at least two formed in a long hole shape are formed,
The insertion member hole formed in the elongated hole shape is
It is arranged so that the direction of the longitudinal direction is different, and the clearance between the longitudinal direction and the insertion member is formed larger than the clearance between the insertion member hole formed in a round hole shape and the insertion member. Scroll compressor. The elongated hole-shaped insertion member hole is
The scroll compressor according to claim 1, wherein the scroll compressor is formed in an elongated hole shape from two semicircles and two straight portions. In the direction of the line connecting the center of the round hole-shaped insertion member hole and the center of one elongated hole-shaped insertion member hole and the center of the thrust bearing, the other long Match the longitudinal direction of the hole-shaped insertion member hole,
In the direction of the line connecting the center of the round hole-shaped insertion member hole and the center of the other elongated hole-shaped insertion member hole and the center of the thrust bearing, The scroll compressor according to claim 1 or 2, wherein the longitudinal direction of the hole-shaped insertion member hole is matched. The direction of the line connecting the center of the insertion member hole of the round hole shape and the center of the insertion member hole of one elongated hole shape is matched with the longitudinal direction of the insertion member hole of the one elongated hole shape,
The direction of the line connecting the center of the round hole-shaped insertion member hole and the center of the other long hole-shaped insertion member hole is matched with the longitudinal direction of the other long hole-shaped insertion member hole. The scroll compressor according to claim 1 or 2, characterized by the above-mentioned. The direction of the line connecting the center of the circular hole-shaped insertion member hole and the center of one elongated hole-shaped insertion member hole and the center of the thrust bearing, and the other elongated hole-shaped The direction of the longitudinal direction of the insertion member hole, the direction of the line connecting the center of the insertion member hole of the round hole shape and the center of the insertion member hole of the other elongated hole shape are matched,
The direction of the line connecting the center of the circular hole-shaped insertion member hole and the center of the other elongated hole-shaped insertion member hole and the center of the thrust bearing, The direction of the insertion member hole in the longitudinal direction, the direction of the line connecting the center of the insertion member hole of the round hole shape and the center of the insertion member hole of the one elongated hole shape, and the three directions are matched. The scroll compressor according to claim 1 or 2, characterized by the above-mentioned.

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