JP2008208717A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a scroll compressor suppressing generation of abnormal noise. <P>SOLUTION: This scroll compressor is provided with: a fixed scroll and a slewing scroll; a main shaft 9 rotatably supported around a center axis; a driving pin 59 extending along the center axis; a bush 63 formed with an eccentric hole 63 into which the driving pin 59 is rotatably inserted; a limit pin 65 decentered from the center axis and also extending along the center axis from a position different from the driving pin 59, in one of the main shaft 9 and the bush 63; a limit hole 61 extending along the center axis from a position opposite to the limit pin 65 for inserting the limit pin 65 and having larger diameter than that of the limit pin 65, in either of the main shaft 9 and the bush 63; and an elastic portion 73 arranged in contact with the limit pin 65 and limit hole 61 between the limit pin 65 and the limit hole 61. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a scroll compressor, and more particularly to a scroll compressor driven by a motor.

  In general, a scroll compressor forms a compression chamber for compressing a compressible fluid such as gas between a fixed scroll and a turning scroll, and orbits the turning scroll to reduce the volume of the compression chamber. The gas is compressed.

  The scroll type compressor employs a configuration in which the orbiting scroll is pressed against the fixed scroll by using a reaction force generated during gas compression in order to ensure the function and performance as the compressor. By adopting such a configuration, fluid leakage from the compression chamber is prevented during gas compression, and the function and performance as a compressor are ensured.

In a scroll compressor employing the above-described configuration, when an incompressible fluid such as a liquid is present in the compression chamber, the reaction force generated during compression is greater than when a gas is compressed. . As a result, the force for pressing the orbiting scroll against the fixed scroll also increases, and there is a problem that a liquid escape passage in the compression chamber cannot be secured. In particular, when the reaction force is increased, the fixed scroll or the turning scroll may be damaged.
In addition, when a foreign object is caught between the fixed scroll and the orbiting scroll, a reaction force is generated due to the biting of the foreign object, and the escape path for the foreign object cannot be secured, and the fixed scroll may be damaged. .

In order to solve the above-mentioned problem, for example, when there is a possibility that a fixed scroll or the like may be damaged, the turning radius of the orbiting scroll is changed using the generated reaction force to secure an escape passage for liquid or foreign matter (A mechanism composed of a pin and an arcuate groove, hereinafter referred to as a swing link mechanism) has been proposed (see, for example, Patent Document 1).
JP-A-61-215481

  Since the scroll compressor using the swing link mechanism described above changes the turning radius of the orbiting scroll by moving the pin along the arcuate groove, the pin contacts the end of the arcuate groove. There has been a problem that the noise is repeatedly generated, for example, an abnormal noise such as “katakata”.

  Examples of the predetermined situation include when the scroll compressor whose orbiting scroll behavior is unstable is started or stopped. In particular, at the time of start-up, liquid often accumulates in the compression chamber, and the turning radius of the orbiting scroll is repeatedly changed until the liquid comes out of the compression chamber, and the contact and separation between the pin and the end of the arc-shaped groove are repeated. There was an abnormal noise.

  Another predetermined situation is the form of a scroll compressor. That is, the horizontal scroll compressor in which the revolution axis of the orbiting scroll extends in the horizontal direction is more likely to generate the above-mentioned noise than the vertical scroll compressor that extends in the vertical direction.

When the horizontal scroll compressor is stopped, centrifugal force does not work on the orbiting scroll, the pressure in the compression chamber is released, and there is no force to press the orbiting scroll against the fixed scroll. Move away from the scroll. Thereafter, when the scroll compressor is activated, a force that presses against the fixed scroll acts on the orbiting scroll, and the orbiting scroll is pressed against the fixed scroll. At this time, the pin and the end of the arc-shaped groove collided, and the above-described abnormal noise was generated.
On the other hand, the vertical scroll compressor does not separate the orbiting scroll from the fixed scroll because the direction in which gravity acts differs even when the scroll compressor stops. Therefore, compared with a horizontal scroll compressor, the above-described abnormal noise is less likely to occur at startup.

  Still another predetermined situation is a method of driving the scroll compressor. That is, a scroll compressor driven by an electric motor such as an inverter motor is more likely to generate the above-described abnormal noise than a scroll compressor driven by an internal combustion engine such as an automobile engine.

Inverter motors and the like are limited in the value of drive torque that can be generated, depending on the value of the current supplied and the size of the inverter motor. On the other hand, a large driving torque is required to discharge the liquid accumulated in the compression chamber from the compression chamber. If the driving torque generated by the inverter motor or the like is not a sufficient value for discharging the liquid from the compression chamber, the liquid stays in the compression chamber for a relatively long period of time. When the liquid stays in the compression chamber for a long period, the period during which the above-mentioned abnormal noise occurs is also long.
On the other hand, an engine or the like has a larger drive torque value that can be generated than an inverter motor or the like. Therefore, the period required for discharging the liquid from the compression chamber is shortened, and the period during which the above-described abnormal noise is generated is also shortened.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a scroll compressor that can suppress the generation of abnormal noise.

In order to achieve the above object, the present invention provides the following means.
The scroll compressor according to the present invention includes the fixed scroll and the orbiting scroll forming the closed compression chamber, the main shaft rotatably supported around the central axis, and the center at the end of the main shaft facing the orbiting scroll. A drive pin extending along the central axis from a position eccentric from the axis, a boss extending along the central axis from a surface facing the main shaft in the orbiting scroll, and an eccentric where the drive pin is rotatably inserted. A bush is formed and rotatably disposed inside the boss, and one of the main shaft and the bush is eccentric from the central axis and extends from the position different from the drive pin along the central axis. From the position facing the limit pin on the other of the limit pin and the main shaft and the bush The limit pin extends along the central axis so that the limit pin has a diameter larger than that of the limit pin and the limit pin and the limit hole are in contact with the limit pin and the limit hole. And an elastic portion arranged in a manner.

  According to the present invention, the force pressing the orbiting scroll against the fixed scroll (for example, the centrifugal force acting on the orbiting scroll or the reaction force from the compressive fluid compressed in the compression chamber) is not so great as to deform the elastic portion. In some cases (for example, immediately after the scroll compressor is started or stopped), the elastic portion separates the limit pin and the limit hole and holds them in a predetermined relative positional relationship (for example, the limit is placed at the center of the limit hole). Hold the pin).

On the other hand, when the force pressing the orbiting scroll against the fixed scroll is so great that the elastic portion is deformed, the elastic portion is deformed and the limit pin and the limit hole can be brought into contact with each other. Then, the bush is rotated around the drive pin in the direction in which the turning radius of the orbiting scroll is increased, and the orbiting scroll is pressed against the fixed scroll.
When the force that presses the orbiting scroll against the fixed scroll becomes too large (for example, when there is a liquid that is an incompressible fluid in the compression chamber, or when foreign matter is caught between both scrolls) The bush is rotated around the drive pin in a direction in which the turning radius of the orbiting scroll becomes smaller, and the limit pin and the limit hole are separated from each other.

  In the said invention, it is desirable that the said elastic part is formed in the cylindrical shape.

  According to the present invention, the contact area between the elastic part and the limit pin or the contact area between the elastic part and the limit hole can be ensured, so that the elastic part can be easily fixed to the limit pin or the limit hole.

  In the above invention, it is desirable that the elastic part is provided in the limit pin, and the limit pin is provided with a fitting groove into which at least a part of the elastic part is fitted.

  According to the present invention, it is possible to make it difficult for the elastic portion to come off the limit pin by fitting at least a part of the elastic portion into the fitting groove.

  In the above invention, the elastic part is preferably formed in a ring shape having a substantially circular cross section.

  According to the present invention, since the inner peripheral side portion of the elastic portion is fitted into the fitting groove, the elastic portion is unlikely to come off from the limit pin.

  According to the scroll compressor of the present invention, since the elastic part can keep the limit pin and the limit hole apart and hold them in a predetermined relative positional relationship, the noise generated when the limit pin and the limit hole come into contact with each other is prevented. There exists an effect that it can control.

[First Embodiment]
A scroll compressor according to a first embodiment of the present invention will be described below with reference to FIGS.
FIG. 1 is a schematic diagram illustrating the configuration of the scroll compressor according to the present embodiment.
In the present embodiment, a horizontal scroll compressor driven by an inverter motor, which is applied to a scroll compressor that compresses a refrigerant of a vehicle air conditioner, will be described.

  As shown in FIG. 1, the scroll compressor 1 includes a housing 3, a fixed scroll 5 and a orbiting scroll 7 that compress refrigerant used in a vehicle air conditioner, a main shaft 9 that drives the orbiting scroll 7, and a drive bush portion. 11 and an inverter motor 13 are provided.

  The housing 3 is a housing that houses the fixed scroll 5, the orbiting scroll 7, the main shaft 9, the inverter motor 13, and the like. The housing 3 includes a first housing 15, a second housing 17, and a motor case. 19 are provided.

  The first housing 15 is a member formed in a bottomed cylindrical shape, and the fixed scroll 5 is fixed to the bottom surface. A discharge chamber 21 into which the refrigerant compressed by the fixed scroll 5 and the orbiting scroll 7 flows is formed between the fixed scroll 5 and the first housing 15.

The first housing 15 is provided with a discharge portion (not shown) that guides the refrigerant in the discharge chamber 21 to the outside, and a first flange portion 23.
The first flange portion 23 is used when the first housing 15, the second housing 17, and the motor case 19 are integrally fixed using the housing bolt 25, and is an end portion on the opening side of the first housing 15. And a member extending radially outward.

  As shown in FIG. 1, the second housing 17 is a member provided with a side wall portion 27 formed in a cylindrical shape and a flange portion 29 extending radially outward from an end portion on the first housing 15 side. . The second housing 17 is disposed such that the flange portion 29 is sandwiched between the first housing 15 and the motor case 19.

A radial bearing 31 that rotatably supports the main shaft 9 is provided in the side wall portion 27 of the second housing 17, and a suction passage 28 that extends along the central axis of the main shaft 9 is provided in the wall surface of the side wall portion 27. Is provided.
The flange portion 29 of the second housing 17 is provided with a second flange portion 33 that is used when the first housing 15, the second housing 17 and the motor case 19 are fixed together using the housing bolt 25. The second flange portion 33 is a member that extends outward from the flange portion 29 in the radial direction.

  As shown in FIG. 1, the motor case 19 is a member formed in a bottomed cylindrical shape, and a stator 77 of the inverter motor 13 is fixed therein. The motor case 19 is provided with a suction portion (not shown) through which refrigerant flows from the outside, a box 35, and a case flange portion 37.

The box 35 opens toward the outer side in the radial direction of the motor case 19 and accommodates the inverter portion 79 of the inverter motor 13 therein.
The case flange portion 37 is used when the first housing 15, the second housing 17, and the motor case 19 are integrally fixed using the housing bolt 25, and has a radius from the end of the motor case 19 on the opening side. This is a member extending outward in the direction.

As shown in FIG. 1, the fixed scroll 5 and the orbiting scroll 7 form a closed compression chamber C to compress the refrigerant.
The fixed scroll 5 is provided with a fixed end plate 39 and a spiral fixed wall body 41 extending from the fixed end plate 39 toward the orbiting scroll 7. The fixed scroll 5 is fixed to the bottom surface of the first housing 15.
A discharge hole 43 is provided at the center of the fixed end plate 39, and the refrigerant compressed in the compression chamber C is discharged into the discharge chamber 21 through the discharge hole 43.

On the other hand, the orbiting scroll 7 includes an orbiting end plate 45 and a spiral orbiting wall plate 47 extending from the orbiting end plate 45 toward the fixed scroll 5. The orbiting scroll 7 is supported by the main shaft 9 and the rotation preventing portion 49 so as to be able to revolve.
A cylindrical boss portion 51 extending toward the main shaft 9 is provided on a surface of the turning end plate 45 facing the main shaft 9. The boss portion 51 is provided with a turning portion bearing that rotatably supports the bush 63 to which the revolution driving force by the main shaft 9 is transmitted.

FIG. 2 is a schematic diagram illustrating the configuration of the main shaft of FIG. FIG. 3 is a side view for explaining the configuration of the crankpin and limit hole of FIG.
As shown in FIG. 1, the main shaft 9 is a columnar member that extends from the inverter motor 13 toward the orbiting scroll 7. As shown in FIGS. 1 and 2, the main shaft 9 includes a columnar crankshaft 55 fixed to the rotor 75, a disk portion 57 having a diameter larger than that of the crankshaft 55, and a central axis line on the crankshaft 55. A crank pin (drive pin) 59 extending along the central axis from a position eccentric from the center is provided.

The crankshaft 55 has a central axis arranged substantially horizontally, and transmits the rotational driving force generated by the stator 77 and the rotor 75 to the orbiting scroll 7.
The circular plate portion 57 is a portion where the circumferential surface is supported by the radial bearing 31, and is a portion provided with a crank pin 59 and a limit hole 61 into which the limit pin 65 is inserted.

  The crank pin 59 is a columnar member that transmits the rotational driving force transmitted to the crankshaft 55 to the orbiting scroll 7 to drive the orbiting scroll 7 to orbit. As shown in FIGS. 2 and 3, the crank pin 59 extends toward the orbiting scroll 7 along the central axis of the crankshaft 55 from a position eccentric from the center of the disc portion 57 in the disc portion 57. .

The limit hole 61 adjusts the revolution radius of the orbiting scroll 7 together with the limit pin 65. The limit hole 61 is a hole extending toward the crankshaft 55 along the center axis of the crankshaft 55 from another eccentric position different from the crankshaft 55 in the disc portion 57. The diameter of the limit hole 61 is formed larger than the diameter of the limit pin 65.
The limit hole 61 may be formed as a hole as described above, or may be formed as a groove through which the limit pin 65 is inserted, and is not particularly limited.

  As shown in FIG. 3, the relative positional relationship between the crank pin 59 and the limit hole 61 is that the limit hole is obtained when the crank pin 59 is arranged in the 12 o'clock direction when the main shaft 9 is viewed from the crank pin 59 side. The case where 61 is arrange | positioned from 4 o'clock to 5 o'clock can be illustrated.

FIG. 4 is a schematic diagram illustrating the configuration of the drive bush portion of FIG. FIG. 5 is a side view for explaining the configuration of the drive bush portion of FIG. 4.
A drive bush 11 is provided between the main shaft 9 and the orbiting scroll 7 as shown in FIG.
As shown in FIG. 4, the drive bush portion 11 is provided with a bush 63, a limit pin 65, and a counterweight 67.

  The bush 63 is a substantially cylindrical member that is disposed between the crank pin 59 and the boss portion 51 and transmits the revolution driving force to the orbiting scroll 7. A crank hole (eccentric hole) 69 through which the crank pin 59 is inserted is formed in the bush 63 at a position eccentric from the center of the bush 63.

The limit pin 65 is a cylindrical member that is disposed between the bush 63 and the disc portion 57 and adjusts the revolution radius of the orbiting scroll 7 together with the limit hole 61. The limit pin 65 is provided to extend from another eccentric position in the bush 63 different from the crank pin 59 toward the disc portion 57 (to the left side in FIG. 4) along the central axis of the main shaft 9. ing.
A concave fitting groove 71 into which the elastic portion 73 is fitted is formed over the circumferential surface of the limit pin 65 in the vicinity of the end portion on the disc portion 57 side of the limit pin 65.
The limit pin 65 may be formed as a columnar member as described above, or may be formed as a columnar member having another cross-sectional shape, and is not particularly limited.

  The elastic portion 73 is a substantially cylindrical elastic member that is provided in the vicinity of the end portion of the limit pin 65 on the disk portion 57 side and is disposed in contact with the limit pin 65 and the limit hole 61. As a material for forming the elastic portion 73, a rubber that is compatible with a refrigerant used in a vehicle air conditioner and a lubricating oil such as the scroll compressor 1 and that does not swell is desirable. Specifically, HNBR (hydrogenated nitrile rubber) or the like can be exemplified, but a suitable rubber can be used according to the refrigerant or lubricating oil used.

The elastic part 73 is formed so that the diameter of the outer peripheral surface is equal to or larger than the diameter of the limit hole 61 and the diameter of the inner peripheral surface is equal to or smaller than the diameter of the limit pin 65. On the inner peripheral surface of the elastic portion 73, a hook-shaped convex portion that fits into the fitting groove 71 is provided over the inner peripheral surface.
The elastic portion 73 has at least rigidity for supporting the weight of the orbiting scroll 7 and holding the limit pin 65 apart from the limit hole 61 when the orbiting scroll 7 is not orbitally driven. On the other hand, the rigidity of the elastic portion 73 is such that when the orbiting scroll 7 is driven to rotate and a reaction force due to centrifugal force and refrigerant compression is applied, the limit pin 65 and the limit hole 61 are in direct contact with each other. Is suppressed.

  The relative positional relationship between the crank hole 69 and the limit pin 65 is as shown in FIG. In the case where the limit pin 65 is arranged in the 8 o'clock direction.

  The counterweight 67 is a member that adjusts the pressing force of the orbiting scroll 7 against the fixed scroll 5 and balances it. As shown in FIGS. 4 and 5, the counterweight 67 is a bowl-shaped member extending in a semicircular shape from the circumferential surface on the main shaft 9 side of the bush 63 toward the radially outer side. As shown in FIG. 5, the range in which the counterweight 67 extends is a range between the 3 o'clock direction and the 9 o'clock direction when the crank hole 69 is disposed in the 2 o'clock direction. It is offset from the line passing through the center of 63 in the 6 o'clock direction.

FIG. 6 is a schematic diagram for explaining a combination of the main shaft and the drive bush portion of FIG. FIG. 7 is a view of the main shaft and the drive bush portion of FIG. 6 as viewed from the drive bush portion side.
As shown in FIGS. 6 and 7, the main shaft 9 and the drive bush portion 11 are combined such that the crank pin 59 is inserted through the crank hole 69 and the limit pin 65 is inserted through the limit hole 61. The elastic part 73 of the limit pin 65 is inserted into the limit hole 61 together with the limit pin 65 and is in contact with the inner peripheral surface of the limit hole 61.
Since they are combined in this way, the drive bushing 11 is rotatable within a range regulated by the limit pin 65 and the limit hole 61 with the crank pin 59 as the rotation center.

The inverter motor 13 is a motor that is rotationally driven by a frequency-controlled alternating current, and is an electric part that drives the orbiting scroll 7 to revolve.
As shown in FIG. 1, the inverter motor 13 includes a rotor 75 and a stator 77 that revolve the revolving scroll 7 through the main shaft 9 and the drive bush portion 11, and an inverter unit 79 that controls an alternating current supplied to the stator 77. And are provided.

The rotor 75 generates a rotational driving force by an alternating magnetic field formed by the stator 77, and is a permanent magnet formed in a cylindrical shape. A crankshaft 55 of the main shaft 9 is fixed to the rotor 75.
The stator 77 forms an alternating magnetic field based on the alternating current supplied from the inverter unit 79 and rotates the rotor 75. The stator 77 is fixed to the inner peripheral surface of the motor case 19 using a fixing method such as shrink fitting.

  The inverter unit 79 controls an alternating current supplied to the stator 77 and is disposed in the box 35. The inverter unit 79 is provided with a capacitor 81, a plurality of substrates 85 including electronic elements such as a power transistor 83, and terminals 87.

The capacitor 81 temporarily stores current. Electronic elements such as the power transistor 83 provided on the substrate 85 control the frequency of the alternating current supplied from the outside. The terminal 87 supplies an alternating current to the stator 77.
The substrate 85 provided with the power transistor 83 is fixed in contact with the motor case 19 in the box 35, and is configured to release heat generated from the power transistor 83 to the motor case 19. Other substrates 85 are fixed at positions away from the motor case 19. In other words, the substrate 85 is fixed in a stacked state.
The terminal 87 supplies an alternating current controlled by the power transistor 83 or the like to the stator 77.

  As described above, the inverter motor 13 may be used as the electric part, and other known motors may be used as the electric part, and there is no particular limitation.

Next, refrigerant compression in the scroll compressor 1 having the above configuration will be described.
As shown in FIG. 1, the frequency of the direct current supplied from the outside of the inverter is controlled by an electronic element such as the power transistor 83 of the inverter unit 79 and supplied to the stator 77.
The stator 77 forms an alternating magnetic field based on the alternating current whose frequency is controlled, and the rotor 75 generates a rotational driving force by interaction with the formed alternating magnetic field. The rotational driving force generated by the rotor 75 is transmitted to the main shaft 9.

  The rotational driving force is transmitted to the crankshaft 55 and the disc portion 57 of the main shaft 9, and the crankpin 59 is driven to rotate by the rotation of the disc portion 57. The orbiting motion of the crankpin 59 is transmitted to the orbiting scroll 7 through the bush 63 and the boss portion 51. The orbiting scroll 7 is driven to revolve in a state in which the rotation motion is restricted by the rotation prevention unit 49.

When the orbiting scroll 7 is driven to revolve, the compression chamber C formed between the fixed scroll 5 takes in the refrigerant flowing into the scroll compressor 1 from the motor case 19 and compresses it. Specifically, the compression chamber C takes in the refrigerant at the outer peripheral ends of the fixed scroll 5 and the orbiting scroll 7. As the revolving scroll 7 revolves, the compression chamber C decreases in volume as it moves from the outer peripheral end toward the center along the fixed wall body 41 and the revolving wall plate 47, and compresses the taken-in refrigerant.
The refrigerant compressed in the compression chamber C is discharged to the discharge chamber 21 through the discharge hole 43 of the fixed scroll 5, and is discharged from the discharge chamber 21 to the outside of the first housing 15.

On the orbiting scroll 7, the centrifugal force caused by the revolution orbit and the compression reaction force of the refrigerant compressed by the compression chamber C act in the direction of expanding the revolution orbit radius. With these forces, the orbiting scroll 7 and the drive bushing 11 rotate about the crankpin 59 to increase the revolution orbit radius.
When the orbiting scroll 7 and the drive bushing 11 rotate, the crank pin 59 and the crank hole 69 come close to each other and come into contact with each other while crushing the elastic part 73. The crank pin 59 and the crank hole 69 are in contact with each other, thereby restricting the rotation range of the orbiting scroll 7 and the drive bushing 11 around the crank pin 59.
Note that the centrifugal force and the compression reaction force acting on the orbiting scroll 7 are large enough to crush the elastic portion 73, and can include, for example, the magnitude of a force of about several thousand N.

  For example, when a liquid refrigerant (hereinafter referred to as a liquid refrigerant) exists in the compression chamber C, or when a foreign object is caught between the orbiting scroll 7 and the fixed scroll 5, the orbiting scroll 7. Has a smaller turning radius and forms a passage for liquid refrigerant and foreign matter. In other words, the orbiting scroll 7 and the drive bushing 11 have the revolution turning radius around the crank pin 59 by the liquid compression reaction force generated when the liquid refrigerant is compressed and the resistance force generated when the foreign matter is bitten. Rotate in the direction to make it smaller. By this rotation, an escape passage is formed between the orbiting scroll 7 and the fixed scroll 5.

Next, suppression of the generation of rattling noise, which is a feature of the present embodiment, will be described.
When the operation of the scroll compressor 1 is stopped and the revolution of the orbiting scroll 7 stops, the centrifugal force and the compression reaction force acting on the orbiting scroll 7 disappear, and the force for increasing the revolution radius of the orbiting scroll 7 disappears. The orbiting scroll 7 is rotated about the crank pin 59 by gravity acting downward in the vertical direction, and the limit pin 65 and the limit hole 61 are separated from each other. The elastic part 73 crushed between the limit pin 65 and the limit hole 61 due to centrifugal force or the like also separates the limit pin 65 and the limit hole 61 by a force returning from the crushed shape to the original shape.

Further, the elastic portion 73 holds the limit pin 65 in a state of being separated from the limit hole 61. The elastic part 73 has a force that crushes the elastic part 73 due to the gravity acting on the orbiting scroll 7 and the drive bushing part 11, but its magnitude is about several N, compared with centrifugal force and compression reaction force Since the elastic portion 73 is small, the limit pin 65 can be held away from the limit hole 61.
Therefore, when the operation of the scroll compressor 1 is stopped, the rattling noise generated by the contact between the limit pin 65 and the limit hole 61 is suppressed.

Further, when liquid refrigerant is present in the compression chamber C, the revolution radius of the orbiting scroll 7 becomes small as described above. That is, the limit pin 65 and the limit hole 61 are separated from each other, and the revolution radius of the orbiting scroll 7 is reduced.
At this time, when the limit pin 65 is separated from a predetermined region on the inner peripheral surface of the limit hole 61 and contacts (collises) with the opposite region, the shape of the elastic portion 73 is deformed and the limit pin 65 and the limit pin 65 are limited. The momentum at the time of contact with the hole 61 is reduced. Therefore, the rattling sound generated when the limit pin 65 and the limit hole 61 come into contact with each other when the liquid refrigerant is present in the compression chamber C is suppressed.

  The elastic part 73 similarly suppresses the rattling sound when the revolution turning radius of the turning scroll 7 is not stable or when a foreign object is caught between the turning scroll 7 and the fixed scroll 5.

  According to the above configuration, when the force that presses the orbiting scroll 7 against the fixed scroll 5 (for example, centrifugal force or compression reaction force acting on the orbiting scroll 7) is not so large as to deform the elastic portion 73, for example, the scroll When the compressor is started or stopped, the elastic portion 73 separates the limit pin 65 and the limit hole 61 and holds the limit pin 65 in the center of the limit hole 61. Therefore, the rattling sound generated when the limit pin 65 and the limit hole 61 come into contact with each other can be suppressed.

By forming the elastic portion 73 in a substantially cylindrical shape, a contact area between the elastic portion 73 and the limit pin 65 can be secured, and the elastic portion 73 can be easily fixed to the limit pin 65. Specifically, it is possible to secure an area for providing a hook-shaped convex portion that fits into the fitting groove 71 of the limit pin 65, and the elastic portion 73 can be easily fixed to the limit pin 65.
By fitting the hook-shaped convex part of the elastic part 73 into the fitting groove 71 provided in the limit pin 65, the elastic part 73 can be made difficult to come off from the limit pin 65.

[First Modification of First Embodiment]
Next, a scroll compressor according to a first modification of the first embodiment of the present invention will be described with reference to FIG.
The basic configuration of the scroll compressor of the present modification is the same as that of the first embodiment, but the configuration of limit pins and elastic portions is different from that of the first embodiment. Therefore, in this modification, only the peripheral configuration of the limit pin and the elastic portion will be described with reference to FIG. 8, and description of other components and the like will be omitted.
FIG. 8 is a schematic diagram for explaining the peripheral configuration of the limit pin and the elastic portion according to the scroll compressor of the present modification.
In addition, about the component same as 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 8, the drive bush portion 11 of the scroll compressor 1 is provided with a bush 63, a limit pin 65 </ b> A, an elastic portion 73 </ b> A, and a counterweight 67.
The limit pin 65 </ b> A is a cylindrical member that is disposed between the bush 63 and the disc portion 57 and adjusts the revolution radius of the orbiting scroll 7 together with the limit hole 61. The limit pin 65A is provided to extend from another eccentric position in the bush 63 different from the crank pin 59 toward the disc portion 57 (to the left side in FIG. 8) along the central axis of the main shaft 9. ing.

  In the vicinity of the end of the limit pin 65A on the disc portion 57 side, a concave fitting groove 71A into which the inner peripheral portion of the elastic portion 73A is fitted is formed over the circumferential surface of the limit pin 65A. The fitting groove 71A has a depth shorter than the diameter of the cross section of the elastic portion 73A, and is formed to have a length approximately equal to the diameter of the cross section even if the width is wide.

The elastic portion 73A is an elastic member that is provided in the vicinity of the end of the limit pin 65A on the disc portion 57 side and is in contact with the limit pin 65A and the limit hole 61. The elastic portion 73A is a so-called O-ring having a substantially circular cross section formed in a ring shape.
As a material for forming the elastic portion 73A, similarly to the first embodiment, a refrigerant that is used in a vehicle air conditioner and a rubber that is compatible with lubricating oil such as the scroll compressor 1 and that does not swell is used. desirable. Specifically, HNBR (hydrogenated nitrile rubber) or the like can be exemplified, but a suitable rubber can be used according to the refrigerant or lubricating oil used.

The elastic portion 73A has an outermost diameter that is greater than or equal to the diameter of the limit hole 61, and an outermost inner diameter that is at least smaller than the diameter of the limit pin 65A.
The elastic portion 73A has at least rigidity for supporting the weight of the orbiting scroll 7 and holding the limit pin 65A away from the limit hole 61 when the orbiting scroll 7 is not driven to rotate. On the other hand, the rigidity of the elastic portion 73A is such that when the orbiting scroll 7 is driven to rotate and a reaction force due to centrifugal force and refrigerant compression is applied, the limit pin 65A and the limit hole 61 are in direct contact with each other. Is suppressed.

  Since the relative positional relationship between the limit pin 65A and the crank hole 69 is the same as that in the first embodiment, the description thereof is omitted.

  Since the operation relating to the compression of the refrigerant and the suppression of the generation of rattling noise in the scroll compressor 1 having the above-described configuration is the same as that of the first embodiment, the description thereof is omitted.

According to said structure, since the part of the inner peripheral side in 73 A of elastic parts is engage | inserted by the fitting groove 71A, the elastic part 73A becomes difficult to remove | deviate from 65 A of limit pins.
Since the elastic portion 73A is a so-called O-ring and does not have a special shape like the elastic portion 73 of the first embodiment, it is easy to form the elastic portion 73A. Or a commercial item can be used as 73A of elastic parts.

[Second Modification of First Embodiment]
Next, a scroll compressor according to a second modification of the first embodiment of the present invention will be described with reference to FIGS.
The basic configuration of the scroll compressor of the present modification is the same as that of the first embodiment, but the configuration of limit pins and elastic portions is different from that of the first embodiment. Therefore, in this modification, only the peripheral configuration of the limit pin and the elastic portion will be described with reference to FIGS. 9 to 11, and description of other components and the like will be omitted.
FIG. 9 is a schematic diagram illustrating the configuration of the drive bush portion according to the scroll compressor of the present modification. FIG. 10 is a diagram for explaining a combination of the drive bush portion and the main shaft in FIG. 9.
In addition, about the component same as 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 9, the drive bush portion 11 of the scroll compressor 1 is provided with a bush 63, a limit pin 65B, an elastic portion 73B, and a counterweight 67.
The limit pin 65 </ b> B is a cylindrical member that is disposed between the bush 63 and the disc portion 57 and adjusts the revolution radius of the orbiting scroll 7 together with the limit hole 61. The limit pin 65B is provided to extend from another eccentric position in the bush 63 different from the crank pin 59 toward the disc portion 57 (to the left side in FIG. 9) along the central axis of the main shaft 9. ing.

The elastic portion 73B is an elastic member that is provided in the vicinity of the end portion of the limit pin 65B on the disk portion 57 side, and is disposed in contact with the limit pin 65B and the limit hole 61 as shown in FIGS. is there. The elastic part 73B is an elastic member formed in a substantially cylindrical shape.
As a material for forming the elastic portion 73B, similarly to the first embodiment, there is a rubber that is compatible with a refrigerant used in a vehicle air conditioner or a lubricant such as the scroll compressor 1 and that does not swell. desirable. Specifically, HNBR (hydrogenated nitrile rubber) or the like can be exemplified, but a suitable rubber can be used according to the refrigerant or lubricating oil used.

The elastic part 73B is formed so that the diameter of the outer peripheral surface is equal to or larger than the diameter of the limit hole 61, and the diameter of the inner peripheral surface is equal to or smaller than the diameter of the limit pin 65B.
The elastic portion 73 </ b> B has at least a rigidity that supports the weight of the orbiting scroll 7 and holds the limit pin 65 </ b> B apart from the limit hole 61 when the orbiting scroll 7 is not orbitally driven. On the other hand, the rigidity of the elastic portion 73B is such that the limit pin 65B and the limit hole 61 are in direct contact with each other when the orbiting scroll 7 is driven to rotate and the reaction force due to centrifugal force and refrigerant compression is applied. Is suppressed.

  Since the relative positional relationship between the limit pin 65B and the crank hole 69 is the same as that in the first embodiment, the description thereof is omitted.

  Since the operation relating to the compression of the refrigerant and the suppression of the generation of rattling noise in the scroll compressor 1 having the above-described configuration is the same as that of the first embodiment, the description thereof is omitted.

According to said structure, by making the elastic part 73B substantially cylindrical shape, the contact area of the elastic part 73B and the limit pin 65B can be ensured, and fixation of the elastic part 73B to the limit pin 65B is easy. Become.
Since the shape of the elastic portion 73B does not have a special shape like the elastic portion 73 of the first embodiment, the elastic portion 73B can be easily formed.
Since the elastic portion 73B is attached to the limit pin 65B, the elastic portion 73B can be easily attached as compared with the method of attaching the elastic portion 73B to the limit hole 61B.

FIG. 11 is a schematic diagram for explaining another configuration of the drive bush portion of FIG. 9.
As in the above-described modification, the elastic portion 73B may be formed in a substantially cylindrical member and disposed on the limit pin 65B. As shown in FIG. 11, the bottomed cylindrical elastic portion 73C May be arranged on the limit pin 65C, and is not particularly limited.

[Second Embodiment]
Next, a scroll compressor according to a second embodiment of the present invention will be described with reference to FIGS.
The basic configuration of the scroll compressor of this embodiment is the same as that of the first embodiment, but the configurations of limit pins, limit holes, and elastic portions are different from those of the first embodiment. Therefore, in the present embodiment, only the peripheral configuration of the limit pin, the limit hole, and the elastic portion will be described using FIGS. 12 to 15, and description of other components will be omitted.
FIG. 12 is a schematic diagram illustrating a configuration of a drive bush portion according to the scroll compressor of the present embodiment. FIG. 13 is a partially enlarged view illustrating the configuration of the main shaft according to the scroll compressor of the present embodiment.
In addition, about the component same as 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 12, the drive bush portion 11 of the scroll compressor 1 is provided with a bush 63, a limit pin 65 </ b> D, and a counterweight 67.
On the other hand, as shown in FIG. 13, the main shaft 9 of the scroll compressor 1 is provided with a crankshaft 55, a disc portion 57, a crankpin 59, a limit hole 61D, and an elastic portion 73D. .

  As shown in FIG. 12, the limit pin 65D is a cylindrical member that is disposed between the bush 63 and the disc portion 57 and adjusts the revolution radius of the orbiting scroll 7 together with the limit hole 61D. The limit pin 65D is provided to extend from another eccentric position on the bush 63 different from the crank pin 59 toward the disc portion 57 (to the left side in FIG. 12) along the central axis of the main shaft 9. ing.

  Since the relative positional relationship between the limit pin 65D and the crank hole 69 is the same as that in the first embodiment, the description thereof is omitted.

  The limit hole 61D adjusts the revolution radius of the orbiting scroll 7 together with the limit pin 65D. The limit hole 61D is a hole extending toward the crankshaft 55 along the central axis of the crankshaft 55 from another eccentric position different from the crankshaft 55 in the disc portion 57. The diameter of the limit hole 61D is formed larger than the diameter of the limit pin 65D.

FIG. 14 is a view for explaining a combination of the drive bush portion and the main shaft in FIGS. 12 and 13.
The elastic portion 73D is an elastic member that is provided on the inner peripheral surface of the limit hole 61D and is disposed in contact with the limit pin 65D and the limit hole 61D. The elastic portion 73D is an elastic member formed in a substantially cylindrical shape.
As a material for forming the elastic portion 73D, similarly to the first embodiment, there is a rubber that is compatible with a refrigerant used in a vehicle air conditioner or a lubricant such as the scroll compressor 1 and that does not swell. desirable. Specifically, HNBR (hydrogenated nitrile rubber) or the like can be exemplified, but a suitable rubber can be used according to the refrigerant or lubricating oil used.

The elastic part 73D is formed so that the diameter of the outer peripheral surface is about the diameter of the limit hole 61D, and the diameter of the inner peripheral surface is equal to or smaller than the diameter of the limit pin 65D.
The elastic portion 73D has at least rigidity to support the weight of the orbiting scroll 7 and hold the limit pin 65D away from the limit hole 61D when the orbiting scroll 7 is not driven to be orbited. On the other hand, the rigidity of the elastic portion 73D is such that the limit pin 65D and the limit hole 61D are in direct contact with each other when the orbiting scroll 7 is driven to rotate and a reaction force due to centrifugal force and refrigerant compression is applied. Is suppressed.

  Since the operation relating to the compression of the refrigerant and the suppression of the generation of rattling noise in the scroll compressor 1 having the above-described configuration is the same as that of the first embodiment, the description thereof is omitted.

According to said structure, by making elastic part 73D into a substantially cylindrical shape, the contact area of elastic part 73D and limit hole 61D can be ensured, and fixation of elastic part 73D to limit hole 61D is easy. Become.
Since the shape of the elastic portion 73D does not have a special shape like the elastic portion 73 of the first embodiment, the elastic portion 73D can be easily formed.

  Compared to the method of attaching the elastic portion 73D to the limit pin 65D in order to attach the elastic portion 73D to the limit hole 61D, the arrangement position of the elastic portion 73D is less likely to shift when the limit pin 65D is inserted into the limit hole 61D. Becomes easy.

FIG. 15 is a schematic diagram for explaining another modification of the limit pin, the limit hole, and the elastic portion in FIG.
As in the above-described modification, the elastic portion 73D may be formed in a substantially cylindrical member and disposed inside the limit hole 61D, or as shown in FIG. The portion 73E may be disposed inside the limit hole 61E, and is not particularly limited.

The technical scope of the present invention is not limited to the above embodiment, and various modifications can be made without departing from the spirit of the present invention.
For example, in the above embodiment, the present invention is applied to a scroll compressor used in a vehicle air conditioner. However, the present invention is limited to a scroll compressor used in a vehicle air conditioner. It can be applied to other various scroll compressors.

It is the schematic explaining a structure to the scroll compressor which concerns on the 1st Embodiment of this invention. It is the schematic explaining the structure of the main axis | shaft of FIG. It is a side view explaining the structure of the crankpin and limit hole of FIG. It is the schematic explaining the structure of the drive bush part of FIG. It is a side view explaining the structure of the drive bush part of FIG. It is the schematic explaining the combination of the main axis | shaft of FIG. 1, and a drive bush part. It is the figure which looked at the main axis | shaft and drive bush part of FIG. 6 from the drive bush part side. It is a mimetic diagram explaining peripheral composition of a limit pin concerning a scroll compressor of the 1st example of a 1st embodiment of the present invention, and an elastic part. It is a schematic diagram explaining the structure of the drive bush part concerning the scroll compressor of the 2nd modification of the 1st Embodiment of this invention. It is a figure explaining the combination of the drive bush part of FIG. 9, and a main axis | shaft. It is a schematic diagram explaining the other structure of the drive bush part of FIG. It is a schematic diagram explaining the structure of the drive bush part concerning the scroll compressor of the 2nd Embodiment of this invention. It is a schematic diagram explaining the structure of the main axis | shaft concerning the scroll compressor of the 2nd Embodiment of this invention. It is a figure explaining the combination of the drive bush part of FIG. 12 and FIG. 13, and a main axis | shaft. It is a schematic diagram explaining the other modification of the limit pin of FIG. 12, a limit hole, and an elastic part.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Scroll compressor 5 Fixed scroll 7 Orbiting scroll 9 Main shaft 11 Drive bush part 59 Crank pin (drive pin)
61, 61D, 61E Limit hole 63 Bushing 65, 65A, 65B, 65C, 65D Limit pin 69 Crank hole (eccentric hole)
71, 71A Fitting groove 73, 73A, 73B, 73C, 73D, 73E Elastic part

Claims (4)

A fixed scroll and an orbiting scroll forming a closed compression chamber;
A main shaft supported rotatably around a central axis,
A drive pin extending along the central axis from a position eccentric from the central axis at an end of the main shaft facing the orbiting scroll;
A boss extending along the central axis from a surface facing the main shaft in the orbiting scroll;
An eccentric hole through which the drive pin is rotatably inserted is formed, and a bush disposed rotatably inside the boss;
In one of the main shaft and the bush, a limit pin that is eccentric from the central axis and extends along the central axis from a position different from the drive pin;
In the other of the main shaft and the bush, the limit pin extends from the position facing the limit pin so that the limit pin is inserted along the central axis, and the limit hole has a larger diameter than the limit pin,
Between the limit pin and the limit hole, an elastic part arranged in contact with the limit pin and the limit hole,
The scroll compressor characterized by being provided.   The scroll compressor according to claim 1, wherein the elastic portion is formed in a cylindrical shape. The elastic portion is provided on the limit pin,
The scroll compressor according to claim 1, wherein the limit pin is provided with a fitting groove into which at least a part of the elastic portion is fitted.   4. The scroll compressor according to claim 3, wherein the elastic portion is formed in a ring shape having a substantially circular cross section.

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