JPH10220369A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a scroll compressor with high reliability which can prevent damage of a main bearing such as abrasion or seizure even when a cylindrical bush is going to be moved to a rotary scroll side. SOLUTION: A scroll compressor has a closed vessel 10 in which lubricating oil 13 is stored at the bottom part thereof. A fixed scroll 1 and a rotary scroll 2 are arranged on an upper side within the closed vessel 10. The scroll compressor also has a crank shaft 3, a main frame 6 for pivoting the crank shaft 3, a sub-frame 9, and motor rotor 8 arranged on the crank shaft 3. An upper balance weight 14 and a lower balance weight 15 arranged on the motor rotor 8. A strip portion 32 is formed around an outer periphery of a main shaft part 3b of the crank shaft 3. A cylindrical bush 33 is fitted to the main shaft part 3b. An oil hole 3d and an oil supply hole 3e are formed on the crank shaft 3. A stepped portion 33b is formed near an end of the inner periphery of a cylindrical bush 33A on the side of the motor rotor 8.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor, and more particularly, to a scroll compressor used in a refrigerant circuit of a refrigeration system, an air conditioner, or the like.

[0002]

2. Description of the Related Art For example, a conventional scroll compressor disclosed in Japanese Patent Laying-Open No. 4-358784 is configured as shown in FIG. In FIG. 11, reference numeral 1 denotes a fixed scroll arranged at an upper part in a closed container 10, 2 denotes a orbiting scroll which forms a compression chamber by combining the spiral scroll with the fixed scroll 1, and 3 denotes an upper end extending vertically. A crankshaft slidably connected to the orbiting scroll 2 at a portion to apply a rotational force to the orbiting scroll 2, 4 is a drive bush rotatably mounted on a bearing 2 a formed on the orbiting scroll 2, 5 is an Oldham ring Reference numeral 6 denotes a main frame for supporting the orbiting scroll 2 so as to be capable of orbital sliding and a main shaft portion 3b on the upper part of the crankshaft 3 to be rotatable, 6a being a main bearing formed on the main frame 6, and 9 being a crankshaft 3. , A sub-frame rotatably supported by a sub-bearing 9 a at a lower portion of the sub-frame 9, a motor stator 7, and a crank shaft 3 between the main frame 6 and the sub-frame 9. Motor rotor, 11 is a suction pipe for introducing refrigerant from the outside, 12 is a discharge pipe for discharging compressed refrigerant to the outside, 13 is lubricating oil stored at the bottom of the sealed container 10, and 32 is a main shaft of the crankshaft 3. A drum-shaped band-shaped portion provided on 3b and having a central portion protruding over the entire circumference, 33 is a band-shaped portion facing the outer peripheral surface of the main shaft portion 3b.
2 shows a cylindrical bush fitted near the outer periphery and a small gap. An eccentric shaft portion 3a is formed at an upper end portion of the crankshaft 3, and the eccentric shaft portion 3a is fitted into a bearing portion 2a formed on the lower surface of the base plate of the orbiting scroll 2 with a drive bush 4 interposed therebetween. . The upper main shaft portion 3b of the crankshaft 3 is supported by the main bearing 6a of the main frame 6 via the cylindrical bush 33, and the lower sub shaft portion 3c is supported by the sub bearing 9a of the sub frame 9. ing. Reference numerals 14 and 15 denote upper balance weights and lower balance weights attached to the upper and lower sides of the motor rotor 8, respectively. The centrifugal force generated by the orbiting motion of the orbiting scroll 2 and the balance force are provided on the upper and lower sides of the motor rotor 8. It is for taking.

Next, the operation of the conventional scroll compressor shown in FIG. 11 will be described. The rotational force of the motor is
The power is transmitted by the crankshaft 3 fixed to the motor rotor 8 by shrink fitting, and transmitted to the orbiting scroll 2 via the eccentric shaft 3a and the drive bush 4. Orbiting scroll 2
The Oldham ring 5, which is a rotation preventing mechanism, performs a revolving motion that moves in a circular orbit, and compresses the refrigerant according to a change in the volume of a compression chamber formed between the scroll and the fixed scroll 1. In this case, the refrigerant flows into the closed vessel 10 from the external refrigeration cycle through the suction pipe 11, is compressed in the compression chamber to a high pressure, and flows out of the discharge pipe 12 to the external refrigeration cycle.

The thrust force in the compression load of the refrigerant acting on the orbiting scroll 2 is supported by the thrust bearing surface 6 b of the main frame 6. The radial component of the compression load of the refrigerant acting on the orbiting scroll 2 and the centrifugal force such as the balance weight are supported by the main bearing 6a, the sub-bearing 9a, and the like via the crankshaft 3. Deforms minutely. Cylindrical bush 3
Numeral 3 is rotatably fitted in the main bearing 6a of the main frame 6, and the central portion thereof is in contact with the curved surface portion of the band-shaped portion 32 formed in a drum shape which is convex over the entire circumference, so that the crank is provided. Axis 3
Is slightly deformed, the cylindrical bush 33 and the main bearing 6a are kept parallel regardless of operating conditions.

[0005] The lubricating oil 13 stored in the bottom of the sealed container 10 is sent by an oil pump 16 to sliding parts such as bearings and compression chambers. In particular, around the cylindrical bush 33,
The lubricating oil that has exited from a lubrication hole 3e formed in the main shaft portion 3b of the crankshaft 3 along the radial direction flows through the following three lubrication routes. That is, (1) an oil supply path to be supplied to the main bearing 6a through an oil supply hole 33a of the cylindrical bush 33, and (2) a portion of the cylindrical bush 33 passing through the gap between the main shaft portion 3b and the cylindrical bush 33 on the motor rotor 8 side. (3) a lubrication path returning to the lubricating oil 13 at the bottom through the end face, (3) a thrust bearing surface 6b passing through an end face of the cylindrical bush 33 on the orbiting scroll 2 side through a gap between the main shaft 3b and the cylindrical bush 33.
Is a refueling path supplied to the vehicle. Normally, the oil supply port 3e in the main shaft portion 3b of the crankshaft 3 and the oil supply hole 33a of the cylindrical bush 33 are at the same height position in the axial direction.

[0006]

By the way, the conventional scroll compressor is configured such that the main bearing 6a of the main frame 6 supports the main shaft portion 3b of the crankshaft 3 via the cylindrical bush 33. However, the positioning of the cylindrical bush 33 in the axial direction is not clarified. As described above, there are three oil supply paths for the cylindrical bush 33, of which two are related to the axial direction: the circuit on the motor rotor 8 side and the path on the orbiting scroll 2 side.

However, when the scroll compressor is started, the hydraulic pressure is reduced due to the structure of the oil supply path.
The side path is larger than the orbiting scroll 2 side path. In this case, the cylindrical bush 33 rises toward the orbiting scroll 2 due to the balance of the forces acting in the axial direction, so that the inward surface of the main bearing 6a and the cylindrical bush 33 are lifted.
The center position of the contact surface with the outward surface of the main shaft 3b of the crankshaft 3 and the center position of the contact surface with the inward surface of the cylindrical bush 33 should normally match. Move to the orbiting scroll 2 side. During the steady operation of the scroll compressor, the oil pressure in the oil supply path passing through the end face of the cylindrical bush 33 on the side of the orbiting scroll 2 and the oil pressure in the oil supply path passing through the end face on the side of the motor rotor 8 become substantially equal, and the cylindrical bush 33 is turned. The cause of the movement to the two sides is not the difference between the two refueling paths. However, once the cylindrical bush 33 moves to the orbiting scroll 2 side, the cylindrical bush 33
Since the point of application of the radial load acting on the orbit is shifted, the cylindrical bush 33 is held in a state of moving to the orbiting scroll 2 side.

Further, since the scroll compressor used in the refrigerant circuit frequently starts and stops, a situation in which the cylindrical bush 33 moves to the orbiting scroll 2 is likely to occur. In addition, once the cylindrical bush 33 moves to the orbiting scroll 2 side, it does not return to its original position, so that the bearing length of the main shaft is reduced.
b and the lubrication hole 33 of the cylindrical bush 33
As a result, the amount of oil supplied to the main bearing 6a is reduced due to the deviation from a, so that the load capacity of the main bearing 6a is reduced, and there is a problem that the main bearing 6a is worn or seized.

The present invention has been made in view of the above-mentioned conventional problems, and even if a situation occurs in which the cylindrical bush is moved to the orbiting scroll side, damage such as wear and seizure of the main bearing occurs. It is an object of the present invention to provide a highly reliable scroll compressor that can prevent the occurrence of a scroll.

[0010]

In order to achieve the above-mentioned object, a scroll compressor according to the first aspect of the present invention comprises a closed container storing lubricating oil at a bottom portion and a closed container disposed at an upper portion in the closed container. A fixed scroll and an orbiting scroll that form a compression chamber by combining spiral projections; a crankshaft that extends vertically and is slidably connected to the orbiting scroll at the upper end and applies rotational force to the orbiting scroll; A main frame that pivotally supports the main shaft portion above the crankshaft and a sub-frame that rotatably supports the lower portion of the crankshaft, and a sub-frame between the main frame and the sub-frame. To balance the motor rotor provided on the crankshaft and the centrifugal force generated by the orbiting motion of the orbiting scroll provided on the upper and lower sides of the motor rotor. The upper and lower balance weights are formed in a drum-like shape in which the upper and lower central portions are convex over the entire circumference on the outer periphery of the main shaft portion so as to prevent occurrence of one-sided contact at the main shaft portion due to bending deformation of the crankshaft. And a cylindrical bush that faces the outer peripheral surface of the main shaft portion and is fitted around the outer periphery of the belt-shaped portion with a small gap, and through an oil passage hole formed through the crankshaft in the axial direction. A scroll compressor in which oil is supplied to a main shaft portion via a cylindrical bush is provided with a movement restricting means for restricting upward movement of the cylindrical bush in the axial direction at the start of refueling.

According to a second aspect of the present invention, there is provided a scroll compressor according to the first aspect, wherein a radial oil hole communicating with the oil hole is provided in the main shaft portion of the crankshaft. While being pierced, the movement restricting means makes the area of the bottom surface of the cylindrical bush smaller than the upper surface,
This is a configuration in which the inner peripheral surface shape of the cylindrical bush is set.

The scroll compressor according to a third aspect of the present invention is the scroll compressor according to the first aspect, wherein a radial oil supply hole communicating with the oil supply hole is provided in the main shaft portion of the crankshaft. The movement restricting means is provided such that the oil supply path between the outer peripheral surface of the main shaft portion and the inner peripheral surface of the cylindrical bush below the opening position of the oil supply hole is refueled. This is a configuration that is arranged at an axial center position that is wider than the oil supply path above the hole opening position.

A scroll compressor according to a fourth aspect of the present invention is the scroll compressor according to the first aspect, wherein the movement restricting means is provided at a position above the cylindrical bush, and the cylinder for refueling is provided. It is a regulating member that regulates upward movement of the cylindrical bush by interfering with the cylindrical bush.

A scroll compressor according to a fifth aspect of the present invention is the scroll compressor according to the fourth aspect, wherein an elastic material is interposed between the cylindrical bush and the regulating member. is there.

[0015]

Embodiments of the present invention will be described below with reference to the drawings. However, in each embodiment,
Portions that are the same as or correspond to those in the related art are given the same reference numerals, and descriptions thereof are omitted. Embodiment 1 of the Invention FIG. 1 shows an embodiment of the scroll compressor according to claims 1 and 2, and FIG. 2 shows the periphery of the main bearing 6a. In each figure,
33A is a cylindrical bush according to this embodiment,
The shape of the inner peripheral surface in the vicinity of the end near the motor rotor 8 is a stepped portion 33b over the entire circumference, partly, or several places in the circumferential direction.
Is set to the shape. Reference numeral 3d denotes an oil passage hole of the crankshaft 3, which penetrates in the axial direction. 3e is the crankshaft 3
The oil hole is formed in the main shaft portion 3b in the radial direction and communicates with the oil passage hole 3d of the main shaft portion 3b. There are three oil supply paths for the cylindrical bush 33A. Of these, those related to the axial direction are the motor rotor side path below the oil supply hole 3e opening position indicated by 39 and the orbiting scroll side path above the oil supply hole 3e opening position indicated by 40. Reference numeral 41 denotes a minimum flow path cross section of the motor rotor side path 39, which is a portion having the largest hydraulic pressure in the motor rotor side path 39.

Next, the operation of the scroll compressor according to the first embodiment will be described. When the scroll compressor is started, the power generated by the electric motor stator 7 and the electric motor rotor 8 activates the oil pump 16 via the crankshaft 3, and the lubricating oil 13 at the bottom of the sealed container 10 is first passed through the crankshaft 3. The space of the hole 3d and the oil supply hole 3e is filled. Next, the cylindrical bush 3
The lubricating oil 13 is provided in two oil supply paths related to the axial direction of 3A.
, The filling is completed in the order of the motor rotor side path 39 having a small space to be filled, and then the orbiting scroll side path 40. Then, when the filling of the lubricating oil 13 into each oil supply path is completed, the lubricating oil 13 starts flowing toward the front of each oil supply path. In this case, the force balance in the axial direction is not balanced between the time when the filling of the motor rotor-side path 39 is completed and the time when the filling of the orbiting scroll-side path 40 is next completed, and the cylindrical bush 33A.
, An upward force in the axial direction acting to move the orbiting scroll 2 is applied.

However, the cylindrical bush 33A has a step 3
3b, the pressure receiving area at the minimum flow passage cross-sectional portion 41 is small, so that the acting force is small as compared with the case without the step portion 33b. In addition, since the step portion 33b is provided, the motor rotor-side path 39 is inevitably wider than the orbiting scroll-side path 40, so that the time required to complete the filling of the motor rotor-side path 39 increases. That is, since the time until the filling of the orbiting scroll side path 40 is not changed, the time for causing the imbalance of the force applied in the axial direction is reduced. As described above, it is difficult for the cylindrical bush 33A to move toward the orbiting scroll 2 when the scroll compressor is started. If the cylindrical bush 33A does not move toward the orbiting scroll 2 when the scroll compressor is started, it is unlikely that the cylindrical bush 33A moves during the steady operation. That is, the configuration in which the area of the end surface (lower surface) of the cylindrical bush 33A on the electric motor rotor 8 side is made smaller than the area of the end surface (upper surface) of the orbiting scroll 2 by the step portion 33b of the first embodiment, It is an example of the movement restricting means according to the present invention. By this movement restricting means, the axial force balance applied to the cylindrical bush 33A is balanced, and the upward movement of the cylindrical bush 33A in the axial direction can be restricted. Further, since it is not necessary to add a new component, the assemblability does not deteriorate.
This can be achieved by adding simple processing to a conventional cylindrical bush.

Embodiment 2 of the Invention FIG.
1 shows an embodiment of the scroll compressor according to the present invention, and shows the periphery of a main bearing 6a. In the figure, 33
B is a cylindrical bush according to this embodiment. The inner peripheral surface shape of the cylindrical bush 33B near the end near the motor rotor 8 is set to a shape of a tapered portion 33c expanding downward.

Next, the operation will be described. As described above in the first embodiment, when the scroll compressor is started, the balance in the axial direction is maintained after the filling of the electric motor rotor side path 39 is completed until the filling of the orbiting scroll side path 40 is completed. The force that moves toward the orbiting scroll 2 acts on the cylindrical bush 33B without being balanced. However, since the cylindrical bush 33B has the tapered portion 33c and the minimum flow passage cross-sectional portion 41 is small, the acting force is small as compared with the case without the tapered portion 33c. Also, the tapered portion 33
c, the motor rotor side path 3 is inevitably
9, the time required for completing the filling of the orbiting scroll-side path 40 is substantially the same, so that the time required for imbalance of the axial force is reduced.
As described above, it is unlikely that the cylindrical bush 33B moves toward the orbiting scroll 2 when the scroll compressor is started. When the scroll compressor is started, the cylindrical bush 33
If B does not move to the orbiting scroll 2, the cylindrical bush 33B is unlikely to move during the steady operation. That is, the configuration in which the area of the end surface of the cylindrical bush 33B on the electric motor rotor 8 side is made smaller than the area of the end surface of the orbiting scroll 2 side by the tapered portion 33c of the second embodiment is the movement restriction according to the present invention. It is an example of the means. By this movement restricting means, the axial force balance applied to the cylindrical bush 33B is balanced, and the upward movement of the cylindrical bush 33B in the axial direction can be restricted. Further, since it is not necessary to add a new component, the assemblability does not deteriorate. This can be achieved by adding simple processing to a conventional cylindrical bush. Further, since the tapered shape is less likely to cause stress concentration on the cylindrical bush 33B as compared with the first embodiment, there is little problem in strength. A tapered portion (not shown) formed by narrowing the vicinity of the upper end of the inner peripheral surface of the cylindrical bush 33B upward to increase the area of the end surface on the orbiting scroll 2 side may be used as the movement restricting means according to the present invention. .

Embodiment 3 of the Invention FIG. 4 shows an embodiment of the scroll compressor according to claim 1,
The periphery of the main bearing 6a is shown. In the figure, reference numeral 33C denotes a cylindrical bush according to this embodiment. At the end of the cylindrical bush 33C near the motor rotor 8, one or more grooves 33d are provided in the radial direction,
The inner peripheral surface side and the outer peripheral surface side of the cylindrical bush 33C communicate with each other.

Next, the operation will be described. As described above in the first embodiment, when the scroll compressor is started, the axial direction between the completion of the filling of the motor rotor side path 39 and the completion of the next orbiting scroll side path 40 is completed. The force balance is not balanced, and a force that moves toward the orbiting scroll 2 acts on the cylindrical bush 33C. However, most of the lubricating oil 13 passing through the motor rotor side path 39 is
Because it passes through the groove 33d rather than the minimum flow path cross section 41,
Compared to the case without the groove 33d, the cylindrical bush 33
The force acting on C is small. As described above, when the scroll compressor is started, it becomes difficult for the cylindrical bush 33C to move to the orbiting scroll 2 side. If the cylindrical bush 33C does not move toward the orbiting scroll 2 when the scroll compressor is started, the cylindrical bush 33C hardly moves during the steady operation. That is, the configuration in which the inner peripheral surface side and the outer peripheral surface side of the cylindrical bush 33C are allowed to communicate with each other by the groove 33d according to the third embodiment is an example of the movement restricting means according to the present invention. By this movement restricting means, the axial force balance applied to the cylindrical bush 33C is balanced, and the upward movement of the cylindrical bush 33C in the axial direction can be restricted. Further, since it is not necessary to add a new component, the assemblability does not deteriorate. This can be achieved by adding simple processing to the conventional cylindrical bush. Further, since it is not necessary to process the entire circumference of the cylindrical bush 33C, workability is good.

Embodiment 4 of the Invention FIG.
1 shows an embodiment of the scroll compressor according to the present invention, and shows the periphery of a main bearing 6a. In the figure, 3b
A is a main shaft portion according to this embodiment, and 33D is a cylindrical bush according to this embodiment. 3e is the crankshaft 3
Is a lubrication hole provided in the main shaft portion 3bA of the main shaft portion 3bA.
A communicates with the oil passage hole 3d. However, this lubrication hole 3e
Is located closer to the orbiting scroll 2 than the center of the main shaft portion 3bA in the axial direction.

Next, the operation of the scroll compressor according to the fourth embodiment will be described. As described above in Embodiment 1, when the scroll compressor is started, the power generated by the electric motor stator 7 and the electric motor rotor 8 is supplied to the oil pump 1 via the crankshaft 3.
6, the lubricating oil 13 stored in the closed container 10
Is first filled in the space of the oil passage hole 3d and the oil supply hole 3e of the crankshaft 3. Next, the lubricating oil 13 is started to be filled in the two oil supply paths related to the axial direction of the cylindrical bush 33D.
Then, the filling to the orbiting scroll side path 40 is completed. In this case, the force balance in the axial direction is not balanced between the time when the filling of the electric motor rotor side path 39 is completed and the time when the next filling of the orbiting scroll side path 40 is completed,
A force moving toward the orbiting scroll 2 acts on the cylindrical bush 33D.

However, since the opening position of the oil supply hole 3e is biased upward toward the orbiting scroll 2, the flow rate of the lubricating oil 13 in the motor rotor side path 39 is smaller than that in the case where it is not biased. The force acting on 33D is reduced. As described above, it is unlikely that the cylindrical bush 33D moves toward the orbiting scroll 2 when the scroll compressor is started. If the cylindrical bush 33D does not move toward the orbiting scroll 2 when the scroll compressor is started,
It is unlikely that the cylindrical bush 33D moves during the steady operation. That is, in the fourth embodiment, the oil supply hole 3e
The opening position of the lubrication hole 3e is adjusted so that the motor rotor side path 39 below the opening position of the motor shaft is wider than the orbiting scroll side path 40 above the opening position.
The configuration arranged at a position closer to the orbiting scroll 2 than the center of bA is an example of the movement restricting means according to the present invention. By this movement restricting means, the cylindrical bush 33D
Is balanced in the axial direction, and the upward movement of the cylindrical bush 33D in the axial direction can be restricted. Also, there is no need to add new parts,
The assemblability is not impaired. In addition, since it is only necessary to change the processing position of the conventional crankshaft, the workability is not impaired.

Embodiment 5 of the Invention FIG. 6 shows an embodiment of the scroll compressor according to claim 1,
The periphery of the main bearing 6a is shown. In the figure, 3bB is a main shaft portion according to this embodiment, and 33E is a cylindrical bush according to this embodiment. Reference numeral 3d denotes an oil passage hole of the crankshaft 3, which penetrates in the axial direction.
There is no oil supply hole penetrating through the main shaft portion 3bB in the radial direction from the oil passage hole 3d.

Next, the operation of the scroll compressor according to the fifth embodiment will be described. As described in the first embodiment, when the scroll compressor is started, each oil supply path is filled with lubricating oil. However, since there is no oil supply hole in the main shaft portion 3bB, the main shaft portion 3bB directly flows from the main shaft portion 3bB to the cylindrical bush 33E. There is no lubricating oil 13 supplied. Therefore, there is no need to consider the balance of the force balance in the axial direction, and the force for moving the scroll bush 2 toward the orbiting scroll 2 does not act on the cylindrical bush 33E. When the scroll compressor is started, the cylindrical bush 3
If the 3E does not move to the orbiting scroll 2 side, the cylindrical bush 33E hardly moves during the steady operation. That is, in the fifth embodiment, the crankshaft 3
The configuration in which a direct oil supply path is not provided from the main shaft portion 3bB to the inner peripheral surface side of the cylindrical bush 33E is an example of the movement restricting means according to the present invention. By this movement restricting means, the axial force applied to the cylindrical bush 33E is balanced, and the upward movement of the cylindrical bush 33E in the axial direction can be restricted. Further, since it is not necessary to add a new component, the assemblability does not deteriorate.
Further, since the number of steps for machining the conventional crankshaft is reduced, the workability is improved.

Embodiment 6 of the Invention FIG.
1 shows an embodiment of the scroll compressor according to the present invention, and shows the periphery of a main bearing 6a. In the figure, 42
Is a regulating member, which is embedded in the outer peripheral surface of the main shaft portion 3b of the crankshaft 3 at a position above the cylindrical bush 33, for example. The restricting member 42 is a pin-shaped or plate-shaped member for restricting the vertical movement of the cylindrical bush 33. The gap between the regulating member 42 and the cylindrical bush 33 is considerably small. Next, the operation of the scroll compressor according to the sixth embodiment will be described. When a force for moving the scroll compressor toward the orbiting scroll 2 is applied to the cylindrical bush 33 at the time of starting the scroll compressor or at the time of steady operation, the cylindrical bush 33 abuts on the regulating member 42 so as to face upward in the axial direction. Movement is regulated. Further, since both the cylindrical bush 33 and the regulating member 42 rotate, even when they come into contact with each other, there is no damage due to friction, abrasion, or the like at the contact portion.
That is, in the sixth embodiment, the regulating member 42 is moved to the position above the cylindrical bush 33 so that the main shaft 3b of the crankshaft 3 is moved.
The configuration provided on the outer peripheral surface is an example of the movement restricting means according to the present invention.

Embodiment 7 of the Invention FIG.
1 shows an embodiment of the scroll compressor according to the present invention, and shows the periphery of a main bearing 6a. In the figure, 42
A is a regulating member, which is embedded in the inner peripheral surface of the main bearing 6a at a position above the cylindrical bush 33, for example.
The restricting member 42A is a pin-shaped or plate-shaped member that restricts the vertical movement of the cylindrical bush 33. still,
The gap between the regulating member 42A and the cylindrical bush 33 is considerably small. Next, the operation of the scroll compressor according to the seventh embodiment will be described. When a force for moving the scroll compressor toward the orbiting scroll 2 is applied to the cylindrical bush 33 when the scroll compressor is started or when the scroll bush 33 is in a steady operation, the cylindrical bush 33 is moved.
By contacting the regulating member 42A, the upward movement in the axial direction is regulated. Further, since the main frame 6 is generally made of a casting, this can be realized by adding simple processing. That is, in the seventh embodiment, the regulating member 42A is
The structure provided on the inner peripheral surface of the main bearing 6a above the position 3 is an example of the movement restricting means according to the present invention.

Embodiment 8 of the Invention FIG.
1 shows an embodiment of the scroll compressor according to the present invention, and shows the periphery of a main bearing 6a. In the figure, 42
Reference numeral B denotes a regulating member, which is loosely fitted between the upper end surface of the cylindrical bush 33 and the lower end surface of the bearing 2A of the orbiting scroll 2. The gap between the regulating member 42B and the cylindrical bush 33 and the gap between the regulating member 42B and the orbiting scroll 2 are considerably small. Next, the operation of the scroll compressor according to the eighth embodiment will be described. When a force for moving the scroll compressor toward the orbiting scroll 2 is applied to the cylindrical bush 33 when the scroll compressor is started or during steady operation,
The cylindrical bush 33 abuts the regulating member 42B, and the regulating member 42B and the lower end surface of the bearing 2a of the orbiting scroll 2 come into contact with each other, whereby the upward movement in the axial direction is regulated. Further, since the cylindrical bush 33 can be used without changing the conventional parts as it is, the work can be easily performed.
That is, in the eighth embodiment, the configuration in which the regulating member 42B is provided above the cylindrical bush 33 is an example of the movement regulating means according to the present invention.

Embodiment 9 of the Invention FIG.
5 shows an embodiment of the scroll compressor according to No. 5, and shows the periphery of a main bearing 6a. In the figure, 4
Reference numeral 2 denotes a regulating member, for example, a plate-like member which is embedded in the outer peripheral surface of the main shaft portion 3b at a position higher than the cylindrical bush 33 and regulates the vertical movement of the cylindrical bush 33. An elastic member 43 is inserted between the regulating member 42 and the cylindrical bush 33. The elastic member 43 is always in contact with the regulating member 42 and the cylindrical bush 33 and is elastically deformed. Next, the operation of the scroll compressor according to the ninth embodiment will be described. When a force for moving the scroll compressor toward the orbiting scroll 2 is applied to the cylindrical bush 33 when the scroll compressor is started up or in a steady operation, the cylindrical bush 33 is in contact with the elastic member 43, and thus is in the axial direction. Movement is regulated. In addition, the movement of the cylindrical bush 33 in the axial direction can be restricted without receiving an impact force.

[0031]

As described in detail above, according to the scroll compressor of the first aspect of the present invention, the movement restricting means restricts the upward movement of the cylindrical bush in the axial direction at the start of refueling. Therefore, it is possible to provide a highly reliable scroll compressor in which the bearing load capacity is not reduced and the bearing is not damaged.

In the scroll compressor according to the second aspect of the present invention, a radial oil supply hole is formed in the main shaft portion of the crankshaft so that the area of the bottom surface of the cylindrical bush is smaller than that of the upper surface. By adopting the configuration in which the inner peripheral surface shape of the cylindrical bush is set, the force acting upward in the axial direction of the cylindrical bush at the start of refueling is reduced. In addition, the inner peripheral surface shape of the cylindrical bush set as described above inevitably makes the oil supply path below the oil supply hole opening position wider than the upper part, so that it takes time until the lubricating oil is filled downward. It takes. As a result, the balance of the forces acting in the axial direction is balanced, and the upward movement of the cylindrical bush in the axial direction is restricted. Therefore, it is possible to provide a highly reliable scroll compressor without a decrease in bearing load capacity and without damage to the bearing.

According to the scroll compressor of the third aspect of the present invention, the oil supply path below the opening of the oil supply hole is wider than the oil supply path above the opening of the oil supply hole. By adopting the configuration in which the opening position of the lubrication hole is arranged, it takes time for the lubricating oil to fill from the lubrication hole opening position to the lower lubrication path at the start of lubrication. The balance of the acting forces is balanced, and the upward movement of the cylindrical bush in the axial direction is restricted. Therefore, it is possible to provide a highly reliable scroll compressor without a decrease in bearing load capacity and without damage to the bearing.

Further, according to the scroll compressor according to the fourth aspect of the present invention, the regulating member used as the movement regulating means comprises:
Since the movement of the cylindrical bush is restricted by interfering with the cylindrical bush moving upward at the time of refueling, a highly reliable scroll compressor without a decrease in bearing load capacity and without damage to the bearing can be provided.

According to the scroll compressor according to the fifth aspect of the present invention, the elastic member is interposed between the cylindrical bush and the restricting member which is the movement restricting means, so that the restricting member can start the refueling. In this case, the upward movement of the cylindrical bush in the axial direction is restricted, and at that time, the impact force to the cylindrical bush is absorbed by the elastic material, so that the load capacity of the bearing is not reduced and the bearing is further damaged. It is possible to provide a reliable scroll compressor without any trouble.

[Brief description of the drawings]

FIG. 1 is a vertical sectional view showing a scroll compressor according to a first embodiment of the present invention.

FIG. 2 is a longitudinal sectional view showing a main bearing of the scroll compressor according to the first embodiment of the present invention and its periphery.

FIG. 3 is a longitudinal sectional view showing a main bearing of a scroll compressor according to a second embodiment of the present invention, and its periphery.

FIG. 4 is a longitudinal sectional view showing a main bearing of a scroll compressor according to a third embodiment of the present invention and a periphery thereof;

FIG. 5 is a longitudinal sectional view showing a main bearing of a scroll compressor according to a fourth embodiment of the present invention and its periphery.

FIG. 6 is a longitudinal sectional view showing a main bearing of a scroll compressor according to a fifth embodiment of the present invention and the periphery thereof.

FIG. 7 is a longitudinal sectional view showing a main bearing of a scroll compressor according to a sixth embodiment of the present invention and its periphery.

FIG. 8 is a longitudinal sectional view showing a main bearing of a scroll compressor according to a seventh embodiment of the present invention and the periphery thereof.

FIG. 9 is a longitudinal sectional view showing a main bearing of a scroll compressor according to an eighth embodiment of the present invention and its periphery.

FIG. 10 is a longitudinal sectional view showing a main bearing of a scroll compressor according to a ninth embodiment of the present invention and its periphery.

FIG. 11 is a longitudinal sectional view showing a conventional scroll compressor.

[Explanation of symbols]

Reference Signs List 1 fixed scroll, 2 orbiting scroll, 3 crankshaft, 3b main shaft, 3bA main shaft, 3bB main shaft, 3d oil passage hole, 3e oil supply hole, 6 main frame, 8
Motor rotor, 9 auxiliary frame, 10 sealed container, 1
3 Lubricating oil, 14 Upper balance weight, 15 Lower balance weight, 32 Band, 33 Cylindrical bush, 3
3A cylindrical bush, 33B cylindrical bush, 33
C cylindrical bush, 33D cylindrical bush, 33E
Cylindrical bush, 33b step, 33c taper,
33d groove, 39 motor rotor side path, 40 orbiting scroll side path, 41 minimum flow path cross section, 42 restriction member, 42A restriction member, 42B restriction member, 43 elastic material.

Claims (5)

[Claims] 1. A closed container in which lubricating oil is stored at a bottom portion, a fixed scroll and an orbiting scroll which are arranged at an upper portion in the closed container and form a compression chamber by combining spiral projections with each other; A crankshaft slidably connected to the orbiting scroll at a portion to apply a rotational force to the orbiting scroll; and a rotatably and slidably supporting the orbiting scroll and rotatably supporting a main shaft portion above the crankshaft. Main frame, a sub-frame for rotatably supporting a lower portion of the crankshaft, a motor rotor provided on the crankshaft between the main frame and the sub-frame, and a vertical Upper and lower balance weights provided on both sides to balance the centrifugal force generated by the orbiting motion of the orbiting scroll. And a band-shaped portion formed in a drum shape in which an upper and lower central portion is protruded over the entire periphery on the outer periphery of the main shaft portion so as to prevent occurrence of a one-sided hit in the main shaft portion due to bending deformation of the crankshaft. A cylindrical bush that faces the outer peripheral surface of the main shaft portion and is fitted around the outer periphery of the band-shaped portion with a small gap, and the oil passage hole formed through the crankshaft in the axial direction. In a scroll compressor configured to supply oil to the main shaft portion via a cylindrical bush, the scroll compressor further includes a movement restricting unit that restricts upward movement of the cylindrical bush in the axial direction at the start of refueling. And scroll compressor. 2. The scroll compressor according to claim 1, wherein a radial lubrication hole communicating with the lubrication hole is formed in the main shaft portion of the crankshaft, and the movement restricting means includes:
A scroll compressor having a configuration in which the inner peripheral surface shape of the cylindrical bush is set so that the area of the bottom surface of the cylindrical bush is smaller than the upper surface. 3. The scroll compressor according to claim 1, wherein a radial lubrication hole communicating with the lubrication hole is formed in the main shaft portion of the crankshaft, and the movement restricting means includes:
The opening position of the oil supply hole of the main shaft portion is lower than the opening position of the oil supply hole, and the oil supply path between the outer peripheral surface of the main shaft portion and the inner peripheral surface of the cylindrical bush is located above the opening position of the oil supply hole. A scroll compressor having a configuration arranged at an axial position wider than a refueling path. 4. The movement restricting means is a restriction member provided at a position above the cylindrical bush and restricting the upward movement of the cylindrical bush by interfering with the cylindrical bush during refueling. The scroll compressor as described. 5. The scroll compressor according to claim 4, wherein an elastic material is interposed between the cylindrical bush and the regulating member.