JPH08254189A - Scroll compressor - Google Patents

Abstract

PURPOSE: To prevent the generation of large vibration and noise resulting from collision between a fixed helical blade part and a revolving helical blade part. CONSTITUTION: An eccentric bearing groove 10 having a side paralleling the axis of a crankshaft 8 and a central line extending through the axis of a crankshaft 8 is formed in one end on the revolving helical blade part 2 side of a crankshaft 8. An eccentric bearing 11 in which the drive shaft of the revolving helical blade part is rotatably fitted is slidably disposed inside the eccentric drive bearing groove 10. A bearing hole for the eccentric bearing 11 in which the drive shaft 4 of the revolving helical blade part is formed in such a state to be deviated to one of the slide surface of the eccentric bearing 11.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor used for air conditioning or air compression.

[0002]

2. Description of the Related Art Conventionally, a compressor of this type has a structure as shown in FIG. 3, for example.

The structure shown in FIG. 3 is applied to a compressor operating at a constant rotation speed, and the swirling spiral blade 2a and the fixed spiral blade 1a are operated while always in contact with each other to reduce the radial clearance of the blade. This was to keep the leakage in the compression chamber to a minimum and improve the compression efficiency.

That is, a bearing fitting hole 10a is formed on the upper end surface of the crankshaft 8 so as to extend away from its axis 0, and an eccentric bearing 11 is slidable in the longitudinal direction and rotatable in this bearing fitting hole 10a. It is fitted so as not to. And
Before the eccentric bearing 11 contacts the outer wall surface of the bearing fitting hole 10a, both blades are in contact with each other. In addition, the angle formed by the longitudinal direction of the bearing fitting hole 10a and the resultant force F of the gas compression force fg acting on the swirling spiral blade component 2 and the centrifugal force fc is constant rotation speed and under an allowable gas compression load. Therefore, it is set to 90 ° or less. Therefore, in a normal operating state, the resultant force F acting on the swirling spiral blade component 2 moves to the outside of the eccentric bearing fitting hole 10a on the wall surface of the bearing fitting hole 10a. As a result, in such a compressor, the swirling spiral blade 2a and the fixed spiral blade 1a always operate while contacting at any point.

[0005]

With this structure,
It is necessary to machine and finish a groove of a prescribed angle at a fixed distance from the shaft center at the end of the crankshaft 8. At this time, since the reference plane for processing is the outer periphery of the crankshaft 8, it is necessary to set the angle and the amount of eccentricity therefrom, and high-precision processing cannot be expected. If the precision is poor, the contact force of the blades and the gap between the blades cannot be adjusted. If the shape precision of the blades is poor, the contact point between the swirling spiral blade 2a and the fixed spiral blade 1a is continuous. However, the eccentricity constantly fluctuates, and sometimes the blades collide with each other, which causes a problem of large vibration and noise.

Further, as described above, this configuration is suitable for a compressor operating at a constant rotation speed, and has a problem that it cannot be applied to a variable speed compressor which has been mainly used as an air conditioning compressor in recent years. . That is, when the contact force between the swirling spiral blade 22a and the fixed spiral blade 1a is set to an appropriate value at a certain specific rotation speed, the centrifugal force fc acting on the swirling spiral blade component 2 is reduced in the lower rotation speed range. As a result, the contact force of the blades also decreases, the swirling spiral blades 2a vibrate on the fixed spiral blades 1a, and in some cases a large gap is created in the radial direction of the blades, causing the gas being compressed to leak to the low pressure side. There was the problem of being unable to drive.

Further, in the high speed rotation speed range, there is a problem that the blades wear due to excessive contact force between the blades.

[0008]

SUMMARY OF THE INVENTION In order to solve the above problems, the present invention provides a fixed spiral blade component and a spiral spiral blade in which spiral blades are provided on one surface of a wall body and the respective blades are combined with each other. A scroll compression mechanism comprising: a component, a crankshaft that eccentrically drives the orbiting spiral vane component, a bearing component that supports the crankshaft, and a restraint component that constrains the rotation of the orbital spiral vane component. An eccentric drive bearing groove is formed at one end of the shaft on the side of the orbiting spiral vane component, the side surface of the groove being parallel to the axis of the crankshaft and the center line of which passes through the axis of the crankshaft. The eccentric bearing in which the drive shaft of the swirling spiral blade component is rotatably fitted is slidably arranged, and the bearing hole of the eccentric bearing in which the drive shaft of the swirling spiral blade component is fitted is provided. Serial those formed by drilling biased towards over side sliding surface of the eccentric bearing.

With this configuration, the amount of eccentricity can be easily set, and the radial gap of the blades can be kept constant in a wide rotational speed range, so that low vibration, low noise, and high compression efficiency can be achieved. Machine can be realized.

Then, the bearing hole into which the drive shaft of the swirling spiral blade part is rotatably fitted is formed in one of the sliding surfaces of the eccentric bearing in a biased manner so that the angle of the eccentric drive bearing groove can be easily set. it can.

[0011]

In order to solve the above problems, the present invention provides a fixed spiral blade component and a swirl spiral blade component in which spiral blades are provided on one surface of a wall body and the respective blades are combined with each other. A scroll compression mechanism comprising: a crankshaft that eccentrically drives the swirl-vortex-blade component; a bearing component that supports the crankshaft; and a restraint component that restrains rotation of the swirl-vortex-blade component. An eccentric drive bearing groove whose side surface is parallel to the axis of the crankshaft and whose center line passes through the axis of the crankshaft is formed at one end on the side of the orbiting spiral blade component, and inside the eccentric drive bearing groove, An eccentric bearing in which the drive shaft of the swirling spiral blade component is rotatably fitted is slidably disposed,
A bearing hole of the eccentric bearing into which the drive shaft of the swirling spiral blade part is fitted is formed so as to be biased toward the sliding surface of the eccentric bearing.

With this configuration, the amount of eccentricity can be easily set, and the radial gap of the blade can be kept constant over a wide rotation speed range, so that low vibration, low noise and highly efficient compression can be achieved. Machine can be realized.

The angle of the eccentric drive bearing groove can be easily set by forming a bearing hole in which the drive shaft of the swirling spiral blade part is rotatably fitted to one of the sliding surfaces of the eccentric bearing. it can.

[0014]

An embodiment of the present invention will be described below with reference to the accompanying drawings.

FIG. 1 and FIG. 2 show the scroll compressor according to the present invention configured as a refrigerant compressor for air conditioning, for example.

In the figure, 1 is a fixed spiral blade component, 1
a is a fixed spiral blade, 1b is a wall body of the fixed spiral blade,
Reference numeral 2 is a swirl spiral blade component, 2a is a swirl spiral blade, and 2b is a wall body of the swirl spiral blade. The fixed spiral blade 1a and the swirling spiral blade 2a are configured by an involute curve or a curve close to the involute curve.
To form. 4 is a drive shaft of the swirling spiral blade part 2,
In this embodiment, it projects from the center of the back surface of the wall body 2b of the swirling spiral component 2. Reference numeral 5 denotes a thrust bearing for supporting the wall body 2b of the swirling spiral blade 2a, 6 denotes a bearing component fixed to the fixed spiral blade component 1 with bolts, and 7 denotes engagement with the swirl spiral blade component 2 and the bearing component 6. A rotation restraint component for preventing rotation of the swirling spiral component 2, 8 is a crankshaft for driving the swirling spiral blade component 2, and a longitudinal oil hole 9 is formed in the crankshaft 8 at its axial center. Reference numeral 8a is a first main shaft of the crankshaft, 8b is a second main shaft of the crankshaft, 6a is a first bearing above the bearing component 6 and supporting the first main shaft 8a, 6
Reference numeral b is a second bearing located below the bearing component 6 and supporting the second main shaft 8b. An eccentric drive 10 is formed on the end face of the first main shaft 8a on the side of the swirling vane component 2 so that the side surface of the groove is parallel to the axis of the crankshaft 8 and the centerline of the groove passes through the axis of the crankshaft 8. It is a bearing groove. Reference numeral 11 denotes an eccentric bearing which is rotatably fitted to the drive shaft 4 of the swirling spiral blade part 2. The eccentric bearing 11 is slidable in the longitudinal direction of the eccentric drive bearing groove 10 and is eccentric so as not to rotate. It fits in the groove 10. Reference numeral 12 is a coil spring that is inserted into the eccentric drive bearing groove 10 on the axial center side of the crankshaft 8 and presses the eccentric bearing 11 against the outer wall surface of the eccentric drive bearing groove 10. Then, in a state where the eccentric bearing 11 is pressed against the outer wall surface of the eccentric drive bearing groove 10, a small gap exists between the fixed spiral blade 1a and the swirling spiral blade 2a at the closest points in the radial direction. The longitudinal dimension of the eccentric drive bearing groove 10 and the dimension of the eccentric bearing 11 are set. Thirteen
Is an electric motor that rotationally drives the crankshaft 8, 13a is a rotor of the electric motor 13 integrated with the crankshaft 8, and 13b is a stator of the electric motor 13. 14 is an airtight container that seals the entire compression, 15 is an oil pump that is connected to one end of the crankshaft 8 and rotates together with the crankshaft 8. The shaft of the oil pump 15 is connected to the lower part of the airtight container 14 to stop rotation. ing. Reference numeral 16 is refrigerating machine oil, and 17 is a suction pipe connected to a closed container. Reference numeral 18 is a discharge hole provided at the center of the living body 1b of the fixed spiral blade component, 19 is a discharge valve provided so as to cover the discharge hole, 20 is a valve retainer, 21 is a discharge chamber, and 22 is a discharge pipe.

In FIG. 2, eccentricity from the axis O of the crankshaft 8 to the center O of the drive shaft 4 of the swirling spiral blade. If the rotation direction of the crankshaft 8 is now in the direction of arrow A, fg is The centrifugal force acting on the hardened spiral blade component 2, fg is the gas compressive force acting on the hardened spiral blade component 2, and F is the combined force of fc and fg. Further, the angle formed by the eccentric direction of the swirling spiral blade component 2 and the longitudinal direction of the eccentric drive bearing groove 10 is α,
The angle between the eccentric direction and the resultant force F is β.

In the compressor thus constructed, when the stator 13b of the electric motor 13 is energized, the rotor 13a
Generates torque and rotates with the crankshaft 8. When the crankshaft 8 rotates, torque is transmitted to the drive shaft 4 of the swirling spiral blade via the eccentric drive bearing groove 10 and the eccentric bearing 11, and the swirling spiral blade component 2 moves above the thrust bearing 5.
While the posture is maintained by the rotation restraint component 7, it makes a swiveling motion around the axis O of the crankshaft 8 to perform a compression action.

Along with this, the gas is sucked in through the suction pipe 17, once enters the closed container 14, and is taken into the compression chamber 3 through the opening of the bearing component 6 (the arrow indicates the gas flow). The gas that has been compressed in the compression chamber 3 and has a high pressure and high temperature is discharged from the discharge hole 18 to the discharge chamber 21, and then discharged from the discharge pipe 22 to the outside.

As described above, the normal operation is performed. In this embodiment, the resultant force F of the gas compressing force fg and the centrifugal force fc is used.
And the angle formed by the longitudinal direction of the eccentric drive bearing groove 10 (α +
β) is set to 90 ° or more. Therefore, the resultant force F tends to slide the eccentric bearing 11 in a direction to reduce the eccentric amount of the swirling spiral blade part 2, but the eccentric bearing 11 is slid in a predetermined position, that is, outside the eccentric drive bearing groove 10. The adhering force of the coil spring 12 is set so that a minimum necessary force is applied to press the wall against the wall. Therefore, the amount of eccentricity is kept constant in a wide rotational speed range, so that the blades are not in contact with each other and the radial gap is also kept constant.

Therefore, the vibration and noise are small in a wide rotation speed range, the blade is not worn, and the compression efficiency is high.

Further, with such a structure, the angle α formed between the eccentric drive bearing groove 10 and the eccentric direction can be set large even in a compressor operating at a low speed. Then, not only at low speed but also at high speed, when the refrigerant liquid or oil is sucked into the compression chamber 3 and the compression load exceeds the allowable value, the eccentric drive bearing groove increases as the compression load fg increases. Since the angle (α + β) formed by the longitudinal direction of 10 and the resultant force F greatly exceeds 90 °, the component force F of the resultant force F = |
Fcos (α + β) | overcomes the pressing force of the coil spring 12 and causes the eccentric bearing 11 to slide in the longitudinal direction of the eccentric drive bearing groove 10 to reduce the amount of eccentricity. Then, the radial gap between the blades is expanded, the amount of leakage increases from the high pressure compression chamber 3 to the low pressure compression chamber 3, the load is reduced, and the compressor is protected from liquid compression.

Also, when foreign matter is taken into the compression chamber 3, the eccentricity ε is reduced, the radial gap of the blade is enlarged, and the foreign matter is discharged from the discharge hole 18 so that a prompt operation is possible. I can continue.

Then, as shown in FIG.
The angle between the eccentric direction and the longitudinal direction of the eccentric drive bearing groove 10 is set by piercing the one bearing hole to one of the sliding surfaces of the eccentric bearing 11 so that the eccentric drive bearing groove 10 is What is necessary is just to install so that it may pass through the axis O of the shaft 8, and the eccentric drive bearing groove 10 can be processed easily.

[0025]

As described above in detail, according to the present invention, the fixed spiral blade component and the swirl spiral blade component in which the spiral blades are provided on one surface of the wall body and the respective blades are combined with each other, and the swirl A crankshaft for eccentrically driving the spiral blade part, and a bearing part for supporting the crankshaft,
A scroll compression mechanism including a restraint component that restrains rotation of the swirl spiral blade component, wherein a side surface of a groove is parallel to an axis of the crank shaft at one end of the crank shaft on the swirl spiral blade component side. An eccentric drive bearing groove whose center line passes through the axis of the crankshaft is formed, and an eccentric bearing in which the drive shaft of the swirling spiral blade component is rotatably fitted is slidably disposed inside the eccentric drive bearing groove. The bearing hole of the eccentric bearing, into which the drive shaft of the swirling spiral blade part fits, is formed so as to be biased toward the sliding surface of the eccentric bearing, so that the amount of eccentricity can be easily set. In addition, since the radial gap of the blades can be kept constant in a wide rotation speed range, a compressor with low vibration and noise and high efficiency can be realized.

Then, the bearing hole into which the drive shaft of the swirling spiral blade component is rotatably fitted is formed in one of the sliding surfaces of the eccentric bearing in a biased manner so that the angle of the eccentric drive bearing groove can be easily set. it can.

[Brief description of drawings]

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

FIG. 2 is a cross-sectional view of a main part of the scroll compressor.

FIG. 3A is a cross-sectional view of a main part of a conventional scroll compressor, and FIG. 3B is a cross-sectional view of the same part.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Fixed spiral blade part 2 Swirling spiral blade part 3 Compression chamber 4 Drive shaft 5 Thrust bearing 6 Bearing part 7 Rotation restraint part 8 Crankshaft 10 Eccentric drive bearing groove 11 Eccentric bearing 12 Coil spring 13 Electric motor 14 Airtight container 15 Oil pump

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hiroshi Karato 1006 Kadoma, Kadoma City, Osaka Prefecture Matsushita Electric Industrial Co., Ltd.

Claims (1)

[Claims] 1. A fixed spiral vane component and a swirl spiral vane component in which spiral vanes are provided on one surface of a wall body and the respective vanes are combined with each other, and a crankshaft for eccentrically driving the swirl spiral vane component. A scroll compression mechanism including a bearing component that supports the crankshaft and a restraining component that restrains rotation of the swirling spiral vane component, wherein a side surface of a groove is provided at one end of the crankshaft on the swirling spiral vane component side. An eccentric drive bearing groove is formed whose center line is parallel to the axis of the crankshaft and passes through the axis of the crankshaft, and the drive shaft of the swirling spiral blade part is rotatably fitted inside the eccentric drive bearing groove. The eccentric bearing is fitted slidably, and the bearing hole of the eccentric bearing into which the drive shaft of the swirling spiral blade component fits is formed by biasing the bearing hole toward the sliding surface of the eccentric bearing. Lumpur compressor.