JPH0742944B2 - Scroll machine blades - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a scroll machine used as a scroll scroll compressor such as a refrigeration scroll compressor such as an air conditioner and a refrigerator and a pump.

2. Description of the Related Art A compression mechanism of a scroll compressor will be described with reference to FIGS. 2 and 3.

The rotational movement of the crankshaft 5 accompanying the rotation of the electric motor element 4 is
It is transmitted to the swirling spiral vane component 8 via the eccentric bearing 11 and the swirling spiral vane shaft 12, but due to the action of the rotation restraint component 13, the swirling spiral vane component 8 does not rotate and the involute of the fixed spiral vane component 7 or A turning motion is performed with the center of the similar curve as the center of turning.

At this time, the winding end end 8 of the blade 8a of the swirling spiral blade component 8 is
The suction is completed when a'is in contact with the blade 7a of the fixed spiral blade part 7 and the winding end 7a 'of the blade 7a of the fixed spiral blade part 7 is in contact with the blade 8a of the swirl spiral blade part 8, respectively.

Then, along with the revolution movement of the swirling spiral blade component 8, the blade 7a
As the two contact points between the blades 8a and the blades 8a approach the center of the involute, the pressure in the compression chamber 9 rises and is discharged from the discharge port 26.

Next, the shape of the upper end of the wrap will be described.

As shown in FIG. 4, the scroll compressor is provided with chamfers 7c and 8c at the tips of the blades of the fixed and orbiting spiral vane components 7 and 8. When this is used as a compressor, it is desirable that the sealing surfaces of the end plates 7c, 8b and the blades 7a, 8a move relative to each other without a gap as shown in FIG. It is difficult to make the tangent portions of 7a, 8a and the end plates 7b, 8b into ideal shapes.

Therefore, at the intersection of the blades 7a, 8a and the end plates 7b, 8b, as shown in FIG. 6, a slight protrusion 27 remains when the side surfaces of the blades and the end plate portion are processed, and the upper end of the blade opposite to this is formed. In order to avoid interference with the side ridges, it is necessary to provide chamfers at the blade tips.

Problems to be Solved by the Invention The gap 28 surrounded by the chamfers of the vanes 7a, 8a and the vanes 7a, 8a and the vanes 7a, 8a and the vanes 7a, 8a including a slight protrusion of the tangent portion of the vanes 7a, 8a and the vanes 7a, 8b is small. Although it is easy to understand that the gas or liquid leaks less and the efficiency is improved, it is difficult to form the blade tip chamfer to the minimum in consideration of the guarantee of the protrusion 27 on molding.

Further, even if the chamfering of the tips of the blades 7a, 8a can be made extremely small, there is a high possibility that the upper end of the outer peripheral portion of the blade comes into contact with the outside depending on the handling of the compressor assembly. Likely to happen. When the tip chamfered portions of the blades 7a, 8a are deformed due to dents or the like, the compression chamber 9 constituted by the blades 7a, 8a and the end plates 7b, 8b is deformed due to dents or the like, so It deforms as shown in (a) and (b), and gas or fluid leaks more.

In addition, due to the deformation, local contact occurs between the end plates 7b, 8b and the blades 7a, 8a of the fixed spiral vane component 7 and the swirling spiral vane component 8, resulting in abnormal noise and abnormal wear. However, in the worst case, the inside of the compressor or the pump may be destroyed.

The present invention solves the above-mentioned problems, practically reduces the leakage from the tangent portion between the blade and the end plate, and the gap 28 surrounded by the chamfering of the blade tip, and practically prevents the deformation of the blade tip due to a dent or the like. The purpose is to eliminate the phenomena such as leakage reduction, abnormal noise, abnormal wear, and destruction.

Means for Solving the Problems In order to achieve this object, the present invention provides a chamfered portion at each tip of the fixed spiral vane and the swirl spiral vane forming a compression chamber or a pump chamber, and at the vane outer wall side, The chamfered size of at least one chamfered portion of the fixed or swirling spiral blade is formed so as to be larger at the end of winding of the blade and smaller at the beginning of winding of the blade, and chamfered in a cross section perpendicular to the winding direction of the fixed or swirling spiral blade. The chamfered portion is formed so that the inner wall side of the blade is always smaller than the outer wall side of the blade.

As described above, in the compression mechanism of the working scroll compressor, the pressure in the compression chamber 9 increases as it approaches the center. Therefore, the closer to the center, the larger the pressure difference with the adjacent compression space.

Therefore, at the blade start 30b, both the blade outer wall side 31a and the blade inner wall side 31b have a great influence on the compression efficiency.
The effect of improving the efficiency is great by reducing the chamfered size of the upper end of the blade as much as possible. On the other hand, deformation due to dents or the like on the upper end of the blade is likely to occur mainly at the end 30a of the blade on the outer wall side 31a of the blade, and is not a particular obstacle. Also,
At the blade end 30a on the blade outer wall side 31a, by increasing the chamfering size of the spiral upper end, it is possible to prevent deformation of the upper end of the blade due to dents or the like, and it is easy to handle in manufacturing. On the other hand, at the blade winding end 30a, the pressure difference between the adjacent compression chambers is small, and the influence on the efficiency is very small.

Example Hereinafter, one example of the present invention will be described with reference to the accompanying drawings.

First, a schematic structure of a general hermetic scroll compressor including the present invention will be described with reference to FIG.

In the figure, a stator 2 and a rotor 3 are provided inside a closed container 1.
And a compressor element 6 driven by the electric motor element 4 via a crankshaft 5. The fixed spiral vane component 7 and the swirl spiral vane component 8 mesh with each other to form a plurality of compression chambers 9, and the drive of the electric motor element 4 is transmitted to the crankshaft 5, the eccentric bearing 11, and the swirl spiral vane shaft 12 to form the swirl spiral. The blade component 8 turns. The swirling spiral blade component 8 is restrained from rotating by a rotation restraining component 13.

Refrigerant gas that enters the closed container 1 from the suction pipe 24 is sucked into the suction port.
It is sucked into the compressor element 6 from 25, compressed in the compression chamber 9 and discharged from the discharge port 26.

FIG. 1 is a detailed view of a swirling spiral blade component for explaining an example of the present invention.

The swirling spiral blade component 8 is composed of an end plate 8b and a spiral blade 8a. Then, chamfers 8c are provided on both corners at the upper ends of the blades 8a. Regarding the degree of chamfering, on the blade outer wall side 31a, the chamfering degree is large at the winding end outer periphery 30a and is small at the winding start 30b. The degree of chamfer gradually changes from the end of winding to the beginning of winding.

The chamfering degree on the blade inner wall side 31b is always smaller than the chamfering degree on the blade outer wall side 31a of the opposing portion. That is, when the cross section of the swirling spiral blade component 8 perpendicular to the spiral winding direction is viewed, the chamfering degree is always smaller on the blade inner wall side 31a than on the blade outer wall side 31a. However, the size of the blade inner wall side 31b does not necessarily have to change from the winding end to the winding start, and may be uniform (the inner and outer circumferences may be substantially equal at the center of the spiral).

In the above structure, when the compressor is driven, the pressure in the compression chamber 9 increases as it approaches the center of the spiral, and the pressure difference between the compression chamber 9 and the adjacent compression chamber increases. Therefore, at the blade winding start 30b, the blade outer wall side 31a and the blade inner wall side 31a
Both b have a large effect on efficiency, so it is necessary to reduce the chamfer size at the upper end of the blade, but deformation due to dents etc. at the upper end of the blade is mainly due to the end of winding 3 of the blade on the outer wall side 31a of the blade.
It is 0a, which does not cause any obstacle. Also, the blade outer wall side 31
At the end 30a of the blade of a, by increasing the chamfering size of the upper end of the spiral, it is possible to prevent the upper end of the blade from being deformed due to dents or the like, which facilitates the handling in manufacturing. However, at the winding end 30a of the blade, the pressure difference between the adjacent compression chambers is small and the influence on the efficiency is very small.

In addition, the chamfering size of the upper end on the outer wall side of the blade is divided into blocks in which the winding angle of the blade is fixed, and each block is chamfered stepwise so that the winding end is larger by 30a and the winding start is smaller by 30b. Also has the same effect.

In any of the examples, the molding can be performed with the processing equipment using the cam, the gear, or the NC, but particularly in the case of the processing equipment using the NC, it is easy to adjust the shaping of the chamfering of the upper end of the blade.

Further, although the swirling spiral blade component 8 has been described in the present embodiment, it goes without saying that the fixed spiral blade component 7 can be similarly implemented.

Furthermore, although the present embodiment has been described as a scroll compressor, it goes without saying that it can be similarly implemented as a machine such as a pump or an expander.

As described above, according to the present invention, in the scroll machine,
A chamfered portion is provided at each tip of the fixed spiral vane and the swirl spiral vane forming the compression chamber or the pump chamber, and the chamfered size of at least one chamfered portion of the fixed or swirl spiral vane is set on the outer wall side of the vane. In the section perpendicular to the winding direction of the fixed or swirling spiral blade, the chamfered portion of the chamfered portion is always larger on the blade inner wall side than on the blade outer wall side. By making it small, it was possible to realize a highly efficient compressor or pump with little leakage.
At the same time, it is possible to prevent deformation due to dents on the top surface of the spiral,
The productivity can be greatly improved, the cost can be reduced, and the reliability can be improved with respect to problems such as abnormal noise, abnormal wear, and mechanical destruction.

[Brief description of drawings]

FIG. 1 is a perspective view of a swirling spiral blade of a scroll compressor according to an embodiment of the present invention, FIG. 2 is a vertical sectional view of a hermetic scroll compressor, and FIG. 3 is a fixed and swirling spiral blade of the compressor. FIG. 4 is an assembly view, FIG. 4 is a vertical cross-sectional view of a spiral vane portion showing a conventional example, and FIG. 5 is a vertical cross-sectional view showing a spiral vane portion of an ideal shape.
FIG. 6 is a vertical cross-sectional view of a general spiral blade portion, FIG. 7 (a)
(B) is a vertical cross-sectional view of another example in which the conventional blade is deformed. 1 ... airtight container, 2 ... stator, 3 ... rotor, 4 ...
Electric motor element, 5 ... Crankshaft, 6 ... Compressor element, 7
...... Fixed spiral blade parts, 7a ...... Wings, 7b ...... End plate, 8 ...
… Swirl spiral blade component, 8a …… Blade, 8b …… End plate, 8c ……
Chamfer, 9 ... Compressor, 11 ... Eccentric bearing, 12 ... Swirl spiral blade shaft, 13 ... Rotation restraint parts, 30a ... Blade outer circumference, 30b
...... The inner circumference of the blade.

Claims (1)

[Claims] 1. A fixed scroll vane fixed to a housing, which has a first end plate and a first swirl portion projecting from one surface of the first end plate, and faces the fixed end swirl blade. And a second end plate which is provided on the second end plate so as to project from the second end plate and meshes with the first spiral part at a different angle to form a space between the second spiral plate and the first spiral part. A swirl spiral blade having a swirl part of the swirl and a drive mechanism for causing the swirl swirl blade to swivel around the center of the fixed swirl blade while preventing rotation of the swirl swirl blade. In a scroll machine that compresses or sucks, a chamfer is provided at each tip of the fixed spiral vane and the swirl spiral vane that form a compression chamber or a pump chamber, and at least one chamfer of the fixed or swirl spiral vane is provided on the outer wall side of the vane. Department The chamfer is formed to have a size larger toward the end of the blade and smaller toward the start of the blade, and the chamfer of the chamfered portion in the cross section perpendicular to the winding direction of the fixed or swirl spiral vane is larger than the vane outer wall side. Is a blade for scroll machines whose inner wall is always small.