JPH0494485A - Scroll compressor - Google Patents

Abstract

PURPOSE:To reduce a leakage amount by bringing a point end of either one or the other or both volute blades surely into contact with a groove bottom surface, opposed to the point end, when both volute blade parts are combined. CONSTITUTION:A step difference delta1 is provided between a groove bottom surface 23 of a volute blade 11 of a turning volute blade part 13 and a turning end plate surface 24 in the peripheral part, and a step difference delta2 is provided between volute blade point end surface 25 of a fixed volute blade part 9 and a peripheral surface 26 of a fixed blade frame unit 7. A relation of the step differences delta1, delta2 is set to the relation where delta1<delta2 or delta1>delta2, and when both the volute blade parts 9, 13 are combined, a point end of either one or both the volute blades is surely brought into contact with the groove bottom surface of the volute blade opposed to this point end. In this way, before a turning end plate 12 is brought into contact with the fixed blade frame unit 7 during operation, any of the volute blade point end is surely brought into contact with the groove bottom surface of the volute blade opposed to this volute blade point end. Accordingly, a clearance in the axial direction is decreased to almost 0 to substantially reduce leakage, and performance of a compressor is greatly improved.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a hermetic scroll compressor.

BACKGROUND OF THE INVENTION FIGS. 4(a) and 4(b) are cross-sectional views of a rotating spiral vane component and a fixed spiral vane component of a conventional scroll compressor disclosed in Japanese Patent Laid-Open No. 63-65187. Figure 4 (
In 1), the tooth groove bottom surface 51 at the center of the rotating spiral blade component 5o is set lower than the rotating mirror plate surface 53 of the rotating mirror plate 52 by a dimension of . In addition, in FIG. 4(b), a tooth groove bottom surface 55 at the center of the fixed spiral blade component 54 is shown.
is set lower than the tooth groove outer circumferential portion 56 by the dimension of 6-swirling spiral vane part 501F) step dimension.

and the step size of the fixed spiral vane part 54, and - omitted from the frame.
It is in the relationship of mk.

In addition, as another conventional example,
In some cases, as in the publication, a tip seal is inserted into the tip of the spiral blade in order to prevent leakage from the tip of the spiral blade, and the shape of the tip seal is also used to prevent overcompression.

However, with such a structure, a gap is created between the tip of the spiral blade and the bottom of the opposing tooth groove, which greatly reduces the performance of the compressor. If you set the dimensions of the step to be as small as possible, it will cause a wide range of pressure,
Depending on the temperature operating conditions, the contact between the tips of the spiral vanes becomes excessive, causing artificial variations in compression performance and lowering reliability. In addition, in the case where a tip seal is inserted at the tip of the spiral blade in order to avoid the disadvantages of 1), a gap is always created between the side surface of the tip seal and the bottom surface of the tooth groove that opposes it, and leakage occurs in this area. It is clear that the 凰 is larger than that and causes a decrease in performance.

The present invention solves the above-mentioned problems, and aims to provide a scroll compressor in which the contact between the tips of the spiral blades can be optimized and the amount of leakage can be significantly reduced.

Means for Solving the Problems 5 In order to solve the problems, the scroll compressor of the present invention is provided with an electric motor and a compressor ms driven by the electric motor disposed inside a closed container. A fixed spiral vane component having a fixed spiral vane in which the lR is fixed or formed integrally with a fixed vane frame body, and a rotating spiral vane that engages with the fixed spiral vane to form a plurality of compressed spaces is fixed or formed on a rotating mirror plate. A rotating spiral blade component, a rotation restraining component that restrains the rotation of the rotating spiral blade component, a crankshaft that is rotationally driven by the electric motor to eccentrically rotate the rotating spiral blade component, and a bearing that supports this crankshaft. A suction pressure or a pressure close to the pressure is applied to a part or the whole of the outer periphery and back surface of the rotating head plate, and a small gap rII5 is provided at the back surface of the rotating head plate, so that the rotating swirl A step A2 is provided between the groove bottom surface of the spiral vane of the blade component and the rotating mirror plate surface, and a step A2 is provided between the spiral vane tip surface and the outer B surface of the fixed spiral vane component, and this step A1, 12 is provided. Jl (12 or Jl) J2 is constructed so that when the spiral blade parts 1ii are combined, the tip of one or both of the spiral blades is always in contact with the groove bottom surface of the opposing spiral blade. The relationship of J2 is Jl < J2 or Jl)J2. Therefore, during operation, before the rotating head plate and the fixed blade frame come into contact, the tip of one of the H winding blades and the opposite When the groove bottom surface contacts the groove bottom surface, the gap in the uniaxial direction becomes almost zero, and leakage is greatly reduced, resulting in a significant improvement in the performance of the compressor. Furthermore, since the suction pressure or a pressure close to the suction pressure is acting on the rotating head plate surface on the outer periphery of the rotating head plate, leakage from the gap between the rotating head plate and the fixed blade frame does not significantly reduce performance. In addition, the tip of the spiral blade expands greatly due to pressure and temperature.
If the comb-like contact becomes excessive, it can be avoided by providing a very small gap on the back of the turning plate. Therefore, the performance of the compressor is greatly improved and reliability is also sufficiently ensured.

EXAMPLE Hereinafter, an example of the present invention will be described with reference to the drawings.

FIG. 1 is a longitudinal sectional view of a scroll compressor according to an embodiment of the present invention. In FIG. 1, reference numeral 1 denotes an airtight container, in which a compression mechanism 2 is provided below, an electric motor 3 for driving the compression mechanism 2 is provided above the compression mechanism 2, and a stator 4 of an electric fi 3 is fixed to the airtight container 1. , the rotor 5 of the electric motor 3 is the compression mechanism 2
It is connected to a crankshaft 6 that drives the. Compression mechanism 2
is a fixed spiral blade 8 formed integrally with the fixed blade frame 7.
a fixed spiral vane part 9 having a fixed spiral vane part 9;
A swirling spiral vane component 13 formed on a swirling mirror plate 12 and a swirling spiral vane component 3 forming a swirling spiral vane 11
Rotation restraint component 14 that prevents rotation and allows only rotation.
, a turning drive shaft 15 provided on the opposite side of the turning parent plate 12 from the turning spiral blade 11 , and a main shaft 16 of the crankshaft 6 .
The bearing, which has an eccentric bearing 17 which is provided inwardly and is configured to drive the swing drive shaft 15 and a main bearing 18 which supports the crankshaft 6, is a part 19; A back pressure partition ring 20 is provided on the back side of the rotating mirror plate 12 with a fixed tongue to partition the back pressure applied to the rotating mirror plate 12 in the radial direction. Suction pressure or a pressure close to it acts on the space 21 on the outer side of the back pressure partition ring 20, and therefore suction pressure or a pressure close to it also acts on the back surface of the swiveling mirror plate 13. In addition, on the back side of the rotating mirror plate 12, there is a small gap 22 between the bearing and the component 19.
is provided.

FIGS. 2 and 3 are detailed cross-sectional views when the fixed spiral vane part 9 and the swirling spiral vane part 13 are engaged, and as shown in FIGS.
The groove bottom surface 23 of the spiral blade 11 and the rotating mirror plate surface 24 of the outer part
A step δ1 is provided between the fixed spiral blade component 9 and a step a2 between the spiral blade tip m125 of the fixed spiral blade component 9 and the outer circumferential surface 26 of the fixed blade frame 7. This step t1, J
2 is 11<δ2 in Figure 2, and IN>1 in Figure 3.
2, and when both spiral blade parts are combined, the tip of one or both spiral blades will always come into contact with the groove bottom of the opposite spiral blade. . Therefore, in this case, the swirling spiral vane part 1
There is always a minute gap 13 between the rotating mirror plate surface 24 of No. 3 and the outer peripheral surface 26 of the fixed blade frame 7 of the fixed spiral blade component 9.

As a result, during operation, the rotating mirror plate 12 and the fixed blade frame 7
The tip of one of the spiral vanes always comes into contact with the four bottom surfaces of the opposite spiral vane, and the gap in the uniaxial direction becomes almost 0, which greatly reduces leakage and greatly improves the performance of the compressor. improves. In addition, since suction pressure or a pressure close to it is acting on the outer circumference of the swivel head plate 12, leakage from the gap between the outer periphery of the swivel head plate 12 and the outer periphery of the fixed blade frame 7 will greatly impair performance. There is no need to lower the
If the tips of the spiral blades expand greatly due to pressure and temperature, resulting in excessive mechanical welding, this can be avoided by creating a small gap 22 (see FIG. 1) provided on the back of the rotating mirror plate. Therefore, not only the performance of the compressor is greatly improved, but also the reliability is sufficiently ensured.

Effects of Investigation As described above, according to the present invention, during operation, before the rotating head plate and the fixed blade frame come into contact with each other, the tip of the spiral blade and the opposite spiral blade are always connected. Contact with the bottom of the groove,
The axial clearance is almost O, and leakage is significantly reduced.
The performance of the compressor will be greatly improved. In addition, since suction pressure or a pressure close to it acts on the outer periphery of the swivel head plate, leakage from the gap between the swivel head plate and the fixed blade frame will not significantly reduce performance. If the tip of the volute vane expands greatly due to this, resulting in excessive mechanical contact, this can be avoided by the small gap provided at the back of the swivel head plate. Therefore, not only the performance of the compressor is greatly improved, but also the reliability is improved. It will also be necessary to ensure sufficient security.

Moreover, it is no longer necessary to provide a chip seal as in the conventional case, and the number of processing steps, processing cost, and compressor cost can be reduced.

[Brief explanation of the drawing]

Fig. 1 is a vertical cross-sectional view showing a scroll compressor according to an embodiment of the present invention, Figs. 2 and 3 are longitudinal cross-sectional views showing detailed examples of the compression mechanism, and Fig. 4 is a conventional compressor. FIG. 3 is a vertical cross-sectional view showing the mechanism. l...Airtight container, 2--Compression mechanism, 3--Electric motor, 6--Crankshaft, 7--Fixed blade frame, 8...
Fixed spiral vane, 9...Fixed spiral vane part, lO...
Compression space, 11--Swirling spiral vane, 12--Swivel head plate, 13--Swirling spiral vane part, 14--Rotation restraining part, 19--Bearing is a part, 22--Minute gap, 23-
- Groove bottom surface, 24... Turning mirror plate surface, 25... Tip surface, 26... - External surface, il, δ2 -... Step.

Claims (1)

[Claims] 1. A fixed spiral blade component having a fixed spiral blade in which an electric motor and a compression mechanism driven by the electric motor are disposed inside a closed container, and the compression mechanism is fixed or formed integrally with a fixed blade frame; A swirling spiral vane component in which a swirling spiral vane that engages with the blade and forms a plurality of compressed spaces is fixed or formed on a rotating head plate, a rotation restraining component that restrains the rotation of the swirling spiral vane component, and a rotationally restraining component that is rotationally driven by the electric motor. The rotating spiral vane component is configured to include a crankshaft that rotates eccentrically and a bearing component that supports the crankshaft, and a suction pressure or a pressure close to it is applied to a part or the whole of the outer circumference and back surface of the rotating head plate. , a slight gap is provided on the back surface of the rotating mirror plate, a step δ1 is provided between the bottom surface of the groove of the spiral blade of the rotating spiral blade component and the surface of the rotating mirror plate, and a tip surface and an outer peripheral surface of the spiral blade of the fixed spiral blade component are provided. A step δ2 is provided between the steps δ1, δ
2 is configured to be δ1<δ2 or δ1>δ2, so that when the two spiral blade parts are combined, the tip of one or both of the spiral blades is always in contact with the groove bottom surface of the opposing spiral blade. scroll compressor.