JP2990907B2 - Scroll compressor - Google Patents

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 a cooling device such as a cooling and heating system or a refrigerator.

[0002]

2. Description of the Related Art The blade shape of a conventional scroll compressor is similar to that of a swirling spiral blade 102 described in Japanese Patent Application Laid-Open No. 1-216091 (FIG. 7) except for the spiral portion except for the winding start portion at the center. The blade had a uniform involute curve up to the end and had a uniform blade thickness t.

[0003] Further, the blade height is constant H from the start of winding to the end of winding.

[0004]

In the above prior art, there is a problem that the strength of the end portion of the spiral is lower than that of other portions because the thickness of the spiral blade is uniform over the entire blade. In other words, since the blades are configured with a uniform involute curve, one of the blades may come into contact with the wall surface of the other blade due to the large centrifugal force acting on the swirling spiral parts during operation at a high rotation speed. However, if the contact happens to occur at the end of the winding of the blade, the blade is damaged.

[0005] Further, since the blade height is constant from the start of winding to the end of winding, one of the blades may be subjected to temperature distortion or pressure distortion under special pressure and temperature conditions such as defrosting operation. The tip of the blade in the axial direction slides in contact with the end plate of the other spiral part, and as a result, a problem has occurred in that the end part having a weak strength is damaged.

[0006]

In order to achieve the above object, according to the present invention, a fixed swirl vane or a swirl swirl vane is provided.
Decrease the blade height at the end of the winding step by step
Or, the tip of the end of one spiral blade is opposite to the other.
The thickness of the end plate of the spiral part
I have.

[0007]

[0008]

The operation of the above means is as follows. Wings at the end of fixed or swirling swirl vanes
Only the root height may be reduced slightly in steps, or
The other spiral part where the end of the winding end of one spiral blade is opposite
The thickness of the end plate has been reduced slightly step by step.
The actual clearance at the tip of the blade in the axial direction is
Performance during normal operation may vary
During operation under special pressure and temperature conditions
Even if temperature distortion or pressure distortion occurs in the product, the end of the spiral blade end
The part does not slide on the end plate of the spiral blade
To prevent blade damage due to axial contact.
You.

[0009]

[0010]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 6 show one embodiment of the present invention. The scroll compressor shown in these figures includes a revolving spiral part 1 and a fixed spiral part 5. Swirling spiral parts 1
Is provided with a spiral (in this embodiment, an involute curve) swirling spiral blade 3 on one side of a disk-shaped end plate 2.
Is provided with a driven shaft 4 on the other side. Fixed spiral parts 5
Is provided with a fixed spiral blade 7 on the end plate 6, the spiral direction of which is opposite to that of the swirling spiral blade 4. Further, a discharge hole 8 is provided at the center of the end plate 6, and near the outer peripheral portion of the end plate 6. Has an inlet 9. The scroll compression unit is configured by meshing the two orbiting spiral blades 3 and the fixed spiral blade 7 with a phase shift of 180 degrees, and includes a plurality of compression chambers 10. Also,
In the scroll compressor, there are a radial gap and an axial gap as a leakage path of the compression chamber 10, but in order to minimize leakage of the refrigerant gas during compression, these two gaps are set to be extremely small. .

[0011] In the embodiment of the present invention, dropped by a thickness [delta] _r the inner wall surface of the winding end portion 301 of the orbiting wrap element 3 as shown in FIG. 2, the blades of winding end portion 301 thickness (te)
Is thinner than the other part (t). That is, te = t−δ
The relationship is set to _r . When the scroll compressor is operated at a high rotational speed, a centrifugal force that increases in proportion to the square of the rotational speed acts on the orbiting spiral component 1, and the centrifugal force causes the orbiting radius of the orbiting spiral component 1 to be reduced by a bearing clearance (for example, a bearing gap). , And slightly increases in the bearing gap of the driven shaft 4). Due to the effect of increasing the turning radius, the turning swirl blade 1 and the fixed swirl blade 7
The gap in the radial direction disappears, and the wall surfaces of the two blades may come into contact with each other at any place. However, in the present embodiment, since the dropped internal wall surface only [delta] _r of the orbiting wrap element 1 of the winding end portion 301, it will never happen that the winding end portion 301 contacts the wall surface of the fixed wrap element 7 of the mating . In general, the end portion of the spiral blade is partially cut off, so that the spiral blade is weak in strength. However, by this means, it is possible to avoid contact with the blade wall surface at the end portion of the spiral blade, thereby preventing breakage of the blade.

In FIG. 2, the shape of the inner wall of the winding end portion 301 is gradually increased toward the outermost end. According to an experiment, when the height of the blade H, the blade thickness and t, the length A of the inner wall down portion, drop amount [delta] _r of the outermost end next value is appropriate.

A = (2-3) × H δ _r = (3/1000 to 10/1000) × t FIG. 3 shows an embodiment in which only the outermost end of the winding end portion 301 has the inner wall largely dropped. Is shown. The shape shown in FIG. 3 does not significantly reduce the strength of the winding end portion 301, and has the same effect as the shape shown in FIG.

Here, B = (0.5-1) × H is an appropriate value. The means for avoiding the contact with the end wall surface of the blade end is not limited to the above-described method, and as shown in FIG. 4, the other approaching the inner wall surface of one blade (rotating spiral blade 3). It is dropped outer wall surface of the blade (fixed wrap element 7) by [delta] _r, obtained exactly the same effect. In Figure 4, it is subtracted [delta] _r by the thickness over the length A swirl swirl vane winding end equivalent 701 of the fixed wrap element 7.

On the other hand, FIG. 5 shows a stepped shape of the axial end surface of the winding end portion 301 of the swirling spiral blade 3. Generally, in a scroll compressor, the effect of the blade tip clearance on performance is one order of magnitude higher than the radial clearance, and therefore,
The blade tip clearance is set to a minimum (partial contact) during assembly. However, the pressure and temperature acting on the two spiral components vary, and the tip surface may slide in contact due to the resulting pressure and temperature distortions. As described above, since the strength of the winding end portion of the blade is weak, if the axial end surface of the blade repeats strong contact, the blade is damaged from the winding end portion 301. The stepped shape of the axial end surface of the winding end portion 301 shown in FIG. 5 prevents this breakage,
It protects the swirl vanes from pressure distortion and temperature distortion under various operating conditions. According to an experiment, when the height of the blade and H, paragraphs and director of A, B, paragraph and the amount [delta] _a has the following values are appropriate.

A = (2 to 3) × H, B = (0.5 to 1) × H δ _a = (1/1000 to 3/1000) × H In this manner, only the end of the winding end 301 has the height of the blade. Even if the height is reduced, the leakage of the refrigerant from this portion is small, and the performance is hardly affected.

The means for avoiding axial contact of the end of one of the blades (the swirling spiral blades) is not limited to the above-described method, and the thickness of the end plate of the other blade (the fixed spiral part) may be reduced. Exactly the same effect can be obtained even with the reducing means. FIG. 6 shows this distal end surface that faces the portion of the winding end portion 301 of the orbiting wrap element 3 (swirl spiral vanes, the winding end portion distal end face opposite face 702) [delta] _a only of the end plate 6 The thickness has been reduced.

[0018]

According to the present invention, a fixed spiral blade or
Only the blade height at the end of the winding of the swirling spiral blade is slightly reduced in steps.
Decrease or decrease the end of one spiral blade
The thickness of the end plate of the other spiral part whose end is opposite
It is slightly reduced, and the actual blade
Since the axial tip clearance is not increased,
During operation, the performance remains unchanged and special pressure
Temperature and pressure distortions occur in spiral components during operation under temperature conditions
However, the end of the end of the spiral blade is the mirror of the opposing spiral blade
No longer slides in contact with the plate.
The effect that breakage of the blade does not occur is obtained.

[0019]

[Brief description of the drawings]

FIG. 1 is a sectional view of a main part of a scroll compressor according to an embodiment of the present invention.

FIG. 2 is a perspective view of the main part.

FIG. 3 is a perspective view of the main part.

FIG. 4 is a plan view of the main part.

FIG. 5 is a perspective view of the main part.

FIG. 6A is a plan view of the main part, and FIG. 6B is a sectional view of the main part.

FIG. 7A is a plan view of a swirling spiral part of a conventional scroll compressor, and FIG.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 swirl spiral part 3 swirl spiral blade 5 fixed swirl part 7 fixed spiral swirler 301 end-of-turn part 701 part corresponding to end part of swirl-spiral blade end 702 surface facing end face of end of swirl-spiral blade end

──────────────────────────────────────────────────の Continuing on the front page (72) Inventor Sadao Kawahara 1006 Kadoma Kadoma, Osaka Pref. Matsushita Electric Industrial Co., Ltd. (72) Inventor Manabu Sakai 1006 Odakadoma Kadoma, Osaka Pref. Matsushita Electric Industrial Co., Ltd. (72) Inventor Yasushi Aiba 1006 Kadoma, Kadoma, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. (72) Inventor Shuichi Yamamoto 1006 Odaka, Kazuma, Kadoma, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. (72) Inventor Masahiro Tsubokawa 1006 Kadoma, Kazuma, Osaka Prefecture Matsushita Electric Industrial Co., Ltd. (72) Inventor Nobuyoshi Kojima 1006, Kadoma Kadoma, Kadoma City, Osaka Prefecture Matsushita Electric Industrial Co., Ltd. (56) References JP-A Hei 3- 264789 (JP, A) JP-A-2-264178 (JP, A) (58) Fields investigated (Int. Cl. ⁶ , DB name) F04C 18/02 311

Claims (2)

(57) [Claims] 1. A plurality of compression spaces are formed by engaging a fixed spiral component having a fixed spiral blade on an end plate with a swirling spiral component having a swirling spiral blade on an end plate to rotate the rotating spiral component. A scroll compressor that moves the compression space toward the center of the spiral while reducing the volume by preventing rotation and performing only swirling motion, wherein the fixed spiral blade and the spiral spiral blade are arranged. Is the axis
In order not to contact in the same direction, the blade height at the end of the winding of the fixed spiral blade or the swirling spiral blade is slightly reduced in a stepwise manner, or the end of the winding end of one spiral blade is opposed to the other. A scroll compressor in which the thickness of the end plate of the spiral part is slightly reduced stepwise. 2. The height of the blade is H, the length of the section is A, B,
When the .delta.a paragraph and amount, claims and characterized in that the A = (2~3) × H B = (0.5~1) × H δa = (1 / 1000~3 / 1000) × H Item 1 scroll compression
Machine.