JPS60145474A - Scroll-type fluid machinery - Google Patents

Abstract

PURPOSE:To obtain a scroll-type fluid machine having a low vibration by making the pressure distribution symmetrical by forming a band-shaped concaved part shallower than the depth of the groove in the lap part along the lap in the region on the winding end side of the lap of a fixed scroll member. CONSTITUTION:In the region ranging from the winding end part 1b' of the lap 1b of a fixed scroll member 1 to the winding end part 2b' of the lap 2b of a swirling scroll member 2, a band-shaped concaved part 16' is formed along the lap 1b. Said concaved part 16' communicates to a relief part 16 and is under the equal pressure to that of the relief part 16, and the depth is less than that of the groove in the lap part. Therefore, the distribution of gas pressure is symmetrical, and the vibration generated by the biased gas pressure can be suppressed.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to scroll-type fluid machines such as scroll compressors, scroll expanders, and scroll pumps.

[Background of the invention]

1 and 2 show a conventional scroll fluid machine. The stationary scroll member 1 consists of an end plate 1a and a spiral wrap 1b standing upright on the end plate 1a. The orbiting scroll member 2 consists of an end plate 2a and a wrap 2b similar to the stationary scroll member 1. Both scroll members 1
．． The wraps lb and 2b of 2 are formed into an involute or a curved line approximating it, and have a uniform thickness and a uniform height.

A boat 3 is located at the center of the end plate 1a of the stationary scroll member 1.
is provided, and another boat 4 is provided on the outer peripheral side. The boat 3 serves as a discharge boat for a compressor, and serves as an inflow boat for an expander.

The boat 4 is a suction boat in the case of a compressor, and a discharge boat in the case of an expander.

A scroll pin 2C is provided to protrude from the back surface of the orbiting scroll member 2.

Both scroll members 1 and 2 are engaged with each other with their wraps lb and 2b facing inside. In this state, each lap lb,
The winding end ends 1b' and 2b/ of 2b are #'l[
It is located at a distance of '180'.

The frame 5 is fixed to the outer periphery of the end plate 1a of the stationary scroll member 1 with several bolts.

The crown shaft 6 has two bearings 7 attached to the frame 5,
8 and is rotatably supported by the frame 5. A balance weight 9 is integrally formed on the crown shaft 6. The balance weight 9 may be separate from the crankshaft 6.

A boss hole 10 is formed in the head of the crankshaft 60. The boss hole 10 has its center at a position centered by a distance ε (turning radius) from the axis 0 of the crankshaft 6.
0 has a scroll pin 2C fitted therein. A needle bearing 1 is installed between the boss hole 10 and the scroll pin 2C.
1 is provided.

The rotation prevention member consists of a ring 12 and an Oldham key 13, and the back surface of the end plate 2a of the orbiting scroll member 2 and the frame 5.
is established between. The ring 12 has linear grooves (not shown) on the surface facing the end plate 2a and the surface facing the frame 5. The groove provided on the surface facing the frame 5 is orthogonal to the groove provided on the surface facing the end plate 2a.

In the groove provided on the surface facing the frame 5, the frame 5
The Oldham key 13 fixed to the end plate 2a is fitted into the end plate 2a.
An Oldham key (not shown) fixed to the end plate 2a is fitted into a groove provided on the surface facing the end plate 2a.

The mechanical seal 14 is provided at a portion where the crankshaft 6 penetrates the frame 5 and projects to the outside, and is housed in a seal housing 15. This mechanical seal 1
4 uses a publicly known structure, so the explanation of the structure will be omitted.

When the crankshaft 6 is rotated clockwise in FIG. 1 by a prime mover (not shown), the orbiting scroll member 2
rotates clockwise relative to the stationary scroll member 1 without changing its attitude (apparently not rotating). As a result, a closed space Vr formed between both scroll members II2
, Vz, while turning clockwise, the closed space Vt, v
The volume of s is reduced, the fluid taken in from the boat 4 is compressed, and the fluid is discharged from the boat 3.

On the other hand, when the orbiting scroll member 2 rotates counterclockwise, the volume of the closed spaces Vl and V2 gradually increases while rotating in the opposite direction to the above, and the high temperature and high pressure (
The gas (which is at high temperature and pressure relative to what is being discharged from the boat 4) expands and is discharged from the boat 4. At this time, power is generated in the crankshaft 6. Wrap lb, the number of turns of 2b is 1
．． If you set it to 5 and make sure that there is no change in the volume of the closed space,
Becomes a pump.

In such a configuration, the lamp 1 of the stationary scroll member 1
A relief 16 is provided over a range of at least 180°, preferably 200' from the winding end 1b' of the winding end 1b' of the winding end 1b'. However, the outer periphery of the remaining part in the range of 180' or 160' is connected to the wrap 1b of the stationary scroll member 1, and the pressure of the fluid leaking from the chamber at the back of the orbiting scroll 2 and the low pressure chamber are The pressure is between the two. For this reason, the pressure distribution was not point symmetrical, and an unbalanced axial force acted on the orbiting scroll 2, making it impossible to obtain normal orbiting motion of the orbiting scroll 2.

In another conventional example (FIG. 3), the wrap 2b of the stationary scroll member 2 and the wrap 2b of the orbiting scroll member 2 are
BL has the same shape over the entire circumference, and the above-mentioned end plate part is configured to have no fitting part. In this configuration, since the thin stationary scroll end plate 4a occupies a large proportion, one stationary scroll member is deformed in the axial direction due to the pressure of the gas acting on the compressor formed by both scroll members 1 and 2. , the axial gap in the central working chamber increases, gas leakage increases, and efficiency decreases. Furthermore, in order to suppress deformation, reduce the axial gap, and obtain higher efficiency, the thickness of the end plate must be increased, which causes an increase in weight.

[Purpose of the invention]

An object of the present invention is to provide a compressor with low vibration, small amount of vibration, and high efficiency.

[Summary of the invention]

A feature of the present invention is that a concave portion shallower than the groove bottom of the wrap portion is formed in the region of the cylindrical portion of the stationary scroll member on the end side of the ramp winding.

(7) Another feature is that a lip-shaped partition wall is formed in a band-shaped recess formed outside the range from the end of winding to 180' on the outermost periphery of the spiral of a stationary scroll member. This is because we have established

By doing this, the inside of the recess has the same pressure υ as the low-pressure part, and the pressure distribution becomes substantially point symmetrical, and since the recess has higher rigidity than the end plate, the axis acting on the working chamber The deformation in the axial direction due to the direction scar can be suppressed to a small level.

[Embodiments of the invention]

An embodiment of the present invention will be described below with reference to FIGS. 4, 5, and 6.

Winding end 1b' of the wrap 1b of the stationary scroll member 1
A relief 16 is provided at a half-circumferential portion of the scroll member 2 so as not to impede the orbiting movement of the orbiting scroll member 2, and in the case of a compressor or an expander, it serves as a passage for low-pressure gas. The remaining half circumference portion, that is, the wrap 1b of the stationary scroll member 1
In the region from the winding end 16' of the orbiting scroll member 20 wrap 2b to the winding end 2b' of the wrap 2b (the region on the winding end (8) side of the wrap 1b), there are four band-shaped parts 16 along the ramp 1b.
′.

This four part 16' communicates with the part of the relief 16. Further, the depth of the recessed portion 16' is shallower than the groove depth of the ramp portion,
It is formed.

In this way, since the cylindrical portion IC of the stationary scroll member 1 has a recess 16' communicating with the relief 16 in the area on the end of winding of the wrap 1b, this recess has almost the same pressure as the relief 16. C, stationary scroll member 10 cylindrical portion I
Inside C, the gas pressure distribution becomes approximately point symmetrical. Therefore, a point-symmetrical pressure acts on the orbiting scroll member 2 facing the stationary scroll member 1, and vibrations caused by uneven gas pressure can be suppressed.

Further, since the depth of the recess 16' is shallower than the relief portion 16, the thickness of the bottom surface of the recess is greater than that of the relief portion 16', and the amount by which the stationary scroll on the recess side is deformed in the axial direction due to pressure is small. In addition, the rigidity of the entire stationary scroll increases, so
The overall axial deformation (9) can be kept small.

Furthermore, if the rigidity of the stationary scroll member on the side where the recessed portion 16' is provided is equal to that on the side where the relief portion 16 is provided as shown in FIG.
Since the overall thickness of the IC can be made smaller than that of the IC on the side where the relief portion is located, the weight can be reduced by reducing the thickness.

FIG. 7 shows another embodiment of the present invention.

The recess 16' is defined as an opening IKFJ, and the curve K
F and IJ are concentric arcs. Stationary scroll member 1
The outer imporute curvature of the lap 1b is up to 1d, and the curve 1dIJ can be any curve, so especially the curve I
This embodiment differs from the previous embodiment in that J is an arc.

This has the effect of simplifying the machining of the recess 16'.

FIG. 8 shows yet another embodiment of the invention.

Winding end 1b' of the wrap 1b of the stationary scroll member 1
A lip-shaped partition wall 17 that divides the recess 16' is provided in a part of the band-shaped recess formed on the outside of the range from 180° to 180°.

The partition wall 17 includes the wrap 1b of the stationary scroll member and the mirror plate 1a.
It is designed to connect. The portion other than the partition wall is a recess 16' and a recess 16''.
The depth of 6" may be the same depth as the scroll wrap groove or the relief 16, or may be shallower. Also, the height of the lip 17 is from the bottom of the recess to the tip of the ramp section. It may be equal or may be smaller. According to the present invention,
The stationary scroll member 1 on the side where the recess 16' is provided is
The rib-shaped partition wall 17 increases the rigidity, and the deformation of the entire stationary scroll member due to gas pressure can be suppressed to a small extent, so that gas leakage from the axial clearance is reduced and a highly efficient fluid machine can be obtained.

〔Effect of the invention〕

As described above, according to the present invention, a band-shaped recess is provided along the lap in the region of the stationary scroll member on the end side of the lap, and the groove depth of the lap portion is shallower, so that the pressure distribution can be improved. (11) It is possible to provide a scroll-type fluid machine that is symmetrical and has low vibration. Furthermore, since the rigidity of the stationary scroll member on the side provided with the recess is increased, it is possible to provide a highly efficient scroll-type fluid machine with less axial deformation of the stationary scroll member due to gas pressure and less gas leakage.

[Brief explanation of the drawing]

Fig. 1 is a cross-sectional plan view of a conventional scroll fluid machine, Fig. 2 is a cross-sectional view taken along the line I-I of Fig. 1, and Fig. 3 is a cross-sectional view of a conventional scroll fluid machine.
FIG. 4 is a sectional plan view of two conventional examples. 5 and 6 are views of one embodiment of the invention, FIG. 7 is a sectional plan view of another embodiment, and FIG. 8 is a sectional plan view of another embodiment. DESCRIPTION OF SYMBOLS 1... Stationary scroll member, 2... Orbiting scroll member, la, 'l, a, one end plate, lb, 2b--
・Wrap, 3° 4...Boat, 5...Frame, 6
...Crankshaft, 7゜8...Bearing, 9...Balance weight, 12...Rotation prevention member, 13...Oldham key, 14...Mechanical (12) ￥J 1st Z diagram Figure 3 A No. 4 No. 7 No. 8 B

Claims (1)

[Claims] 1. Two scroll members having an end plate and a helical wrap formed upright thereon are engaged with each other, and one orbiting scroll member is connected to the other stationary scroll member. In a case where the stationary scroll member orbits so as not to apparently rotate relative to the scroll member, and the stationary scroll member has a cylindrical part on the outside of the ship with the same height as the wrap height, the stationary scroll member in the cylindrical part A recess f7 is formed along the wrap of the stationary scroll member in a region from the end of the lap winding to a position near the end of the ramp winding of the orbiting scroll member, and the depth of the recess is , a scroll fluid machine characterized in that the depth is shallower than #4 depth of the lap portion. 2. The scroll fluid machine according to claim 1, wherein the curve defining the inner boundary of the four parts is a circular arc. 3. The scroll fluid machine according to claim 1, wherein the curve defining the inner boundary of the recess is a circular arc. 4. The scroll fluid machine according to claim 1, wherein the curve defining the inner boundary of the recess is formed of the same involute as the ramp. 5. The scroll fluid machine according to any one of claims 1 to 4, further comprising a partition wall that divides the recess into a plurality of parts.