JPS60252187A - Rotary fluid machine - Google Patents

Abstract

PURPOSE:To prevent breakdown of a spiral member by employing specific shape for the inner and outer continuous curves to a spiral member at the fixed side while slightly setting back a portion of the inside curve when compared with conventional one thereby balancing the stress at the continuous curved sections of said curves. CONSTITUTION:The inside curve 702 of a spiral member 701 at the fixed side is formed into involute from the point F on the involute sufficiently at the outside to the point H corresponding with increase by DELTAbeta of the parameter beta, and retracted by slight gap DELTAC when compared with conventional one at the inside of the point H. Consequently, gearing will move gradually to the inside as it will revolve to gear the point H on the involute of the inside curve of the fixed side spiral member 701 with the point H' on the involute of the outside curve of the revolving side spiral member then both spiral members will revolve while being separated by the slight gap DELTAC. Since the arrow section and the pressure changeover point are separated, the pressure will balance at the arrow section resulting in reduction of the breakdown or abrasion of the spiral member.

Description

[Detailed description of the invention] [Industrial application field] The present invention relates to a rotary fluid machine.

[Conventional technology]

For example, in a known scroll compressor, one of two spiral bodies having the same shape, as shown in FIG.
is fixed to a seal end plate having a discharge port 4 approximately in the center, and both are rotated 180 degrees relative to each other, and the spiral bodies of both are fixed to a seal end plate having a discharge port 4 approximately in the center. , 52, 51', and 52'. and the other spiral body] is configured to revolve around the center O of one spiral body 2 with a radius ρ−〇〇′ without rotating on its own axis using a crank mechanism having a crank radius ρ. .

Then, between the two spiral bodies], there are points 5 ], , , 52 and points 5 ]' where both spiral bodies are white.
, 52' are formed with closed chambers 3, 3, and the volumes of the closed chambers 3, 3 gradually change as the spiral body 1 revolves.

In other words, from the state of (1) in the same figure, first transform the spiral body into 9
When it revolves 0", it becomes (2) in the same figure, when it revolves 180 degrees, it becomes (3) in the same figure, and when it revolves 270 degrees, it becomes (4) in the same figure.
During this period, the volume of small chamber 3 gradually decreases, as shown in the figure (
In 4), the two chambers 3°3 are connected to form a chamber 53,
If the figure revolves further 90 degrees from the state shown in figure (4), the same figure (')
), and the volume of the small chamber 53 is calculated from figure (2) to figure (3).
The volume decreases to the maximum volume between (3) and (4) in the same figure, and during this time, the outer space that began to open in (2) in the same figure expands to (3) in the same figure and (4) in the same figure. Moving from Figure (4) to Figure (1), new gas is taken in to form a closed chamber, and this process is repeated thereafter, and the gas taken in from the whirlpool outside the body is compressed and discharged from the discharge port 4. .

The above is the operating principle of a scroll type compressor. Specifically, as shown in the vertical sectional view of FIG. 6, the scroll type compressor has a housing 10, a front end plate 11.
Rear end plate 12. Consisting of a cylinder plate 13, an intake port 14 and a discharge port 15 on the rear end plate 12.
When protruding from the roof tile, the spiral body 252 and the disc 25
The main shaft 1 has a crank pin 23 fixed on the front end plate 11 and has a stationary scroll post 25 fixed thereon.
7 (see A in Fig. 6), and
As shown in (rix-w sectional view), the radial needle bearing 26. Boss 243 of the revolving scroll member 24. Square tube member 271. The revolving scroll member 2 consisting of the spiral body 242 and the disk 241 is rotated through the rotating mechanism consisting of the sliding body 291, IJ song material 2922, detent 293, etc.
4 is attached.

In this type of scroll compressor, the volume of the small chamber 53 gradually decreases, so that when high-pressure fluid is discharged from the discharge boat, the volume of the small chamber becomes zero due to the thickness of the spiral body. Instead, a so-called top clearance volume remains, and the high-pressure fluid in this top clearance volume is not discharged to the outside from the discharge port 4, but communicates with the small chambers 3, 3 again, so this top clearance volume The work done by the compressor on the fluid remains as ~
It will be a loss.

In order to solve this problem, the present inventors previously proposed a rotary fluid machine equipped with a spiral body as shown in FIG. 8 in Japanese Patent Application No. 57-06088.

That is, in the same figure, 501 is a fixed side spiral body,
601 and 602 are the outer and inner curves of the spiral body 501, respectively, where the outer curve 601 is the radius of the base circle, the involute curve to the starting point, and the EF of the inner curve 602 is out of phase with the outer curve 601 by an angle π-■. Tainbo I
The distance between J, - curve, and DE is a circular arc with a radius of approximately 60 mm.
1 and the inner curve 602 has a radius r
, and point A is the inbo of the outer curve 601),
-1- Starting point, point B is the boundary point between the outer curve 601 and the connecting curve 603, both curves make their respective tangents equal at this point, point C is a point well outside the outer curve 601, the point is inside At the boundary point between the curve 602 and the connecting curve 603, the radius R is
The two arcs of and r touch, point E is the inner curve 6020
Point F is the boundary point between the arc (between 'DE) and the involete curve EF, where both curves have equal tangents to each other, and is a point well outside the inner curve 602.

The same applies to the other revolution side spiral body 502.

In this case, the radii R+ and r are expressed by the following formula.

R=ρ+bβ+d... (3) r=bβ+d
...... 1---------(3) 2(---1-
bβ) β Niparameter.

The parameter β is equal to the angle between the straight line passing through the origin O and the negative ，
and straight line BO, are in contact with the base circle at the above-mentioned intersection.

That is, the parameter β gives the limit for the involute formation of the outer curve and the inner curve, and the involute formation limit points E and B are determined by the pavmeter β.

In general, the distance between EB and the spiral body is set appropriately so that the spiral bodies do not come into contact with each other, and the limits at which both spiral bodies come into contact with each other from the outer contact point are points E and E3, and the point E of the fixed spiral body is generally come into contact with point B of the spiral body on the revolution side, but from then on they are separated from each other.

[Problem that the invention seeks to solve]

However, in a compressor having such a spiral body 252°242, the difference between the low-pressure side pressure and the high-pressure side pressure is large (during high-load operation, the spiral body shown by the arrow in Fig. 5 (1) Since the rigidity of the inner tip is relatively small compared to the other parts, this part may be damaged.

Furthermore, in a machine designed so that both spiral bodies are in contact, the relative sliding rate of both spiral bodies at the inner part is relatively lower than that at the outer part, so that the area near the inner tip is On the other hand, in machines designed so that both spiral bodies are not in contact with each other, machining errors in the spiral bodies or assembly errors in both spiral bodies may cause abnormal contact between the two spiral bodies, resulting in the internal force inside the spiral bodies. There is damage to the tip ℃
- Abnormal wear may occur.

The present invention was proposed in view of the above circumstances, and an object of the present invention is to provide a high-performance rotary fluid machine that prevents abnormal wear and damage to the inner tip of the spiral body.

[Means for solving problems]

To this end, in the present invention, the stationary side spiral body and the revolving side spiral body, each consisting of a spiral body having substantially the same shape, are rotated by 80 degrees to mesh with each other, and the revolution side spiral body is rotated with a revolution radius ρ relative to the stationary side spiral body. The two spiral bodies are made to revolve around each other, and each of the spiral bodies has an outer curve made of an involute curve, an inner curve made of an involute curve having an arc of radius R inward, and the above outer curve and the above radius. If it is formed by a connecting curve with an arc of radius I'' that smoothly connects the arc of A very small gap was provided between both spiral bodies so as to separate them from a part or all of the contact between the curve and the connecting curve. + 1) β)' d = −−−−−−−−−−−−− 2(−+bβ) 1): A characteristic [effect] characterized by the base circle radius of the involute curve) In such a configuration, Accordingly, it is possible to prevent abnormal wear and damage of the inner tip of the spiral body and obtain a high-performance rotary fluid machine.

〔Example〕

An embodiment of the present invention will be explained with reference to the drawings. FIG. 1 is a front view showing the spiral body, FIG. 2 is a partial model diagram showing the pressure distribution at the tip of the spiral body in FIG. 1, and FIGS. FIG. 4 is a front view showing a modification of FIG. 1, respectively.

In the above figure, the same reference numerals as in Fig. 8 indicate the same members and dimensions as in the same figure.
601 is the fixed side spiral body according to the present invention, 601 is the outer curve,
603 are connection curves, each of which is the same as that in FIG.

702 is an inner curve, and the inner curve 702 is an involute sufficiently outward from point F to point H, which corresponds to β + Δβ, which is obtained by increasing parameter β by Δβ. It is made by retracting a slight gap ΔC from the inner curve 602 in FIG.

In other words, in Fig. 8, what is involute outside point E determined by the parameter β that gives the limit for involute formation is involute in Fig. 1, but in Fig. It is preferable that the area outside the H point corresponding to 2 is involute, and Δβ is 10 to 15 degrees or more.

Here, p p'j p'I-I + Q Q'±Q/
E, p.

p', Q, Q' are points on the base circle, and tangents to the base circle at points p', Q' are p'H, qE.

Note that point G is the intersection of the inner curve 702 and the connecting curve 603, and is provided between BD of the connecting curve 603, and point H' is the intersection of the outer curve 601 and the tangent that is tangent to the base circle from the point P, and is the connecting point. The radius r of the curve 6030 is the same as that in FIG. 8, and the spiral body on the revolution side is also the same as the spiral body on the stationary side.

When these two spiral bodies are interlocked and the revolution side spiral body is made to revolve, first, the invoice IJ of the inner curve of the fixed side spiral body,...) The outer curve of the revolution side spiral body corresponding to the outer point F on the curve The points on the involute mesh with each other, and the point H on the involute meshes with the point J-(' on the involute on the outer curve of the orbiting side of the spiral body, and then both spiral bodies revolve with a slight gap △C apart. do.

In other words, in the case of FIG. 8, there was engagement at points E and B determined by the parameter β of the limit for forming an inpolycoat, but in this example, the two spiral bodies separate by /\β before this point. Let's start.

In this S, before the two spiral bodies are separated, the inner curve 702 where the two spiral bodies are engaged is the connecting curve 60.
3, the part of the outer curve 601 near the connection curve 603, and the connection curve 603 are loaded with discharge pressure or a relatively high temperature and pressure Po. Outside the point where the inner curves mesh, a relatively low pressure p' is applied during compression.

A model of the state when the two spiral bodies begin to separate is shown in Figure 2 (B), and the hole in the figure is the 8th hole.
Shown in the figure.

That is, in Fig. 8, as shown in Fig. 2 (5), the pressure changes from p' to Po at point B near the arrow where the tip of the spiral body has relatively low rigidity. , in the present invention, the pressure changes at points H/, which are quite far apart, as shown in ) in FIG.

As a result, in Fig. 8, Po-P is located at the arrow part in Fig. 2 (8).
'' (ignoring the meshing force between both spiral bodies), stress is generated due to deformation, but in the present invention, the arrow part and the pressure turning point are far apart, so the same figure (B
), the stress at the arrow part is balanced and becomes much smaller, preventing damage to this part.

In addition, in the inner part of the spiral body, the relative slip rate between both spiral bodies is large, and the vicinity of the inner tip is likely to wear out, but in the present invention, both spiral bodies have a relative slip rate lower than that of the conventional one. Since they only engage up to the desired position, the amount of wear on the spiral body is also reduced.

Furthermore, in machines designed to be non-contact,
Processing error 1 Even if the two spiral bodies come into abnormal contact due to an assembly error, in the present invention, the abnormal contact will not occur at the inner tip, so damage or wear will not occur at the inner tip. be.

Furthermore, since the clearance ΔC is a small amount in the present invention, the advantages intended in Japanese Patent Application No. 57-206088 are not impaired (substantially exhibited, and a highly efficient machine can be obtained).

In addition, in the above-mentioned example, the following modification example can be considered.

(1) Instead of making both spiral bodies the same shape and disengaging with the parameter β0△β, one spiral body is set with the parameter β0△β, and the other spiral body is set with the parameter β+
Δβ' (Δβ to Δβ') may be shaped so that both spiral bodies separate from contact at different corresponding points.

(2) Instead of providing a gap △C on the inner curve, the third
This may also be provided on the outer curve 2, as shown in the figure.

In that case, the parameter β+△β A part of the outer curve from point H' on the outer curve.

The conventional 601 straddles the connecting curve and part of the inner curve
．． ．． An arbitrary curve 751 is constructed by providing a slight gap ΔC from 603 and 602, and the curve 751 and the inner curve 602 are
The position of the intersection point G between the dot and E may be appropriately selected between the dot and E.

By configuring both spiral bodies in this manner, substantially the same effect as that shown in FIG. 1 can be obtained.

However, in this case, the connection curve 603 is replaced by a curve 751 that is slightly drawn inward, so the rigidity of this part is slightly reduced.\In practice, since the gap △C is small, it may be adversely affected. There isn't.

(3) As shown in Figure 4, one spiral body has the same shape as Figure 8, and only the other spiral body has a point E determined by the parameter β, and a point outside B determined by the parameter β + Δβ. Shape 76 where a square gap △C is provided between H and H' so that both spiral bodies can be disengaged at H and I ('
It may be set to 1.

Note that instead of setting H and H' as corresponding points determined by the parameter β+Δβ, for example, the point H may be set to the parameter β+Δβ, and the point R may be set to the parameter β+Δβ' (Δβ to Δβ'). .

(4) The present invention can be applied to pumps, expanders, etc. in addition to scroll compressors.

〔Effect of the invention〕

In short, according to the present invention, the stationary side spiral body and the revolving side spiral body, each consisting of a spiral body having substantially the same shape, are arranged at 18 degrees from each other.

In a device in which the meshing spiral body is rotated so that it revolves around the stationary spiral body at a revolution radius ρ, both spiral bodies each have an outer curve consisting of an involito curve and an involute curve having an inward arc of radius approximately. When forming an inner curve with an arc of radius r that smoothly connects the outer curve and the arc with the radius of Determined by β + △β of 2
A slight gap was provided between both spiral bodies so that part or all of the inner curve and connecting curve between the points are separated from contact (by R-ρ+bβ+dr=bβ+db'-( -4bβ)' d Knee-11---□--- 2(-+1)β) b: Inbori, -1-Base circle radius of curve) High performance rotary type that prevents wear and damage Because you get a fluid machine,
The present invention is extremely useful industrially.

[Brief explanation of drawings]

FIG. 1 is a front view showing a spiral body according to an embodiment of the present invention;
FIG. 2 is a partial model diagram showing the pressure distribution at the tip of the spiral body shown in FIG. 1, and FIGS. 3 and 4 are front views showing modifications of FIG. 1, respectively. FIG. 5 is an operational diagram of a known scroll compressor, FIG. 6 is a vertical sectional view showing a known scroll compressor, and FIG. 7 is a cross sectional view taken along the line ■-■ in FIG. 6. FIG. 8 is a front view showing the spiral body proposed in Japanese Patent Application No. 57-206088. 601...Outer curve, 602...Inner curve, 603
... Connection curve, 701 ... Fixed side spiral body, 70
2...Inner curve, 751.761...Connection curve, r, R...Radius, b...Base circle of involute curve, △C...Gap, β, △β...Parameter, Sub-Agent Patent Attorney Masa Tsukamoto Figure 7 Figure 2 (A> Figure 3 AY Figure 4 Figure 5 (1) (2) Figure 6 0 Figure 7 2q1 Figure 8

Claims (1)

[Scope of Claims] The stationary side spiral body and the revolving side spiral body, each consisting of a spiral body having substantially the same shape, are rotated by 80 degrees to mesh with each other, and the revolution side spiral body revolves with the revolution radius ρ with respect to the stationary side spiral body. In such a device, each of the spiral bodies has an outer curve made of an involute curve, an inner curve made of an in-poly curve having an arc of radius R inward, and the outer curve and an arc of the radius R. If it is formed by a connection curve having an arc of radius r that smoothly connects the two, the in-poly is determined by the parameter β. ,
- A very small gap was created between both spiral bodies so that part or all of the inner curve and connecting curve between the two points determined by β + △β, which is slightly outward from the limit point for establishing the curve, are separated from contact. A rotary fluid machine characterized by the following (R = ρ + bβ d r = bβ + d b' - (-+I) β)' b: base circle radius of an involute curve).