JPS59126096A - Rotary scroll member driving mechanism in scroll type compressor - Google Patents

Abstract

PURPOSE:To prevent the generation of an abnormal high pressure and the damage of a scroll body due to the generation of the same by a method wherein an eccentricity of a rotary scroll member is decreased when the rotary scroll member is in a condition contacting with a fixed scroll member. CONSTITUTION:The resultant force of the Fg2 of gas in a compression chamber C, which is pushing a rotary scroll member 12, and the force Fg2 of an eccentric shaft 8, which is pushing the rotary scroll member 12, is the force Fo2. The resultant force Fo2 effects into the direction of decreasing the eccentricity (e) of the rotary scroll member 12. Accordingly, the rotary scroll member 12 is separated from a fixed scroll member 17 and liquid, enclosed in the compression chamber C, may escape to the sides of suction and delivery and prevents the generation of the abnormal high pressure, therefore, the damage of the scroll body may be prevented.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention is characterized in that the thin winding body of the fixed scroll member and the spiral winding body of the movable scroll member are eccentrically engaged, and the spiral winding body of the movable scroll member is caused to revolve so that a thin winding body of the movable scroll member is formed between the two spiral winding bodies. This relates to a drive mechanism* for a movable scroll member in a scroll compressor that moves a closed compression chamber toward the center while reducing its volume and discharges compressed fluid from the center.

In a scroll compressor, a sealed compression chamber is formed between the line contact portions of two mutually meshed thin windings, and the relative circular orbital movement (and thus the line contact) of the scroll members is As the compression chamber moves toward the center along the spiral surface (this causes the compression chamber to move toward the center while decreasing its volume and compress the fluid, the sealing force at the line contact area increases. However, if the contact force is increased to ensure this seal, wear will occur on the thin coil, so in order to provide an appropriate sealing force, the contact force of the three spiral coils should be increased. However, this contact force cannot always be kept constant due to dimensional errors in manufacturing the spiral wound body, and reducing the dimensional error makes manufacturing difficult.

” - In order to eliminate the defect mentioned above,
A scroll type compressor shown in Japanese Patent No. 91 was proposed. In order to absorb the dimensional tolerances of each component, this compressor is designed to vary the amount of eccentricity between the rotating shaft and the movable scroll member eccentrically attached to the rotating shaft within a certain range. During the compression operation, due to the reaction force of the compressed gas pressure, the rotating scroll part was moved in a direction G to increase the amount of eccentricity, so as to maintain a seal at the line contact part of the spiral wound body.

However, in the conventional scroll type compressor described in item 1, when liquid compression occurs, the movable and fixed thin windings can separate, and the suction chamber and discharge chamber (the compression chambers that are not communicated with each other can generate abnormally high pressure). There was a risk that the spiral body etc. would be destroyed.

The present invention has been achieved in order to eliminate the above-mentioned conventional deficiencies, and its purpose is to maintain proper sealing between the movable and fixed spiral bodies during normal compression operation, and to When compressed or foreign matter gets caught (in this case, the amount of eccentricity of the movable scroll member can be reduced to prevent abnormally high pressure from occurring and damage to the spiral body, and the dimensional tolerances of each part can be relaxed. To provide a drive mechanism for the movable scroll member in a scroll type compressor.

An embodiment embodying the present invention is shown in FIGS. 1 to 9 (
To explain further, the left end Q of the center housing 1 is connected to the front housing 2 by a plurality of bolts (not shown).
A rear housing 3 is integrally provided at the right end Q of the center housing 1.

A cylindrical boss portion 4 is integrally formed in the center of the front housing 2, and a pair of left and right radial ball bearings 5 (a rotating shaft 6 is supported by the central hole 4a).
Connected to a drive source at the outer end. Further, a shaft seal mechanism 7 is interposed between the rotating shaft 6 and the boss part 4, and communicates with the upper part of the seal chamber S that houses this seal mechanism 7 (this is the upper part of the proximal end of the boss part 4). is provided with a refrigerant gas introduction hole 4b.

An eccentric shaft 8 is connected to the inner end of the rotating shaft 6, and on this eccentric shaft 8, a balancer 9 shown in FIG. (This is supported. The balancer 9 and the bush 1o are connected by a Q-coupling pin 11 so as to integrally rotate relative to each other around the eccentric shaft 8. The engagement recess 6a, which serves as a stopping means in the present invention, is recessed in the center of the inner end surface of the rotating shaft 6, and the bushing 10 is loosely engaged with the engaging recess 6a, which serves as a stopping means in the present invention. (It is designed to be able to rotate within a very small width (for example, one horse).

A boss portion 12b integrally formed at the center of the back surface of a circular base plate 12a constituting the rotating scroll member 12 is rotatably supported on the bush 10 via a radial needle bearing 13 or a plain bearing. A spiral body 12c is integrally formed on the front surface of the substrate 12a of the rotating scroll part 12, as shown in FIG.

On the other hand, an annular locking step formed at the joint between the center housing 1 and the front housing 2 (this means that the outer periphery of the fixing ring 14 that prevents the rotation of the rotating scroll member 12 cannot be rotated by the key 15 (3). A suction chamber A is formed on the front housing 2 side with this fixing ring 14 as a boundary, an operating chamber B is formed on the center housing 1 side, and a suction chamber Al is formed on the front housing 2 side. Refrigerant gas is introduced from the external circuit through the suction port 2a, which is provided through the upper part of the outer periphery of the fixing ring 1.
The outer part Q of 4 is shown in Figure 2 (as shown here, the suction passage 14
The refrigerant gas is introduced from the suction chamber A to the working chamber B by providing a plurality of holes (in this embodiment, there are four small holes, but many small holes may be provided).

On the back surface of the substrate 12a of the rotating scroll member 12, a guide groove 12d for preventing rotation in the vertical direction O passing through the center is carved, as shown in FIG. As shown in Fig. 1.2.5, a guide groove 14b for preventing rotation is carved in the left-right direction.The guide groove 12d has a square annular shape as shown in Fig. 5Q. The anti-rotation ring 16 is fitted so as to be relatively slidable in the vertical direction, and the anti-rotation ring 16 is also fitted in the guide groove 14b so as to be slidable in the left-right direction as shown in Fig. 2Q. (·reactor.

Therefore, the rotation shaft 6 causes the eccentric shaft 8 and the bush 10 to
is rotated, for example, 90 degrees counterclockwise in FIG. 2 while drawing a constant circular locus, the first
The anti-rotation ring 16 is connected to the guide groove 14 of the fixed ring 14.
b (Since this is restricted, the rotation prevention ring 16 is moved straight (parallel) to the left along the guide groove 14b, so that the guide groove 12d of the substrate 12a is also held in the same direction upward and downward, and the rotating scroll member 12 is prevented from rotating.

A locking step formed by the center housing 1 and the rear housing 3 (this is a locking stepped portion in which the outer peripheral edge of the thick circular base plate 17a constituting the fixed scroll portion 17 is not rotatable and in the radial direction The front surface of the board 17a is shown in FIG. The two are integrally fixed so that they are in contact with each other.

Also, a discharge passage 17c is provided through substantially the center of the substrate 17a, through which compressed refrigerant gas can be discharged into a discharge chamber formed by the substrate 17a, the rear housing 3, and the Q. This discharge passage 17c is closed by a discharge valve 19 whose position is regulated by a retainer 18 within the discharge chamber. The bottom of the discharge chamber (this is where the discharge port 3a is transparent).

Therefore, due to the eccentric shaft 8, the thin wound body 12c of the rotating scroll member 12 is rotated by the spiral wound body 1 of the fixed scroll member 17.
It revolves clockwise in Figure 3 while locally contacting 7b (
When the rotating scroll member 12 and the fixed scroll member 17 are rotated with relative angular movement prevented,
The wire contact portion of both spiral winding bodies 12c and 17b is thin winding body 17b.
As a result, the airtight compression chamber C formed by the two contact parts gradually compresses the taken-in refrigerant gas and moves toward the center, and from the discharge passage 17c. It is discharged into the discharge chamber and is forced into the external circuit through the discharge port 3a.

Next, two drive mechanisms for the movable scroll member 12 of the present invention will be described in detail.

As mentioned above, the front end of the connecting pin 11 is loosely engaged with the retaining portion 6a of the rotating shaft 6, and the bushing 10 can swing a small distance around the eccentric pin 8. Thin winding body 17b of fixed scroll member 17
On the other hand, the spiral body 12c of the rotating scroll member 12 makes contact and separation within a very small width. and,
This is done to absorb dimensional tolerances of each member, to prevent foreign matter from escaping when trapped, and to prevent abnormally high pressure when compressing liquid.

In addition, in this embodiment, as shown in FIG.
The center of the connecting bin 11 is made substantially coincident with the center of the bushing 10 and the center Oc of the rotating scroll member 12 attached to the bushing 104 is made coincident with each other. The distance between the center Os and the center Op of the eccentric shaft 8 is 0.
sOI) is set larger than the distance OsOc between the centers Os and Oc, and the distance dsop is set thicker than the distance OcOp between the centers Oc and the center Op.

By the way, the present invention is designed so that the amount of eccentricity of the rotary scroll member 12 can be changed by a minute width (the drive unit for the scroll member 12 is composed of one piece, and either the rotary scroll member 12 or the fixed scroll member 17 (in a state in which they are in contact with each other) The gist is to set the angle θ0 on the acute side formed by the straight line 0sOc and the straight line ocop using the following formula, which will be detailed later, under the condition that the compression ratio ε is 8≦ε≦17. It is.

Therefore, the above equation will be analyzed (the process that led to this will be explained).

First, considering the two forces that act on the rotating nuclear member 12, when a compression operation is performed, the gas compression reaction force F that the rotating nuclear member 12 receives is as shown in Figure 6. , the following two (divided into:

Ft; tangential force Fr; radial force The tangential force Ft is the theoretical gas compression power N (kq・C
m/5ec), where: V ; Suction volume (cnr"/rev) n ; Rotational speed (r-p-
m) Ps; suction pressure (kg/oR) (absolute pressure) Pd;
Discharge pressure (kg/oft) (absolute pressure) K: When K is an adiabatic index, the compression power N is expressed by the following equation.

Further, if the distance from the center Os of the rotating shaft 6 to the center OC of the rotating scroll member 12 is the eccentricity e (cyn), then from the above equations (t) and (2), the tangential force F is
t becomes.

On the other hand, in the case of a scroll compressor, A; base circle radius β of the spiral; inner wall line delay angle α of the spiral; winding angle H of the spiral; height of the spiral. The maximum volume V and eccentricity e of the two compression chambers C formed by the windings 12c and 17b are generally expressed as follows.

V = 2 rr A (yr-β) (2α-3yr
-β)H---(4)e=A(π-β)
...(5) From the above formulas (3) to (5), Ft
becomes as follows.

...(6) On the other hand, the above-mentioned radial force Fr is expressed by the following equation since it is the difference between the pressure difference between the outside and inside of the two compression chambers C and the deviation of the line contact portion of the two compression chambers C. .

Fr-2AH(Pd-Ps)...(7
) From this, the gas compression reaction force F against the straight line 0sOc
The angle θ on the acute side of is calculated as follows.

] ... (8) Here, Pd/Ps is the compression ratio ε, When replaced with , the angle θ becomes as shown in the following equation.

As is clear from the above equation (9), when ε>1 and c'<1, as ε increases, θ decreases. In other words, when the compression ratio ε increases, the force F acting on the rotating scroll member 12
becomes downward. -If I were to give an example, I would do something like the table below.

It has been clarified that the direction of the force F acting on the rotating scroll member 12 through the above Q is influenced by the compression ratio ε, and the present invention is an application of this theory.

In other words, as the compression ratio ε increases, the direction of the force F acting on the rotating scroll member 12G decreases in angle θ, and the direction changes downward in FIG.
The angle θ becomes smaller than the angle θ0 of Op, and as a result, the force F and the force F that causes the eccentric shaft 8 to push the rotating scroll member 12
'The combined force is directed downward (as a result of this action, the bush 10 is rotated counterclockwise in FIG. The present invention focuses on this point and selects the compression ratio ε within the range of 8≦ε≦17, and the angle θ calculated from equation (9) at this time is the angle θ0 ( The gist of this is that these settings have been made.

Therefore, the rotating scroll member 12 configured as described above is
The operation of the drive mechanism will be explained with reference to FIGS. 7 to 9.

During normal operation Q, the force F of the gas in the second compression chamber C pushing the rotating scroll member 12 is as shown in Figure 7*.
gl and the force F by which the eccentric shaft 8 pushes the rotating scroll member 12
The resultant force with p1 is Fol, and the angle θ0 and straight line 0s
The relationship between Oc and the angle θ1 of the force pgl is θ1>00 (from the core, the resultant force Fol is the rotational scroll heating material 12
(Accordingly, the rotating scroll member 12 is a fixed scroll portion) l:A' 174
It revolves while being pressed in the radial direction and exerts a compressive action.

When liquid compression occurs, the compression ratio ε becomes extremely high, and as shown in FIG. The combined force with the force Fp2 pushing 12 is Fo2
, and the angle θ between the angles θ0 and θSOC and the force Fg2 is
2 is the relationship θ2<θO (because of this, the resultant force Fo
2 is a direction (
This works. Therefore, the rotating scroll member 12 is broken from the fixed scroll member 17, and the liquid trapped in the compression chamber C can escape to the suction side and the discharge side, thereby preventing the occurrence of abnormally high pressure.

By the way, if the above-mentioned angle θO is too large, during normal operation (compression ratio ε is 3 to 8), the angle θ1 of jEFgl becomes smaller than the angle θ0, and the rotating scroll member 12 becomes fixed scroll member 177. !J) There is a risk that they will become separated from each other. If the opposite Q angle θ0 force is too small, the angle θ21 of the force Fg2 will not become smaller than the angle θ0 unless the pressure in the compression chamber C becomes considerably high, so the rotating scroll member 12 will not separate from the fixed scroll member 17.
Excessive stress will be exerted on each part. Taking this into consideration, in this embodiment, the angle θ0 is set within the range indicated by diagonal lines in FIG. The range of the angle θO may be set under the condition of ≦ε≦17. Rotating scroll (The frictional force that acts on this acts in the direction of increasing the tangential force Ft. Even with the same ε, θ is larger, so when using a material with a large friction coefficient, ε should be slightly smaller (difficult). Although it is necessary,
In many cases, the +W frictional force is very small compared to the tangential force Ft+, so it can be ignored.

Note that the present invention is not limited to the above embodiments,
It can also be specified as follows.

(1) As shown in FIGS. 10 and 11, the drive mechanism of the rotating scroll member 12 may be replaced by a link mechanism. That is, the rotating shaft 6 (this lever 20 is fixed integrally), the eccentric shaft 21 is fixed to the tip of the lever 20 as an integral surface, and the connecting link 22 is relatively rotatable to the eccentric shaft 21.
A boss portion (not shown) protruding from the center of the substrate 12a of the rotating scroll portion 1'12 is attached to the tip of the connecting link 22 so as to rotate 411 times. Also, the swing width of the rotating scroll heating material 12 is regulated by the contact between the collar 23 fixed to the lever 2 and the spiral bodies 12c and 17b. The effect is similar to that of the embodiment described above.

(2) Arrange the eccentric shaft 8, the bushing 10, and the connecting pin 11 so that the eccentric shaft 8 pushes the bushing 10 as shown in FIGS. 12 and 13G.

The operation and effect of this other example are also similar to those of the above-mentioned embodiment. In this case, the straight line 0sOT) is not necessarily longer than the straight line OsO,c and the straight line 0cOp.

(3) The balancer 9, the bush 10 and the connecting bottle 11 are integrally formed.

As described in detail above, the present invention is characterized in that the rotating scroll heating material is attached to the fixed scroll pigment so that it can move slightly, and the rotating scroll member is in contact with the fixed scroll pigment (ζ
: At some point, the angle θO on the acute side formed by the straight line 0sOc and the straight line 0cOp is set from ε0'-1 θ〇2!an(C・□) ε-1 8≦ε≦17 from the above equation 1 G As a result, the amount of eccentricity of the rotating scroll member is reduced when liquid is compressed or foreign matter gets caught, and it is possible to prevent the generation of abnormally high pressure and damage to the spiral wound body due to it, and also to prevent each part from being damaged. This has the effect of loosening the dimensional tolerances.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal cross-sectional view of the central part showing an embodiment embodying the present invention, FIG. 2 is a cross-sectional view taken along the line X--X of FIG. 1, and FIG.
4 is an enlarged perspective view showing the drive mechanism of the rotating scroll section 41, which is the main part of the present invention,
Fig. 5 is an exploded perspective view showing the rotation prevention mechanism of the rotating scroll member, Fig. 6 is a front view of one drive mechanism of the rotating scroll member seen from the rear side, and Fig. 7 is a diagram showing the drive mechanism t1 during normal operation. Figure 8 is a front view showing the working relationship of the forces in the drive machine [1] during liquid compression.
9 is a graph showing the direction of the force acting on the rotating scroll member, FIG. 10 is an exploded perspective view showing the drive mechanism of the present invention separately, and FIG. 11 is a diagram showing the separate assembly. Fig. 12 is a front view of the 11 baby movement mechanisms of the present invention during normal operation, and Fig. 13 is a front view of the same during liquid compression.Housings 1 to 3, rotating shaft 6, Eccentric shafts 8, 21, bushing 10, connecting bin 11, rotating scroll member 12, fixed cylinder 14, anti-rotation ring 16, fixed scroll member 17, lever 20, connecting link 22, stopper 23゜Patent applicant: Sutta Jido Co., Ltd. Loom factory representative
Person Patent Attorney On 1) Hiroshi Hiroshi 3rd I

Claims (1)

[Scope of Claims] 1. The front end surface of the housing passes through and supports a rotating shaft in a positive rotatable manner at the center of the housing. A mechanism for preventing rotation of the movable scroll member is provided on the inner surface of the housing, and a fixed scroll member is provided on the rear side of the housing to prevent the rotation of the movable scroll member. The spiral body is small (Tomo 21
The rotary scroll member is overlapped in a state of partial contact at 1111 points or more, and the rotating scroll member is revolved on a constant circular trajectory between both spiral bodies (while moving the airtight compression chamber formed by this toward the center O). In a scroll type compressor, the eccentric shaft* The connecting member can be rotated relative to the other.
s supports a rotating scroll member so as to be relatively rotatable at the offset position;
When the rotating scroll member is in contact with the fixed scroll member (in this state, the center of the rotating shaft is Os, offset/L-
Rotate the center of 1i+l+ by Op1
When is OC, the straight line Os Oc and the straight line 0cOp
(The angle θ0 on the acute side formed by this is 8≦ε≦17...(1) -1 C'- where ε is the compression ratio, α is the winding angle of the spiral body, and β is the spiral wound body. inner wall line delay angle, K; insulation index above (1
), (It) formula *J of the rotating Nuclor member in the Nuclor type compressor O
l (Moving mechanism. 2) While the front end surface of the housing is closed, the rotary shaft is positively rotatably supported through the rotary shaft, and an eccentric shaft fixed to the inner end of the rotary shaft (opposed to the rotary scroll) The members are mounted so that they can be rotated relative to each other, and the inside surface of the housing (this is where an anti-rotation IL mechanism is provided for the movable scroll member), and the rear side of the housing (this is where a fixed scroll member is installed and the rotation prevention IL mechanism is installed). The winding body and the spiral winding body of the rotating scroll member are overlapped with each other in a state where they are in partial contact at two or more places, and the rotating spiral part is made to revolve on a constant circular locus to form a space between the two spiral winding bodies. The airtight compression chamber is moved around its center to cause a volume reduction and contraction to perform a unidirectional continuous compression action, and the base plate of the fixed scroll member is discharged to the outside from the discharge passage provided through it. A scroll-type compressor (a rotary scroll compressor) in which a connecting member is rotatably supported relative to the eccentric shaft; In addition to supporting the rotating scroll member, a stopping means is provided to hold the rotating scroll member at a position slightly spaced apart from the fixed scroll member in the radial direction between the rotating shaft side and the connecting member. The scroll member is connected to the fixed scroll member (when the scroll member is in contact with the fixed scroll member, the center of the rotating shaft is Os, the center of the eccentric shaft is OP, and the center of the rotating nuclear member is OC, the straight line 0sOc and the straight line 0cOI) and ζ. The formed acute angle θO is 8≦ε≦17 (11) ε: Compression ratio, α: Winding angle of the spiral body, β: Inner wall line delay angle of the spiral body, K: Heat insulation Index above (1
), (1) A drive mechanism for a rotating scroll member in a scroll compressor, characterized in that it is set as follows. 3. A bushing as a connecting member is supported on the eccentric shaft so as to be relatively rotatable and at a position eccentric from the eccentric shaft,
The bush (herein, the boss portion of the rotating scroll member is supported so as to be relatively rotatable, and the inner end surface of the rotary shaft is further formed with an engaging recessed portion constituting the above-mentioned stopping means, and the above-mentioned bush also has the above-mentioned 4. A nuclear compressor according to claim 2, wherein the connecting bin constituting the stopping means is loosely inserted into the four engaging parts and penetrated therethrough. One end of the connecting link as a connecting member is supported for relative rotation, and the boss portion of the rotating scroll member is supported for relative rotation at the other end of the connecting link. 5. A drive mechanism for a rotating scroll member according to claim 2, in which a shaft side* is fixedly attached with a locking pad as the stopping means for regulating the rotation of the connecting link. The above formula (It) has 10≦ε≦15, and this (
A drive mechanism for a rotating scroll member in a scroll type compressor according to claim 2, wherein the angle θ0 of equation (1) is set from this.