JP2862043B2 - Scroll fluid machine - 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 fluid machine used as an air compressor, a refrigerant compressor or an expander.

[0002]

2. Description of the Related Art FIG. 5 is an operation principle diagram showing a basic structure of a scroll fluid machine. In the figure, reference numeral 1 denotes a first scroll having a base plate provided with a discharge hole 4 in the center and a spiral projection, and 2 has a spiral projection and faces the first scroll,
And the second scroll 3a, which is eccentrically combined to form a plurality of compression chambers 3, is a high-pressure first compression chamber formed at the scroll center, and 3b is a low-pressure second compression chamber formed at the scroll middle. 3c is a third compression chamber formed outside the scroll. The first and second scrolls are formed by spiral projections having the same shape, and the form is a combination of an involute or an arc as conventionally known.

A general scroll fluid machine has the above-described basic configuration. For example, when used as a scroll compressor, a first scroll is stationary with respect to a space, and a second scroll is stationary.
The scroll is opposed to the first scroll and combined eccentrically, and its rotation is not changed with respect to the space, but is rotated, that is, rocked at a predetermined rocking radius (crank radius). The first scroll 1 and 2
Crescent-shaped compression chamber formed between the first and second scrolls 2
3a to 3c sequentially contract to compress the gas in the compression chamber 3 and discharge the gas.
The high pressure gas in the first compression chamber 3 a is discharged from the outlet 4. sand
That is, it is determined by the pitch of the scroll from the swing angle of 0 °.
Compression chamber communication angle (existing in the vicinity of swing angle 180 ° -270 °)
First compression chamber 3a to third compression chamber 3c are formed until
With the communication angle of the compression chamber, the third compression chamber 3c becomes the second compression chamber 3b.
Then, the second compression chamber 3b continuously changes to the first compression chamber 3a.
You. Further, the third compression chamber 3c communicates with an external gas chamber.
New gas is inhaled, and inhalation is completed at a swing angle of 0 °
Then, the gas compression process is started again. The operating principle of the device known by the name of the scroll fluid machine is as described above.

FIG. 6 is a cross-sectional view showing a conventional scroll compressor disclosed, for example, in Japanese Utility Model Laid-Open Publication No. 1-179189. In the drawing, reference numeral 1 denotes a first scroll having a spiral projection 1b and a compressed gas discharge hole 4 at the center of a base plate 1a;
Is arranged to face the first scroll 1, and has a spiral projection 2 b on the first scroll side of the base plate 2 a and a swing shaft 2 on the back side.
d is a compression chamber formed by combining the first scroll 1 and the second scroll 2;
Is a motor composed of a rotor 5a and a stator 5b, 6 is a balance weight portion 6a and a swing shaft 2d of the second scroll 2.
Main shaft having a bearing hole 6b for holding the bearing, 7 is a bearing hole 6b
And is integrated with the main shaft 6 to hold the oscillating shaft 2d and enable the second scroll 2 to oscillate. Reference numeral 8 denotes a bearing housing that holds the main shaft 6, and 9 denotes a bearing housing 8. A main bearing which is press-fitted and integrated with the bearing housing 8;
Reference numeral 10 denotes an outer container of the scroll compressor, 11 denotes an instruction to fix the bearing housing 8 and the stator 5b of the electric motor 5 together with the first scroll 1 to the outer container 10, and furthermore, a sub- portion of the main shaft 6
A bracket having a bearing 11a, 12 is a gas suction pipe mounted on the outer container 10, 13 is a discharge pipe, 14 is mounted on the upper part of the bearing housing 8 to support the internal pressure of the compression chamber 3 and the weight of the second scroll 2. An annular thrust bearing, 15 is an Oldham ring that prevents rotation of the second scroll 2 and maintains an angular position between the first scroll 1 and the second scroll 2, 16 is a forming preventing plate, and 17 is a lower part of the main shaft 6. It is an oil pump.

FIG. 7 is an enlarged schematic plan view showing a central portion of a first scroll 1 and a second scroll 2 of the scroll compressor. In the drawing, 1c is the upper end surface of the spiral projection 1b of the first scroll 1, 2c is the upper end surface of the spiral projection 2b of the second scroll 2, 3a is the first scroll 1 and the second
A high-pressure first compression chamber at the center formed by the scroll 2;
b is a low-pressure second compression chamber similarly formed in the middle part, 20
Is a first seal member inserted into a first seal groove formed on the upper end face 1c of the spiral projection of the first scroll 1, and 21 is a second seal groove formed on the upper end face 2c of the spiral projection of the second scroll 2. Is a base circle of the first scroll 1 and is swirled by the diameter of the base circle.
The pitch P of the winding protrusion 1b is determined. O1 is the center point of the base circle D1 of the first scroll 1. A0 on the base circle D1 is the first
The reference point of the outer wall winding start point C0 of the spiral protrusion 1b of the scroll 1, A10 on the base circle D1 is located at a position advanced from the outer wall winding start reference point A0 of the first scroll 1, and the inner wall winding of the first seal member 20 starts. The reference point, B10, is the contact point from the inner wall winding start point C10 of the first seal member 20 to the base circle D1 of the first scroll 1, and # 10 is limited by the seal width of the first seal member 20, etc., and is defined as: The winding start angle of the first seal member 20 to be wound. Similarly D2
Is a base circle of the second scroll 2, O2 is a center point of the base circle D2, A20 is a reference point at which the inner wall of the second seal member 21 is wound,
B20 is a contact point from the inner wall winding start point C20 of the second seal member 21 to the base circle D2 of the second scroll, and Ф20 is limited by the seal width of the second seal member 21, etc., and Ф20 = ∠A20
The winding start angle of the second seal member 21 defined by O2B20, which is generally 、 20 = Ф10, d2 = d1 (d2 is the base circle D
2 diameter). D3 is the diameter of the discharge hole 4, O3
Is the center point of the discharge hole 4 (usually O1 = O3).

FIG. 8 is a longitudinal sectional view of a discharge hole 4 portion showing an enlarged main portion of the first scroll 1 and the second scroll 2 of the scroll compressor. In the figure, reference numeral 1d denotes an edge of the ejection hole 4 of the first scroll 1. The components other than the above components are the same as the conventional components in FIGS.

The conventional scroll compressor is configured as described above. For example, when the electric motor 5 is energized, the electric motor 5 generates torque to rotate the main shaft 6. By the rotation of the main shaft 6, a rotational force is transmitted to the oscillating shaft 2 d fitted to the oscillating bearing 7 of the main shaft 6, and the second scroll 2 is moved to the Oldham ring 15.
The first and second scrolls 1 and 2 perform the compression action shown in FIG. Top surface 1c, 2c of spiral projection
The first and second seal members 20, 21 inserted into the first and second seal grooves formed in the first and second seals seal the axial gap between the first and second scrolls 1, 2 and the base plates 1a, 2a. As a result, radial gas leakage from the high-pressure first compression chamber 3a to the low-pressure second compression chamber 3b (from the first compression chamber 3a to the second
Radial leakage to the compression chamber 3b, third compression from the second compression chamber 3b
Radial leakage into the chamber 3c or external from the second compression chamber 3b
Radial leakage into the gas chamber) . On the other hand, the gas flowing into the outer container 10 from the gas suction pipe 12 is taken into the compression chamber 3 after cooling the electric motor 5 and the like, compressed, and then discharged from the discharge pipe 13 through the discharge hole 4. In this case the second
The swinging motion of the scroll 2 causes the upper end surface 2 of the spiral projection to move.
When the second seal member 21 inserted into the seal groove c moves to the inside of the discharge hole 4 as shown in FIG. 8, the second seal member 21 is damaged at the edge 1d of the discharge hole 4 or is worn at an early stage. To prevent this, the winding start angle Ф20 at which the inner wall motion trajectory of the second seal member 21 does not enter the area of the discharge hole 4 is determined, and the winding start point C20 of the second seal member 21 (from the point A20 on the base circle D2) At the position of the length of the arc A20 B20 at the tangent at the point B20 of the winding start angle Ф20, the hole diameter D3 of the discharge hole 4
Point outside the circle). The second seal member 21 is installed along the longitudinal direction of the spiral from the position of the winding start point C20 to the upper end surface 2c of the spiral projection. Conventionally, the first seal member 2
The winding start point C10 of 0 is also set as the winding start angle Ф10 = Ф20. The minimum winding start angle Ф is defined as the minimum winding start angle, and the minimum winding start angle of the second seal member 21 is most affected by the diameter and position of the discharge hole 4.

[0008]

In the conventional scroll fluid machine as described above, the first and second seal members 20,
As shown in FIG. 8, the second seal member 21 is arranged from the winding start angle Ф (Ф = Ф10 = Ф20) where the second seal member 21 is not damaged by the edge 1d of the discharge hole 4 or does not wear out early. Accordingly, since the first and second seal members 20, 21 are not disposed at the spiral center portions of the upper end surfaces 1c, 2c of the spiral protrusion, the low pressure second compression chamber 3a is moved from the high pressure first compression chamber 3a.
There is a problem that the leakage area to the compression chamber 3b is relatively large, the power loss of gas leakage increases, and the efficiency decreases.

The present invention has been made to solve such a problem, and an object of the present invention is to provide a scroll fluid machine in which gas leakage from a high-pressure compression chamber to a low-pressure compression chamber is small.

[0010]

According to the present invention, there is provided a scroll fluid machine including at least one of the first and second seal members.
One of them toward the center of the spiral of the spiral projection.
To the minimum winding start angle at which the roll width can be formed.
From the small winding start angle, go to the center of the seal member inner wall.
The part is cut and extended to a smaller winding start angle .

[0011]

Alternatively, the discharge holes are moved from the center of the base plate along the inner wall of the spiral projection of the first scroll, and the first and second scrolls are moved.
A central portion formed by the scroll is provided in a high-pressure first compression chamber and is provided at a position not communicating with the low-pressure second compression chamber, and at least one of the first and second seal members is directed toward the center of the spiral of the spiral projection. In this case, it is arranged so as to extend to the winding start angle where the same seal width can be formed.

Alternatively, the discharge holes are moved from the center of the base plate along the inner wall of the spiral projection of the first scroll, and the first and second scrolls are moved.
A central portion formed by the scroll is provided in a high-pressure first compression chamber and is provided at a position not communicating with the low-pressure second compression chamber, and at least one of the first and second seal members is directed toward the center of the spiral of the spiral projection. The minimum winding start angle that can form the same seal width is obtained by cutting a part of the inner wall of the seal member from the minimum winding start angle toward the center and extending to a smaller winding start angle. is there.

[0014]

According to a first aspect of the present invention, at least one of the first and second seal members is provided.
With the same seal width up to the minimum winding start angle.
Extend it and cut a part of the inner wall of the sealing member.
The length of the seal is extended to the smaller winding start angle,
And the leakage area from the high-pressure first compression chamber to the low-pressure second compression chamber (the outer wall side of the first scroll) is reduced.

[0015]

Further, constructed scroll fluid machine as claimed in claim 2, the discharge holes from the base plate center to move along the spiral protrusion inner wall of the first scroll is formed with first and second scroll Located in the high pressure first compression chamber in the center,
Because it is provided at a position that does not communicate with the low-pressure second compression chamber,
The trajectory of the movement of the inner wall of the second seal member generated by the swinging or rotating motion of the scroll is outside the discharge hole area, and the winding start angle is smaller than before, so that the seal length of the second seal member can be longer than before. . Therefore, by arranging at least one of the first and second seal members so as to extend to the winding start angle where the same seal width can be formed toward the center of the spiral of the spiral projection, the first high-pressure seal member is provided.
The leakage area from the compression chamber to the low-pressure second compression chamber is reduced.

Further, in the scroll fluid machine according to the third aspect , the discharge hole moves from the center of the base plate along the inner wall of the spiral projection of the first scroll, and at least one of the first and second seal members. One of the seal lengths
It extends to the minimum winding start angle with the same seal width and further cuts a part of the inner wall of the seal member to extend to the smaller winding start angle, so that the seal length becomes longer and the high pressure first compression chamber The leakage area from the pressure to the low-pressure second compression chamber is reduced.

[0018]

[Embodiment 1] FIG. 1 is an enlarged schematic plan view of a main part showing one embodiment of the present invention. In the drawing, 1 is a first scroll having a spiral projection 1b and a discharge hole 4, and 2 is a first scroll having a spiral projection 2b.
A second scroll arranged opposite to the scroll 1, 2
Reference numeral 2 denotes a first seal member inserted into a seal groove formed along the longitudinal direction of the spiral projection on the upper end face 1c of the spiral projection of the first scroll 1, and reference numeral 23 denotes a spiral extension on the upper end face 2c of the spiral projection of the second scroll 2. The second seal member 3a inserted into the seal groove formed along the direction is the first scroll 1 and the second scroll 2, and the high-pressure first compression chamber 3b formed in the center portion is similarly the third compression member. A low-pressure second compression chamber formed outside the first compression chamber, 3b1 is an outer wall side of the first scroll, and 3b2 is an inner wall side of the first scroll. D1 is the base circle of the first scroll 1, O1 is the base circle D
The center point of D1, the second point is determined in the same way as the base circle D1
Scroll base circle, O2 is the center point of base circle D2, O3
The central point of discharge holes 4 (O3 = O1), A10 and A20 is the width of the sealing member, the winding start positioning or Ru base circle like D1,
Reference marks B11 and B21 on the base circles D1 and D2 indicate winding start contacts of the first and second sealing members 22 and 23 on D2, and # 11 indicates a first sealing point on D2. The winding start angle of the member 22 (the angle for determining the winding start position of the first seal member 22 Ф11 = ∠A10O
1B11), # 21 is the winding start angle of the second seal member 23 (@
21 = ∠A20 O2 B21), C10 is the conventional first sealing member 2.
0 winding start point, C11 is the first sealing member 2 according to the present invention.
2, the winding start point C20 is the conventional winding start point of the second seal member 21, and C21 is the winding start point of the second seal member 23 according to the present invention.

In the scroll compressor constructed as described above, on the tangent of the contact point B11 on the base circle D1 of the first scroll 1, the winding start angle # 11 in the base circle D1 is set.
The arc length of (Ф11 = ∠A10O1B11) is the winding start point C11 of the first seal member 22. Starting point of winding C11
Is the limit position where the seal width of the first seal member 22 can be made the same, the winding start angle # 11 at this time is called the minimum winding start angle of the first seal member 22. If the winding start point of the first seal member 22 is C11, the first seal member 22 is
The length of the arc C10 C11 is extended, the upper end surface 1 of the spiral projection
This means that the seal length at the center of c has increased by arc C10 C11. The second seal member 23 is determined so that the locus of the inner wall motion of the second seal member 23 caused by the swinging or rotating motion of the second scroll is outside the area of the discharge hole 4 as in the related art. Similarly to the first seal member 22, the winding start point C21 of the second seal member 23 is determined by the winding start angle Ф21 (Ф21 = ∠A20O2B21). In this case, the winding start angle Ф21 is set to the minimum winding start angle such that the movement locus of the winding start point C21 of the second seal member 23 is at a limit position that does not fall within the range of the circle D3 of the discharge hole 4. . As described above, since the seal length of the first and second seal members 22 and 23 is longer toward the center of the spiral of the spiral projection than in the related art, the high-pressure first compression chamber 3a is moved to the low-pressure second compression chamber 3b. The gas leakage area is reduced, the gas leakage is reduced, and the efficiency of the scroll compressor can be improved. In particular, the winding start angle # 11 of the first seal member 22 is set smaller than the winding start angle # 21 of the second seal member 23,
3 (arc C10 C11-arc C20 C21) seal is longer than
The gas leakage area from the compression chamber 3a to the low-pressure second compression chamber 3b1 is reduced.

In the above embodiment, the winding start angles Ф11, Ф
Although the seal length is extended to a position where 21 becomes the minimum winding start angle, Ф21 should be an angle smaller than Ф20.
If Ф11 is smaller than よ り 小 さ い 21,
Each of the angles may be larger than the minimum winding start angle, and gas leakage is reduced as compared with the related art.

Embodiment 2 FIG. In the first embodiment, the first seal member 22 is extended to a range where the same seal width can be formed to reduce the gas leakage area. However, in the second embodiment, the inner wall of the seal member is formed from a position where the same seal width can be formed. A part is cut to further extend the seal member.

FIG. 2 is an enlarged schematic plan view showing a main part of a second embodiment of the present invention. In FIG. 2A, reference numeral 24 denotes a first seal member inserted into a seal groove formed on the upper end surface 1c of the spiral projection of the first scroll 1, and reference numeral 24a denotes a part of an inner wall of the first seal member 24 cut. Cut part, B12 is first
First seal member 2 on base circle D1 of scroll 1
4, a winding start contact point, # 12 is a winding start angle of the first seal member 24 (# 12 = # A10O1B12), and C12 is a winding start point of the first seal member 24. 25 is a second seal member inserted into a seal groove formed on the upper end surface 2c of the spiral projection of the second scroll 2, 25a is a cut portion obtained by cutting a part of the inner wall of the second seal member 25, and B22 is a second seal member. Scroll 2
, The winding start contact point of the second seal member 25 on the base circle D2, # 22 is the winding start angle of the second seal member 25 (# 22 =
{A20O2B22) and C22 are the winding start points of the second seal member 25. FIG. 2B illustrates the movement trajectory of the inner wall winding start point C22 of the second seal member 25, where D42 is C22.
The motion locus O42 is the center point of the motion locus D42. The components other than the above-mentioned components are the same as those in the conventional example and the above-described embodiment, and thus the description thereof will be omitted.

In the scroll compressor constructed as described above, on the tangent of the contact point B12 on the base circle D1 of the first scroll 1, the winding start angle Ф12 on the base circle D1
The arc length of (Ф12 = ∠A10O1B12) is the winding start point C12 of the first seal member 24. In this case, the first
Assuming that the limit position at which the seal width of the seal member 24 can be made the same is C11, the first seal member 24 is cut along the spiral projection from the inner wall C11 to form the cut portion 24a. As a result, the length of the first seal member 24 is further extended by the arc C11C12, and the seal length at the center of the upper end surface 1c of the spiral projection is significantly increased. The second seal member 25 has an inner wall motion trajectory D of the second seal member 25 generated by the swinging or rotating motion of the second scroll 2.
The winding start angle Ф22 so that 42 is outside the area of the discharge hole 4.
(Ф22 = ∠A20O2B22) and the winding start point C22 of the second seal member 25 are determined. In this case, the second seal member 2
The part of the inner wall C21 to C22 of the second seal member 25 is partially cut from the minimum winding start point C21 where the seal width of No. 5 can be formed to be the same, and a cut portion 25a is formed. FIG. 2B shows the movement locus of the winding start point C22 of the second seal member 25.
Will be described. The center points O1 and O2 of the two base circles D1 and D2 are connected, and then the center point O2 of the base circle D2 of the second scroll 2 and the winding start point C22 of the second seal member 25 are connected. A parallelogram having two sides of the line segment O1O2 and the line segment O2C22 is drawn. In this parallelogram, the point opposite to the center point O2 of the base circle D2 of the second scroll 2 is the second seal member 25.
Is the motion locus center point O42 of the winding start point C22. The swing radius R (R = line segment O) of the second scroll 25 around the movement locus center point O42 of the winding start point C22 of the second seal member 25 is the center.
If a circle is drawn by (1O2), the movement locus D42 of the winding start point C22 of the second seal member 25 becomes a position that does not fall within the range of the circle D3 of the discharge hole 4. As a result, the length of the second seal member 25 is such that the arc C21 C22 is extended, and the seal length at the center of the upper end surface 2c of the spiral projection is increased. First and second seal members 24,
Since the seal length of each of the seals 25 increases toward the center of the spiral of the spiral projection, the area of gas leakage from the first compression chamber 3a to the second compression chamber 3b is reduced, and gas leakage is reduced. Efficiency can be improved.

In the above embodiment, the seal length of both the first and second seal members 24 and 25 is extended by the cut portion, but at least one of them may be extended by the cut portion. Than the first compression chamber 3
a to the second compression chamber 3b has a smaller gas leakage area,
Gas leakage is reduced, and the efficiency of the scroll compression chamber can be improved.

One of the first and second seal members has the same seal length as the conventional one, the other has the same seal width extending to the minimum winding start angle, and the cut length reduces the seal length. It may be longer.

Embodiment 3 FIG. In each of the above embodiments, the position of the discharge hole 4 was the conventional state, and the sealing member was lengthened to reduce the gas leakage area. In the third embodiment, the position of the discharge hole 4 was moved and the seal member of the second scroll 2 was moved. The winding start angle can be reduced, and the sealing member is lengthened.

FIG. 3 is an enlarged schematic plan view of a main part showing a third embodiment of the present invention. In FIG. 3A, reference numeral 22 denotes a first seal member which is inserted into a seal groove formed on the upper end surface 1c of the spiral projection of the first scroll 1, up to a limit position where the same seal width can be formed as in the first embodiment. It is an extension. 26 is the upper end surface 2c of the spiral projection of the second scroll 2
B, a second sealing member inserted into a sealing groove formed in
23 is a winding start contact point of the second seal member 26 on the base circle D2 of the second scroll 2, and # 23 is a second seal member 26
Is the winding start angle (Ф23 = ∠A20O2B23), and C23 is the winding start point of the second seal member 26. O30 is the center point of the circle D30 of the discharge hole 4. FIG. 3B shows the second seal member 26.
To explain the movement trajectory of the inner wall winding start point C23 of FIG.
43 is a motion locus of C23, and O43 is a center point of the motion locus D43. The components other than the above-described components are the same as those in the conventional example and the above-described embodiment, and thus description thereof will be omitted.

In the scroll compressor constructed as described above, the length of the first seal member 22 is longer than that of the conventional arc compressor.
C11 is extended, and the seal length at the center of the upper end surface 1c of the spiral projection is increased by the arc C10C11. On the other hand, the discharge hole 4 moves from the center point O1 of the base plate 1a of the first scroll 1 along the inner wall of the spiral projection 1b of the first scroll 1, and the spiral projection 1b of the first and second scrolls 1 and 2. A central point O30 is provided at a position in the central high-pressure first compression chamber 3a formed by 2b and not communicating with the low-pressure second compression chamber 3b. The range in which the movement trajectory of the inner wall of the seal member 26 is not affected by the discharge hole 4 is widened. Thus, the smaller winding start angle Ф23 (Ф23 = ФA20O2B23)
) Becomes possible, and the winding start point C2 of the second seal member 26 becomes
3 is decided. The motion locus of the winding start point C23 in this case will be described with reference to FIG. The center points O1 and O2 of the two base circles D1 and D2 are connected to form a base circle D of the second scroll 2.
2 and the winding start point C23 of the second seal member 26.
Tie. A parallelogram having two sides of the line segment O1O2 and the line segment O2C23 is drawn. In this parallelogram, the point opposite to the center point O2 of the base circle D2 of the second scroll 2 is the winding start point C23.
Is the motion locus center point O43. By drawing a circle around the movement locus center point O43 of the winding start point C23 of the second seal member 26 with the swing radius R (R = line segment O1 O2) of the second scroll 2, the winding of the second seal member 26 can be started. The movement trajectory of the point C23 is not required to fall within the range of the circle D30 of the ejection hole 4. Thereby, the second seal member 26 is
The length of the arc C20 C23 is extended, the upper end surface 2 of the spiral projection
This means that the seal length at the center of c has increased. Since the seal lengths of the first and second seal members 22 and 26 increase toward the center of the spiral of the spiral protrusion, the gas leakage area from the high-pressure first compression chamber 3a to the low-pressure second compression chamber 3b decreases. In addition, gas leakage is reduced, and the efficiency of the scroll compressor can be improved.

In the third embodiment, the first and second seal members 22 and 26 both extend the seal length .
Even if the two seal members 26 are simply extended, the gas leakage area from the first compression chamber 3a to the second compression chamber 3b is reduced, the gas leakage is reduced, and the efficiency of the scroll compressor can be improved. Note that the ejection hole as shown in Example 3 is centered.
As in the case of the first embodiment, even when moving from
In addition, the first sealing member 26
If only 22 is extended, the same effect as in the first embodiment can be obtained.
You. Further, in the third embodiment, the winding start angles Ф11 and Ф23 are
The seal length has been extended to the position where the minimum winding start angle is reached.
But at angles smaller than the above Ф10 and Ф20, respectively.
If any, make sure that the angle
Gas leakage may be reduced as compared with the conventional case.

Embodiment 4 FIG. FIG. 4 is an enlarged schematic plan view of a main part showing a fourth embodiment of the present invention. In FIG. 4A, 24
Is a first seal member inserted into a seal groove formed on the upper end face 1b of the spiral projection of the first scroll 1. Similar to the first seal member in the second embodiment, a limit position C11 at which the same seal width can be formed. The inner wall is cut more along the spiral projection, and the winding start point is extended to C12. 2
Reference numeral 7 denotes a second seal member which is inserted into a seal groove formed in the upper end surface 2b of the spiral projection of the second scroll 2.
Is a cut portion obtained by cutting a part of the inner wall from the minimum winding start point C23 of the second seal member 27 toward the center, and C24 is the second winding member.
This is the winding start point of the seal member 27. B24 is a winding start contact point of the second seal member 27 on the base circle D2 of the second scroll 2, .DELTA.24 is a winding start angle of the second seal member 27 (.DELTA.24 = .DELTA.A20 O2 B24), and O30 is a center point of the discharge hole 4. . In FIG. 4B, D44 is the motion locus of the winding start point C24 of the inner wall of the second seal member 27, and O44 is the center point of the motion locus D44. The components other than the above-described components are the same as those in the conventional example and the above-described embodiment, and thus description thereof will be omitted.

In the scroll compressor configured as described above, the length of the first seal member 27 is longer than that of the conventional arc compressor.
10C12 is extended, and the seal length at the center of the upper end surface 1c of the spiral projection is significantly increased. On the other hand, the discharge hole 40 is located at the center point O1 of the base plate 1a of the first scroll 1.
Move along the inner wall of the spiral projection 1b of the first scroll 1 to form the spiral projections 1b of the first and second scrolls.
The center point O is located at a position in the high pressure first compression chamber 3a at the center formed by 2b and not communicating with the low pressure second compression chamber 3b.
By providing 30, the range in which the movement trajectory of the inner wall of the second seal member 27 caused by the swinging or rotating movement of the second scroll 2 is not affected by the discharge hole 40 is widened. As a result, a smaller winding start angle Ф24 (Ф24 = ∠A20O2B24
) Becomes possible, and the winding start point C2 of the second seal member 27 becomes
4 is decided. If the limit position at which the seal width of the second seal member 27 can be the same is C23, the second seal member 2
7, a part of the inner wall C23 to C24 is cut to form a cut portion 27a, and the second seal member 27 has a longer arc C20C24 than the conventional one. Winding start point C24 in this case
4B will be described with reference to FIG. Both base circles D
1, connecting the center points O1 and O2 of D2,
The center point O2 of the base circle D2 and the winding start point C24 of the second seal member 27 are connected. A parallelogram having two sides of the line segment O1O2 and the line segment O2C24 is drawn.
The point opposite to the center point O2 of the base circle D2 of the scroll 2 is the center point O44 of the movement locus of the winding start point C24. The swing radius R (R = line segment O1O) of the second scroll 27 around the movement locus center point O44 of the winding start point C24 of the second seal member 27 is the center.
If a circle is drawn according to 2), the movement locus of the winding start point C24 of the second seal member 27 becomes a locus, and this locus need not fall within the range of the hole diameter D30 of the discharge hole 40. As a result, the length of the arc C20C24 of the second seal member 27 is longer than that of the related art,
This means that the seal length at the center of the upper end surface 2c of the spiral projection has been significantly increased. First and second seal members 2
Since the seal lengths of the spirals 4 and 27 increase toward the spiral centers of the spiral protrusions 1b and 2b, respectively, the high-pressure first compression chamber 3a
, The area of gas leakage to the low-pressure second compression chamber 3b is reduced, the gas leakage is reduced, and the efficiency of the scroll compressor can be improved.

In the fourth embodiment, the seal length of both the first and second seal members 24 and 27 is extended.
By extending at least one of them, the area of gas leakage from the high-pressure first compression chamber 3a to the low-pressure second compression chamber 3b becomes smaller than before, thereby reducing gas leakage and improving the efficiency of the scroll compressor. .

[0033]

As described above, the present invention provides the first or second embodiment .
Minimize the seal length of at least one of the seal members
Extend with the same seal width to the winding start angle, and further seal
Cut a part of the inner wall to a smaller winding start angle
Extended, the seal length is longer and the high pressure first
The leakage area from the compression chamber to the low-pressure second compression chamber (the outer wall side of the first scroll) is reduced, the recompression power is significantly reduced, and a highly efficient scroll fluid machine with less leakage loss is obtained. is there.

[0034]

In another scroll fluid machine according to the present invention, the discharge hole is moved from the center of the base plate along the inner wall of the spiral projection of the first scroll, and the high pressure at the center formed by the first and second scrolls is increased. A winding start that is provided in the first compression chamber and is provided at a position not communicating with the low-pressure second compression chamber, and at least one of the first and second seal members can form the same seal width toward the center of the spiral of the spiral projection. Since it is arranged to extend to the corner, the sealing length of each seal member can be longer than before, the leakage area from the high pressure first compression chamber to the low pressure second compression chamber is reduced, and a high efficiency scroll fluid machine is provided. The effect is obtained.

According to another scroll fluid machine of the present invention, the discharge hole is moved from the center of the base plate along the inner wall of the spiral projection of the first scroll, and at least one of the first and second seal members is sealed. The length is extended to the minimum winding start angle with the same seal width, and a part of the inner wall of the seal member is further cut to extend to the smaller winding start angle. There is an effect that a leak area from the first compression chamber to the low-pressure second compression chamber is reduced, and a highly efficient scroll fluid machine is obtained.

[Brief description of the drawings]

FIG. 1 is an enlarged schematic plan view of a main part showing a first embodiment of the present invention.

FIG. 2 is an enlarged schematic plan view of a main part showing a second embodiment of the present invention.

FIG. 3 is an enlarged schematic plan view of a main part showing a third embodiment of the present invention.

FIG. 4 is an enlarged schematic plan view of a main part showing a fourth embodiment of the present invention.

FIG. 5 is an operation principle diagram of the scroll fluid machine.

FIG. 6 is a longitudinal sectional view of a conventional scroll compressor.

FIG. 7 is an enlarged schematic plan view of a main part showing a conventional scroll compressor.

FIG. 8 is an enlarged vertical sectional view of a main part showing a conventional scroll compressor.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 1st scroll 1a 1st scroll base plate 1b 1st scroll spiral projection 1c 2nd scroll 2a 2nd scroll base plate 2b 2nd scroll spiral projection 2c 1st scroll 3 Compression chamber 3a First compression chamber 3b Second compression chamber 3b1 Second compression chamber 3b2 Second compression chamber 3c Third compression chamber 4 Discharge hole 22 First seal member 23 Second seal member 24 First Seal member 24a Cut part 25 Second seal member 25a Cut part 26 Second seal member 27 Second seal member 27a Cut part 40 Discharge hole

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. ⁶ , DB name) F04C 18/02 311

Claims (3)

(57) [Claims] A first scroll having a spiral plate and a base plate provided with a discharge hole in a central portion, and a plurality of compression chambers opposed to the first scroll and eccentrically combined with each other to form a first scroll. A second scroll having a spiral projection to be formed, a first seal member provided on the upper end face of the spiral projection of the first scroll along the spiral longitudinal direction, and a spiral seal on the upper end face of the spiral projection of the second scroll. provided Te, in which movement locus of the inner wall resulting from the oscillating or rotary motion of the second scroll having a second sealing member disposed from the winding start angle is outside the discharge hole region, the first or second seal At least of the members
One of them is the same toward the spiral center of the spiral projection
Extend to the minimum winding start angle where the seal width can be formed.
From the minimum winding start angle toward the center of the seal member inner wall
A scroll fluid machine characterized in that a part of the scroll fluid machine is cut and extended to a smaller winding start angle . 2. A base plate having a discharge hole in the center and a first scroll having a spiral projection, a plurality of compression chambers opposed to and eccentric to the first scroll, and having a plurality of compression chambers between the first scroll and the first scroll. A second scroll having a spiral projection to be formed, a first seal member provided on the upper end face of the spiral projection of the first scroll along the spiral longitudinal direction, and a spiral seal on the upper end face of the spiral projection of the second scroll. Wherein the movement trajectory of the inner wall generated by the swinging or rotating movement of the second scroll is provided from the winding start angle outside the discharge hole area, wherein the discharge hole is a base plate. First scrow from center
Moving along the inner wall of the spiral projection of the first and second swirls.
In the high-pressure first compression chamber in the central part formed by crawl
Ri, provided at a position that does not communicate with the second compression chamber of the low pressure, at least one of the first or second sealing member, Ru can be formed by the same seal width toward the spiral center of the spiral protrusions
Scroll fluid machine, characterized in that it arranged to extend to the winding can start angle. 3. A base plate having a discharge hole in the center and a first scroll having a spiral projection. The first scroll is opposed to the first scroll and eccentrically combined, and a plurality of compression chambers are provided between the first scroll and the first scroll. A second scroll having a spiral projection to be formed, a first seal member provided on the upper end face of the spiral projection of the first scroll along the spiral longitudinal direction, and a spiral seal on the upper end face of the spiral projection of the second scroll. Wherein the movement trajectory of the inner wall generated by the swinging or rotating movement of the second scroll is provided from the winding start angle outside the discharge hole area, wherein the discharge hole is a base plate. It moves along the inner wall of the spiral projection of the first scroll from the center, and is located in the high-pressure first compression chamber at the center formed by the first and second scrolls, and is in the low-pressure second compression chamber. And at least one of the first and second seal members can have the same seal width toward the center of the spiral of the spiral projection.
Extend to the minimum winding start angle, and from the minimum winding start angle
Cut part of the inner wall of the seal member toward the center and
A scroll fluid machine, wherein the scroll fluid machine is extended to a small winding start angle.