JPS6275089A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To prevent excessive compression and to reduce an input, by providing delivery gas passages, for compression space to communicate with a delivery port when said compression space is contracted to the preset compression ratio or more, to be recessed respectively in end plated of fixed and turning scrolls. CONSTITUTION:If a crescent-shaped compression space 26, formed by a lap 24 of a fixed scroll 22 and a lap 25 of a turning scroll 23, reaches the preset compression ratio, said compression space 26 immediately communicates with a delivery port 35 through a wide flow path area by delivery gas passages 36a, 36b, and the passages 36a, 36b are formed as recessed parts 37a, 37b, respectively on end plates 22a, 23a of the both scrolls 22, 23. As a result, compression gas in the compression space 26 can be allowed to flow in a large quantity to the delivery port 35 because the flow path sectional area of the deliviery gas passages 36a, 36b is rapidly spread, accordingly efficiency of a compressor can be improve by preventing excessive compression and reducing an input of the compressor.

Description

Detailed Description of the Invention: Technical Field of the Invention 1 The present invention relates to a scroll compressor, and more particularly to a scroll compressor in which a discharge gas passage formed in the center of a fixed scroll and an orbiting scroll is improved. About

[Problems with the Technical Background of the Invention] Recently, there has been a tendency to adopt scroll type compressors for compressors such as refrigerated recycles. As shown in FIG. 9, this scroll compressor is constructed by installing a wrap 3 of a fixed scroll 2 and a wrap 5 of an orbiting scroll 4 on a frame 1 in mesh with each other, and rotating the orbiting scroll 4 with a crankshaft 6. At the same time, an A-ru dam joint 7 is provided between the frame 1 and the orbiting scroll 4, and the rotation of the orbiting scroll 4 is regulated and the orbiting scroll 4 is caused to revolve while maintaining a certain eccentric distance with respect to the fixed scroll 2. , 5 is moved toward the center of the vortices of the wraps 3 and 5, compressed, and discharged from the discharge port 8 of the fixed scroll 2.

The wrap 3 of this fixed scroll 2 and the orbiting scroll 4
The relationship with the wrap 5 will be explained in detail with reference to FIGS. 10 to 13.

Each wrap 3, 5 is formed in the same thin shape such as an involute curve, and the center 04 of the orbiting scroll 4 maintains a constant eccentric distance ε from the center 02 of the fixed scroll 2.
The laps of 3.5 and 10 are engaged at a position rotated by 1801α, and installed in the same position.

The orbiting scroll 4 is able to avoid revolution by keeping an eccentric distance ε with respect to the center 02 of the fixed scroll 2 by 60 rotations of the crankshaft which has reached L. is fixed by the aluminum joint 7 described in 11 above, and moves only in the direction of the two axes that intersect with each other through the center C) 2 of the lever 2, the X axis and the Y axis. It is regulated (<K so that its rotation is prevented).

Now, assuming that the position of the orbiting scroll 4 in FIG. 10 is 0 degrees, FIG. 11 shows the position where the orbiting scroll 1 rotates 90 degrees around half an hour 81, and FIG. 12 shows the position at 270 degrees.
The position after turning 11 is shown at l). Also, Figure 13 shows 18
An enlarged view of the center of position d is shown at the 0th turn.

The wrap 3 of the fixed scroll 2 has an outermost wrap part 3b which is half-wound from the winding end @3a of the wrap 3 in A, and is integrally formed with the circumferential wall 9 of the fixed scroll 2. A suction groove 10 is formed on the inner circumferential surface of the circumferential wall 9 with a rotation angle of 180 degrees.

This suction groove 10 is formed so as to have an inner diameter 2i larger than the maximum locus diameter drawn by the half-wound outermost wrap portion 5 [) from the winding end 5a of the wrap 5 of the orbiting scroll 4, and its outermost side. A suction groove 10 is provided on the outer peripheral side of the wrap portion 5b.
A suction chamber 11, which is a constant space, is formed between the two. This suction 1N10 has a suction port 1QGJ near the end 3a of the lap winding of the fixed scroll 1-1-2 and the end 5a of the wrap winding of the orbiting scroll 4, and also has a suction port 12 near the end 5a of the lap winding of the orbiting scroll 4. The end portion 10a of the suction groove 10 on the side of the end 5a of the wrap winding of No. 4 is formed so as to close the space between the suction groove 10 and the wrap 3 of the fixed scroll 2.

The refrigerant from the suction port 12 is introduced into the suction chamber 11 between the suction groove 10 and the outermost wrap portion 5b of the rotating spacer 1-4, and from there the refrigerant enters the crescent-shaped portion formed by both wraps 3.5. It is introduced into the compression space 13. The j1 contraction space 13 moves while being continuously contracted toward the center along the vortices of the wraps 3 and 5, and the refrigerant introduced therein is contracted by 1 and ul Il!
Tagawa from 118.

By the way, in the scroll type compressor, when the crescent-shaped compression space 13 moves 1 step to the center of the spiral, the lap winding start end 5G of the orbiting scroll 4 is separated from the lap winding start end 3G of the fixed scroll 2. By doing so, the compressed space 13 and Tagawa [18] are communicated there! An I-out gas passage 14 is formed. In addition, the compression space 13 reaches the set compression ratio before the winding start ends 3c and 5c of each wrap 3.5 overlap, and for this reason, in the past, the compression ratio is as shown in the enlarged view of FIG. 3.
A part of the tip of each wrap winding start end 3c, 5c formed in an arc shape with a width of 5 as a diameter is cut out to quickly connect the compression space 13 that has reached the set compression ratio to the discharge port 8. A gas passage 14 is formed.

However, in the discharge gas passage 14 formed as described in -1-, a slight gap is created with respect to the compression space 13 that has reached the set compression ratio [), and a sufficient discharge amount cannot be obtained. There is a problem in that the input to the scroll compressor increases due to overcompression.

[Object of the invention] The present invention has been created taking into account the above circumstances,
The purpose is to provide a scroll compressor that can communicate the compression space that has reached a set compression ratio to the discharge port through a discharge gas passage with a wide cross-sectional area, thereby preventing overcompression and reducing input power. It's about doing.

[Summary of the Invention] In order to achieve the above object, the present invention meshes a fixed scroll and an orbiting scroll to form a crescent-shaped compression space, and rotates the orbiting scroll to bring the compression space into the center of the spiral. In a scroll type compressor, when the compression space is contracted beyond the set compression ratio, the compressed fluid is discharged from the central discharge port. A discharge gas passage for communicating the space with the discharge port is recessed in the end plate of the fixed scroll and the orbiting scroll. This is to prevent overcompression by guiding the gas to the outlet through an outlet gas passage having a wide cross-sectional area.

[Embodiment 1 of the Invention Below are examples of the adhesive of the present invention. (Details below)

As shown in FIG. 1, the compression element 21 of the scroll compressor is
4, it is mainly composed of a fixed scroll 22 and a rotating scroll 11-23, each of which has an end plate 22a.

A spiral wrap 2/1.25 such as impoly j-1- formed in the same shape is erected on 23a.

These fixed scroll 22 and orbiting scroll 23 are
The two spiral wraps 24 and 25 are engaged with each other in a rotatable manner with the wraps 24 and 25 on the inside, and are closed in a crescent shape between the spiral wraps 24 and 25 to form a compression space 26.

The fixed scroll 22 has an outer peripheral edge 22b fixed to the frame 27 (J), and the orbiting scroll 23
is rotatably housed in the frame 27 and has a boss portion 28 formed on the back surface 23b of the end plate 23a on which the wrap 25 is erected. It is connected to the eccentric shaft portion 29a. In other words, the rotating shaft 1-1-le 23 is connected to the crankshaft 2.
9, and is configured to revolve around the center of the fixed scroll 22 with a constant eccentric radius ε.
By avoiding turning in the direction, the crescent-shaped compressed space 2
6 is continuously moved along the wrap 24, 25 of the fixed scroll 22 and the orbiting scroll 23 toward the center of its spiral while being contracted. 1. It is composed of sea urchins.

Fig. 2 is a sectional view taken along the line ■-■ in Fig. 1, Fig. 3 is a sectional view taken along the line III-III in Fig. 2, and Fig. 4 is an enlarged view of the main parts of Fig. 1. . As shown in FIGS. 1 to 4, the configuration of the compression element 21 is exactly the same as that of the conventional one described in FIGS. 10 to 12. That is, in the wrap 24 of the fixed scroll 22, the outermost wrap portion 241) of the q+' winding from the end 2/4a of the wrap 24 is connected to the peripheral wall 22G of the fixed scroll 220.
A suction groove 30 is formed on the inner circumferential surface of the circumferential wall 22c extending 180 jli from the other end of the winding end 24a.

The suction groove 30 is connected to the wrap 25 of the swing valve 1]-rule 23.
The outermost wrap portion 25b is half-rolled from the winding end 25a.
b is formed larger than the flange 31 of the suction groove 30 (a), which is formed so that the inner diameter is larger than the maximum locus diameter drawn by the rotation movement, and this A suction chamber 32 that always has a space between it and the suction groove 30.
to form. This suction chamber 32 has a fixed scroll 2
Near the wrap winding end 24a of No. 2 and the turning sufu 1]-
The suction ports 3 are located near the wrap winding end 25a of the loop 23.
3 is provided, and an end 30a of the suction groove 30 on the lap winding end @25a side of the orbiting scroll 23 is formed to close the space between the suction groove 30 and the wrap 24 of the fixed scroll 22. Reference numeral 34 denotes an Oldham joint installed between the orbiting scroll 23 and the fretwheel 27 to prevent the orbiting scroll 23 from rotating. Also, inlet 3
3 is introduced into the suction chamber 32 between the suction groove 30 and the outermost wrap portion 25b of the orbiting scroll 23, and from there into the crescent-shaped compression space 26 formed by both wraps 24 and 25. Introduced in its lap 24.25
The compressed air is compressed along the spiral toward the center of the spiral, and is discharged from the compression element 21 through a discharge port 35 formed in the fixed scroll 22.

By the way, the F1 compression space 26 reaches the set compression ratio before the winding start ends 24C and 25G of each wrap 24.25 overlap. Therefore, in the present invention,
As shown in FIG. 1, when the crescent-shaped compression space 26 reaches the set compression ratio, a discharge gas passage 36 immediately communicates the compression space 26 with the discharge 1] 35 with a wide flow passage cross-sectional area.
a, 36b, end plate 22a of both scrolls 22.23,
Four portions 37a and 37b are formed on 23a, respectively.

5 and 6 show a recess 37a as a 111 gas outlet passage 36a formed in the end plate 22a of the fixed scroll 22.
FIG. 1 is a plan view. 3!1 (C, 24 is the wrap of the fixed scroll 22, and 2F) is the wrap of the rotating scroll 1-1-23. As shown in the figure, the Tagawa gas passage 36a on the fixed scroll 22 side is connected to the end plate 2 of the fixed scroll 11-22.
Cutting to 3a - 4 parts by "etc.

37a. The shape of the recess 37a on the side of the fixed scroll 11-rule 22 is the same as that of the outer wall 25d of the lap winding start end 25c of the rotating chain 1-1-rule 23 and the fixed scroll 22.
The crescent-shaped compression space 26 a h' iQ formed by the inner wall 24 e of the wrap 24 of No. 2 and the inner wall 24 e of the wrap 24 of 2.
The outer wall 25 of C (j, the region Δ connecting the inner wall 24e of the winding start end 24G of the fixed scroll 220 is the maximum shape and 1) is arbitrarily determined within the region A.

The same goes for the Tagawa gas passage 36b recessed on the orbiting scroll 23 side, and as shown in FIGS. When the November-shaped compression space 26b formed by the wall 24d and the inner wall 25e of the wrap 25 of the orbiting scroll 23 is compressed at the set compression ratio J, the fixed sulphur 1]-ru 22 wrap winding start end 24 outside wall 2
4d and start of wrap winding of rotating suifu []-ru 23 @24
It is arbitrarily determined within the region B, with the region 11tR connecting the inner wall 211e of G as the maximum shape.

Next, let's talk about the effects of the present invention.

As the orbiting scroll 23 rotates, the crescent-shaped compressed spaces 26a and 26b contract and move toward the center of the spiral, and the compressed spaces 26a.

The refrigerant in 26b is compressed to the set compression ratio.

When this set compression ratio is reached, the compression spaces 26a, 2
6b is still closed, and the discharge gas passage 36b provided in the end plate 23a of the orbiting scroll 23 is closed at the lap winding start end 24G of the fixed sleeve 1]-rule 22, and the fixed sleeve [
The discharge gas passage 36a connected to the end plate 22a of the L-rule 22 is connected to the lap winding start end 24 of the orbiting scroll 23.
It is closed with c.

(See Figures 5 and 7.) As the orbiting scroll 23 is further rotated, as shown in Figures 4 and 6.
11 gas passages 36a, 3 as shown in FIG.
6b is opened to create a compressed space 26a.

26b and the discharge port 35 are communicated with each other. After reaching the setting F1-compression ratio, when the orbiting scroll 23 rotates even slightly in y, the cross-sectional area of the outlet gas passages 36a and 36b is rapidly expanded, and the compressed gas refrigerant at the other end flows into the discharge port 35. It flows. Therefore, overcompression is prevented as much as possible, the input to the scroll compressor is reduced, and its efficiency is improved.

In addition, as shown in FIGS. 2 and 3, the suction groove 30 is formed with a larger inner diameter while leaving the flange 31 on the lower surface of the fixed scroll 22, so that the capacity of the suction chamber 32 can be maximized. It is possible to increase the efficiency of the scroll compressor by reducing the flow path resistance of the suction gas. Since the flange 31 is left in place, the turning frame 1] - 2
3, the disease surface can be enlarged, and the rotating space [l-
The force receiver can equalize the blood pressure due to the thrust force between the C surface and the thrust force, and prevents the orbiting scroll 23 from undulating and turning due to surface unevenness.
1-Be able to do it.

Note that the Tagawa gas passage 36a on the fixed scroll 22 side is formed as a discharge port by passing through the end plate 22a as it is, and only the discharge gas passage 36b on the orbiting scroll 23 side is formed as a discharge port.
It may be formed as b.

[Effects of the Invention] In summary, according to the present invention, when the crescent-shaped compression space is contracted beyond the set compression ratio, the discharge gas passage for communicating the compression space with the discharge port is rotated with the fixed scroll. Since there is a recess in each of the scroll and mirror plate,
It exhibits the following excellent effects.

(1) If the orbiting scroll rotates even slightly after reaching the set compression ratio, the compression space and the discharge port can be immediately communicated through the discharge gas passage, and the cross-sectional area of the passage can be rapidly expanded. can be done.

+21 Since the cross-sectional area of the 111 gas outlet passage is rapidly expanded, the 11 condensed gas in the 1f condensed space is discharged 1-
1, thereby preventing over-low compression, reducing the manpower required for the scroll type F1-I, and improving its efficiency.

[Brief explanation of drawings]

FIG. 1 is a side sectional view of a compression element showing a preferred embodiment of a scroll compressor according to the present invention, and FIG.
Figure 3 is a sectional view taken along the line M-M in Figure 2, Figure 4 is an enlarged view of the main part of Figure 1, Figures 5 and 6 are the center of the fixed scroll. Figures 7 and 8 are enlarged plan views of the center of the orbiting scroll, Figure 9 is a schematic side sectional view of a conventional compression element, Figure 10 and Figure 12 are Figure 9. FIG. 13 is an enlarged plan view of the center of the wrap. In the figure, 22 is a fixed scroll, 22a is a mirror plate of A, 23
is an orbiting scroll, 23a is its end plate, 26.26a,
26b is a compression space, 35 is a discharge port, 36a and 36b are r
tt is the gas passage. Agent Patent Attorney Nori Chika Butsuma
Yukio Chiyama Figure 13, shoulder 70a. Figure 12

Claims (1)

[Claims] A fixed scroll and an orbiting scroll are meshed to form a crescent-shaped compression space, and the orbiting scroll is rotated to contract the compression space toward the center of the spiral and move continuously to form a discharge port in the center. In a scroll type compressor configured to discharge compressed fluid from the fixed scroll, when the compression space is contracted to a set compression ratio or higher, a discharge gas passage for communicating the compression space with the discharge port is connected to the fixed scroll. A scroll compressor characterized by having recesses in the end plate of the orbiting scroll and the end plate of the orbiting scroll.