JPS58170884A - Scroll compressor - Google Patents

Abstract

PURPOSE:To raise the compression ratio and the efficiency of a scroll compressor and to reduce the size of the same, by making the shape of the top end portion of a fixed spiral vane located near the center of the scroll and that of a movable spiral vane different from each other such that the volume of a compression space is decreased continuously. CONSTITUTION:Top end portions 21a, 22a of a fixed spiral vane 21 and a movable spiral vane 22 are shaped such that they are held in contact with each other at two points from the time before the final compression position of the scroll to the time when the scroll comes to the final compression position and the volume of a compression space P formed between the two vanes 21 and 22 is decreased continuously, as shown in the drawing. With such an arrangement, the volume of the compression space P at the final compression position where compression is terminated is made sufficiently small, so that most of the compression gas is discharge to the outside. Therefore, it is enabled to increase the compression ratio without increasing the number of turns of the vanes and the size of the entire structure. Further, since high-pressure gas is not leaked from the compression space P into a succeeding space, the efficiency of the compressor can be raised.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a scroll compressor that is capable of improving compression ratio and efficiency and reducing size.

[Technical background of the invention]

Scroll compressors are conventionally known as low-pressure compressors. This scroll type compressor is a combination of a pair of spiral blades, and is specifically constructed as shown in FIGS. 1 and 2.

That is, this compressor is roughly divided into a fixed part 1 and a movable part 2. The fixed part 1 includes a cylindrical case 1 with a bottom and a spiral wing 1 protruding from the inner surface of the bottom wall of the case 11 at a depth slightly lower than the depth of the case 1.
It is composed of 2. In addition, the movable soil consists of a plate 13 that is applied to close the opening of the case 11, and a spiral wing that protrudes from the lower surface of the plate 13 in FIG. 1 and meshes with the wing 12. 14 and.

Plate material 13c) consists of a shaft 15 protruding from the upper surface in FIG. Then, the side wall KFi suction hole 1 of the case 11
In addition, a discharge hole 17 is provided in the center of the bottom wall of the case J1.

This compressor delivers compressed gas in the following manner. That is, the shaft 16 is connected to a power source (not shown), and this power source moves the movable part 2 to the fixed part 1.
Rotate in the anti-vortex direction so as not to rotate relative to the
Let's repeat this turning motion. In the process of the above-mentioned turning operation, the leading edge of the blade 14 of the movable part l is 1X1
When turning to the closest turning position closest to the inner surface of the tip of the blade 2, the space formed between 9jt12゜14 in the center is moved closer to the closest turning position by the effective action of the shape of the wings 12 and 14. As a result, the gas decreases as
J.? .

It is pushed towards the center of the 14 spirals. Tsumeshigasu is compressed. Since the discharge hole 17 is provided at the center of the spiral, the compressed gas is eventually discharged from the discharge hole 17.

Then, when the leading edge of the blade 14 of the movable part passes through the closest turning position and turns, the space volume between the blades 12, 14 increases again, and finally this space opens into the so-called following space. Therefore, when the movable part 2 is rotated, compressed gas is intermittently discharged from the discharge hole 17, and the function as a compressor is exhibited.

[Problems with background technology]

In a scroll type compressor that performs compression operation based on the principle described above, a device 1 provided between a fixed part and a movable part is used.
The shapes of 1 and 14 are generally arc-shaped, round, -
It is formed in a curved shape. Further, as the blades 12 and 14, those having the same shape and edges are normally used.

For this reason, especially at the end of the compression process, the volume of the compression space suddenly increases, which not only makes it impossible to achieve a high compression ratio, but also causes the problem of poor efficiency. In order to explain the above-mentioned reason, the figure shows the shape change of the true central part at the end of the compression process (swirling in the anti-spiral direction), and shows that the blades 12 and 14 are formed to have exactly the same shape. Now, as shown in the same figure, if the tip of the blade 14 of the movable part turns in the anti-spiral direction along the trajectory shown by Y in the figure, the tip of the blade 14 will move along with this turning. As you move in the direction of the arrow in the figure, the volume of the space P formed between the two wings further decreases. As the blade 14 turns further, the volume of the space P further decreases as shown in FIG. When the blades 12 and 14 turn to the closest turning position where they are closest to the tips of the blades 12 and 14, the tips of the wings 12 and 14 cannot maintain contact with each other, and a space 1i1Q1eQm is formed between the wings 12 and 14, and a space P1 is followed by a space P1.

P3, and as a result, the volume of the space P increases rapidly. For this reason, the high-pressure gas that has been compressed in the space P cannot be effectively discharged unless it flows toward the space Pi #P1. Therefore, there was a drawback that a high compression ratio could not be achieved. Therefore, it is conceivable to increase the number of windings of the blades 1z and i4o in order to increase the compression ratio, but if this is done, the overall size will inevitably be increased. Also, as mentioned above, there is a space Pi in which the gas compressed in the space P continues vk.

If it flows into P, the input during the compression process will increase, and as a result, there is also the problem that efficiency is inevitably poor.

[Purpose of the invention]

The present invention has been made in view of the above circumstances, and its purpose is to provide a scroll compressor that can reduce the overall size and improve the compression ratio and efficiency in good condition. It's about doing.

[Summary of the invention]

The scroll compressor according to the present invention is characterized in that the shape of the tip portions located at the center of the spiral blades provided on the fixed part side and the spiral blades provided on the movable part side are different from each other. . To explain in more detail, the tip part is
From the time before reaching the final compression position until the time when the final compression position is reached, the two pieces are kept in contact with each other to continuously reduce the volume of the pressure space formed between them. It is formed into a shape.

[Effects of the Invention] With the above configuration, at the compression end position, as shown in FIG.
), the compressed space P is defined by the relation [Qt-Qs
is never opened, so the compression ratio can be increased without increasing the number of blade turns. It is possible to achieve a high compression ratio while making the overall size smaller. Furthermore, since the compression space is not opened until the compression end position, most of the compressed gas can be discharged by selecting the shape of the tip. Therefore, there is no risk of high-pressure gas flowing into the following space from the compression space, so it is possible to prevent a decrease in efficiency caused by the flow K, and as a result, high efficiency can be obtained.

[Embodiments of the invention]

The scroll compressor according to the present invention is different from conventional ones because of the shape of the tips located approximately in the center of the spiral blades provided on the fixed part side and the movable part side.
Here, only the tips of both wings will be shown and explained.

In FIG. 4, numeral 21 is a spiral wing provided on the fixed part side, and 22 is a spiral wing of the movable W5@ arranged in a meshing relationship with the wing 2. The blades 21 and 22 are formed to have the same shape except for the tips 11JJa and Jja located approximately in the center. The blade 21 is driven so that its leading edge 22e rotates in the counter-vortex ◆ direction without rotating on the trajectory indicated by the broken line Y in the figure.

Therefore, the inner surface H of the blade XXO tip 22& is formed into a curved surface extending according to a function representing the spiral ** of the inner surface of the continuous portion 22b of the tip 12hK.
The outer surface I of the tip portion 22L is formed so as to be smoothly connected to the outer surface of the portion 22b by a suitable vehicle. Ten thousand,
The outer surface J of the tip 21b of the tip 21a of the wing 2 is
When the blade is turning toward the final compression position, from a certain position to the final compression position, it is always formed into a convex curved surface that successively contacts the inner surface of the tip portion 22a of the blade 22; The connecting thick part is formed on one surface that smoothly connects to the convex curved surface and matches the locus of the leading edge 22 of the blade j2. Note that 31 in FIG. 4 indicates a discharge hole.

With such a configuration, the shape of the tips of the wings 21 and 22 at the end of the compression process is as shown in FIG. 5.

That is, as shown in FIG.
When e follows the aforementioned trajectory Y and turns to a position directly above the tip 21b of the wing 21 in the figure, the inner surface of the portion jllk of the wing 22 contacts the outer surface of the tip JJb, and the tip portion jJa of the wing 22 comes into contact with the outer surface of the tip JJb. The outer surface I of the blade 2 contacts the inner surface of the blade 2, and a compression space P is formed at the center of the spiral.

Since the blade j2 continues to rotate in the direction indicated by the solid line arrow 32 in the drawing, the volume of the compression space P decreases, thereby compressing the gas. The pressurized gas is gradually discharged from the discharge hole 3.

As the blades 22 rotate further, as shown in FIG. 2B, the volume of the compression space P further decreases, whereby the gas is further compressed and discharged from the discharge hole 31. in this case,
Since the shape of the tip 22m of the wing 22 and the shape of the tip 21 & of the wing 21 are set in the above relationship, the tip 21 of the image
m and 22b are always in contact at two places, and a so-called closed compression space P is formed between both ends 117 J a l J J a O except for the discharge hole 31 . As a result, the wing 22 rotates further and the same r.
When it turns to the final compression position as shown in IA (red),
Wing 21,210 tip i! ;l 1 m, 22 m
Since the shape of the compressor is determined by the above-mentioned member, the volume of the so-called closed compression space P becomes sufficiently small and the final compression state is achieved in good condition. Therefore, almost every fl of the gas compressed in the compression space P is discharged through the discharge hole 31, and the compression process ends in this state.

In this way, the tip 11jJa located at the center of the spiral wing 21 on the fixed part side and the tip jja located approximately at the center of the spiral wing 22 on the movable part side are set to the above-mentioned shape. Unlike conventional compressors, the volume of the compression space does not suddenly increase at the final position of one compression process, and the volume of the compression space can be made sufficiently small at the above position. Therefore, the compression ratio can be increased without increasing the number of spirals. In addition, since the high-pressure gas compressed in the compression space during the compression process does not flow into the so-called subsequent space, efficiency can also be improved.
In the end, you will get the nine benefits mentioned above. FIG. 6 is a view cut along line BB in FIG. 4 and viewed in the direction of the arrow, and the same parts as No. 4m are indicated by the same reference numerals. In other words, 40 in the figure is a case on the fixed part side.

4 is a valve stop bolt, 42 is a discharge 9f, 4 is a J valve upper plate, 44 is a discharge notch provided in the spiral blade 21, 31 is a discharge hole, and 46 is a compression chamber for the final stroke. There is.

In the above embodiment, the shape of the tip JJa of the spiral blade 21 provided on the fixed part side is changed, but conversely, the shape of the tip part of the spiral blade XXO provided on the movable part side is changed. Of course, the same effect can be obtained even if

[Brief explanation of drawings]

FIG. 1 is a vertical cross-sectional view of a conventional scroll compressor, and FIG. 2 is a cross-sectional view of the same compressor taken along line AA in FIG. 1. Figure 3, which is a view taken along IK and viewed in the direction of the arrow, shows the change in shape of both blade tips at the end of the compression process of the same compressor t-! ! FIG. 4 is a partially cutaway plan view partially showing the essential parts of a scroll compressor according to an embodiment of the present invention, and FIG.
FjA#i A diagram for explaining the shape change of both blade tips W6 at the end of the compression process of the same compressor, FIG. 6 shows a scroll type compressor according to an embodiment of the present invention
FIG. 9 is a local vertical cross-sectional view taken along line -1 and viewed in the direction of the arrow. DESCRIPTION OF SYMBOLS 1... Fixed part, 2... Movable part, 21... Spiral wing on fixed part side, 22... Spiral wing on movable part side, 21
m, 22m...tip, 21b...tip, P...compression space. Applicant's representative Patent attorney Takehiko Suzue Page 1 of 4?
・2 (no change in d) 1M1 Figure 2 Figure 3 fH4WJ 22a Figure 5 Figure 6 Commissioner of the Patent Office Haruki Shimada 1, Indication of Case Patent Application No. 1987-53503 No. 2 Name of Invention Scroll-type tenderness Machine 3, Relationship with the case of the person who did supplementary + E Patent applicant (307) Tokyo Shibaura Electric Co., Ltd. 4, Agent Jun Jun No. 5, Toranomon 1-chome, Minato-ku, Tokyo No. 17 Mori Building Meiji II Document, drawings, 〆 -7,
Contents of amendment 1

Claims (1)

[Claims] In the scroll-type compressor 11, in which a second spiral blade that rotates so as not to rotate is fitted to a first spiral blade provided on a fixed part, the center of the second spiral blade is A scroll compressor characterized in that the side tips of the first blade and the second blade are configured to have different shapes.