JPH05202871A - Scroll compressor - Google Patents

Abstract

PURPOSE:To increase suction volume by using the winding end parts of the first and second spiral elements, make pressure when an outside operation area X where suction volume is increased communicates with the discharge port roughly equal to that when an inside operation area Y communicates with the discharge port to eliminate power loss due to a difference in Pressure and due to increase in the flow rate of fluid to be discharged from a discharge port. CONSTITUTION:The inner wall surface at the winding end part of the first spiral elements 22 of the first scroll 2 is extended near the winding end part, of the second spiral element 32 of the second scroll 3 to increase the suction volume of an outside operation area X. Besides, an advance opening part 61 which opens the outside operation area X where the suction volume is increased in advance of an inside operation area Y is provided to make the pressure equal when the respective operation areas X, Y communicate with the discharge port, 6, and to increase the port opening area of the discharge port 6, thus eliminating power loss.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor mainly used for refrigeration equipment.

[0002]

2. Description of the Related Art Generally, a scroll compressor is disclosed in Japanese Patent Laid-Open No.
-81513. As shown in FIG. 7, this conventional compressor includes a first scroll A having an end plate and a first spiral body A1, and a second scroll B having an end plate facing the end plate and a second spiral body B1. The scrolls A and B are overlapped with each other such that the scroll end portions of the scrolls A1 and B1 are meshed with each other at a position where the end portions of the windings are displaced by about 180 degrees, and the scrolls A and B are discharged to the center of the end plate of the first scroll A. -C and a suction port D are provided on the outer peripheral side to form an operating space formed between the spiral bodies A1 and B1 by the relative revolution movement of the first and second scrolls A and B. The compression action is performed by moving the discharge port C in the direction of the volume while decreasing the volume.

In this general compressor, as shown in FIG. 7, the end of the first scroll A1 of the first scroll A is wound to the end of the end of the second scroll B1 of the second scroll B. A relief E communicating with the suction port D is provided by radially expanding the outer peripheral portion of approximately 180 degrees over the portion, and the relief E forms a suction passage. However, since the escape E is not only involved in the compression function but also serves as a suction passage, the diameter of the first scroll A is large, and the center of gravity of the spiral portion of the second scroll B is second.
There is a problem that a so-called center-of-gravity unbalance component that deviates from the center of gravity of the scroll increases.

Therefore, a scroll compressor which effectively utilizes the outer peripheral portion from the winding end portion of the first scroll A1 to the winding end portion of the second scroll B1 of the second scroll B is disclosed in Japanese Examined Patent Publication. It was proposed as shown in Japanese Patent Publication No. 62-29601. In this conventional compressor, as shown in FIG. 8, the inner wall surface of the end of the first scroll A1 of the first scroll A is wound around the inner wall surface of the second scroll B1 of the second scroll B. By extending near the end end and forming the inner wall surface of this extension with the same involute curve as that of the first spiral body A1, and contacting the outer wall surface of the winding end end of the second spiral body B1. The region where the escape E is formed, that is, the region between the inner wall surface of the extension portion and the outer wall surface of the winding end portion of the second spiral body B1 is defined as the working space G.
It is made to contribute as. Therefore, according to this conventional compressor, the suction volume in the working space G can be increased as compared with the general compressor shown in FIG. 7, and in comparison with the case where the escape E is formed. Thus, the first scroll A can be miniaturized.

Further, in the scroll compressor configured as described above, as shown in FIG. 8, the winding start side (halftone dot portion) of the second scroll B1 in the second scroll B is scraped off,
The outer working space G, that is, the outer working space G formed between the inner wall surface of the first spiral body A1 and the outer wall surface of the second spiral body B1, is the outer wall surface of the first spiral body A1 and the second spiral body. B
The inner working space Y formed between the inner wall surface and the inner wall surface of No. 1 is communicated with the discharge port C provided in the central portion in advance.
Outer working space G with increased suction volume due to the formation of the extension
The communication timing of the discharge port C to the discharge port C is set earlier than that of the inside working space Y so that the pressures when these both working spaces G and Y communicate to the discharge port C are made to be approximately the same pressure.

[0006]

However, in the scroll compressor configured as described above, the discharge port C has a circular shape having the same size as the discharge port C in the known scroll compressor shown in FIG. And the second spiral body B
Since the winding start side of No. 1 is scraped off to make the communication timing of the outer working space G to the discharge port earlier than the inner working space Y, there is no increase in the discharge fluid passage with respect to the increase in suction volume, and therefore the discharge port is increased. There is a problem that the flow velocity of the discharge fluid flowing through the nozzle increases and the discharge passage loss increases, resulting in power loss.

An object of the present invention is to make the pressures when the outer working space and the inner working space, which have increased suction volumes and increased suction volumes, communicate with the discharge port to be approximately the same, and to reduce the power generated by the different pressures. Another object of the present invention is to provide a scroll compressor that can eliminate not only loss but also power loss due to an increase in the flow velocity of the discharge fluid flowing through the discharge port.

[0008]

In order to achieve the above object, the present invention comprises a first scroll 2 and a second scroll 3 having end plates 21 and 31 and spiral bodies 22 and 32, and each scroll 2 , 3 are overlapped so as to mesh with each other at the positions where the end-of-winding ends of the spiral bodies 22, 32 are displaced by about 180 degrees, and the relative revolution movement of the first and second scrolls 2, 3 In the scroll compressor in which the working space formed between the spiral bodies 22 and 32 is moved in the direction of the discharge port provided at the center while reducing the volume to perform the compression action, the first scroll 2 The inner wall surface of the winding end end of the first spiral body 22 in is extended to near the winding end end of the second spiral body 32 in the second scroll 3, and the inner wall surface of the extension portion of the first spiral body 22 is
The discharge port 6 is formed by an envelope along with the revolution movement of the outer wall surface of the second spiral body 32 at the winding end portion of the second scroll 3, and the discharge port 6 is formed on the inner wall surface of the first spiral body 22 and the second spiral body 32. The outer working space X formed between the outer wall surface of the first spiral body 22 and the outer wall surface of the second spiral body 32.
The pre-opening portion 61 is provided to pre-open the inner working space Y formed between the inner working space Y and the inner wall surface.

The leading opening 61 of the discharge port 6 is
When the suction volume of the outer working space X is V1s, the suction volume of the inner working space Y is V2s, and the volume when the inner working space Y is minimum is V2d, the volume V1d of the outer working space X is

[0010]

[Equation 2]

In a state of being reduced to a size determined by, the outer scroll is substantially aligned with the outer wall surface 32g of the second scroll 32 of the second scroll 3 on the winding start side and precedes the inner working space Y. It is preferable to provide a contour 61a at which the space X starts to open to the discharge port 6.

[0012]

The inner wall surface of the winding end end of the first scroll 22 of the first scroll 2 is extended, and the inner wall surface of this extension and the second wall
Since the outer working space X is formed between the outer wall surface of the spiral body 32, the suction volume of the outer working space X can be increased, and the discharge capacity can be increased. Moreover, the first spiral body 22
When the outer working space X is formed between the inner wall surface of the second spiral body 32 and the outer wall surface of the second spiral body 32 to increase the suction volume, the volume of the outer working space X and the outer wall surface of the first spiral body 22 Since the volume of the inner working space Y formed between the inner wall surface of the spiral body 32 and the inner wall surface of the spiral body 32 is different, the pressure of the outer working space X becomes
Although the pressure becomes higher than the pressure in the inner working space Y, the discharge port 6 provided in the central portion has a preceding opening portion in which the outer working space X whose suction volume increases increases prior to the inner working space Y. Since 61 is provided, the outer working space X and the inner working space Y having an increased suction volume form the discharge port 6
The pressure at the time of communicating with can be made almost the same, power loss due to different pressures can be eliminated, and the passage area of the discharge fluid can be increased correspondingly because the preceding opening portion 61 is provided. As a result, the flow velocity of the discharge fluid flowing through the discharge port 6 can be prevented from increasing, the discharge passage loss due to the increase in flow velocity can be suppressed, and the power loss due to the increase in the discharge passage loss can be eliminated.

The advance opening portion 61 of the discharge port 6 is also provided.
By providing a contour that substantially coincides with the outer wall surface 32g on the winding start side of the second spiral body 32 in a state in which the volume V1d of the outer working space X is reduced to a size determined by the equation 1, Volume ratio (V
1d / V1s) and the volume ratio (V2d / V2s) in the inner working space Y can be made equal, and therefore the pressures when the respective working spaces X and Y communicate with the discharge port 6 can be made equal, and Since the port opening area of the discharge port 6 can be maximized, the power loss due to the different pressure and the power loss due to the increase in the discharge flow velocity can be more effectively eliminated.

[0014]

1 and 2, 1 is a closed casing having an intake passage 1a and a discharge passage 1b, 2 is a first scroll having an end plate 21 and a first scroll 22, and 3 is an end plate 31 as well. A second scroll having a second spiral body 32, wherein each of the scrolls 2 and 3 is provided with the spiral body 22,
The first and second scrolls 2 are fixed in the casing 1 and the second and third scrolls 3 are freely revolvably supported by vertically stacking the winding end ends of 32 so as to mesh with each other at a position displaced by approximately 180 degrees. The two scrolls 3 are interlocked with the motor 5 via the drive shaft 4. Incidentally, each of the spiral bodies 22,
32 is formed by an involute curve.

Further, the discharge port 6 is provided at the center of the end plate 21 of the first scroll 2, and the suction port is provided on the outer peripheral side at a portion facing the winding end 32a of the second spiral body 32. A port 7 is provided to reduce the volume of the working space formed between the spiral bodies 22 and 32 by the relative orbital motion of the first and second scrolls 2 and 3 in the direction of the discharge port 6. While moving it, the compression action is performed.

Then, the first of the second spiral body 32 is
End end 2 of the spiral body 22 drawn with an involute curve
The outer wall surface 3 at the winding end portion 32b in the range of approximately 180 ° from the facing portion a facing the 2a to the winding end edge 32a.
2c is gradually displaced toward the inner wall surface 32d so as to continuously reduce the thickness shown by the broken line in FIG. 1 from the facing portion a toward the winding end, and is different from the outer wall surface b drawn by the involute curve. The winding end portion 32b of the second spiral body 32 is formed thinner than the thickness of the other portions. This second spiral body 3
Since the winding end portion 32b of No. 2 is on the suction portion 2a side and exerts only a relatively small pressure, it is possible to provide sufficient strength even if the winding end portion 32b is formed thin. The tangent line between the involute curve forming the second spiral body 32 and the curve at the winding end portion 32b is
They match at their connection points, and both curves are smoothly continuous.

Further, the inner wall surface 22 of the first scroll 22 of the first scroll 2 drawn by an involute curve.
The winding end end 22a of b is extended to the vicinity of the winding end edge 32a of the second scroll 32 of the second scroll 3 continuously with the winding end end 22a, and the inner wall surface 22c at this extension is formed. , The winding end portion 3 of the second scroll 3
The outer wall surface 32c of FIG. 2b is formed by an envelope along with the orbital motion of the outer wall surface 32c so as to be in contact with the outer wall surface 32c of the winding end portion of the second spiral body 32 as shown in FIG. 22c and the outer wall surface 3 of the second spiral body 32
2c forms an outer working space X, and one end of the envelope forming the inner wall surface 22c of the first spiral body 22 has one end of the first spiral body 22 drawn by an involute curve. It coincides with the winding end portion 22a on the inner wall surface, and the envelope is smoothly continuous with the involute curve.

As described above, the inner wall surface 2 of the first spiral body 22
By forming the outer working space X by using 2c and the outer wall surface 32c of the second spiral body 32, the suction volume of the outer working space X is adjusted to the outer wall surface of the first spiral body 22 and the second spiral body 32. The suction volume of the inner working space Y formed between the inner wall surface and the inner wall surface can be increased, and the discharge capacity can be increased.
In this case, the suction volume of the outer working space X is larger than that of the inner working space Y, and when the working spaces X and Y enter the compression process and become close to the discharge, the pressure of the outer working space X is changed to the inner working space Y. Higher than the pressure. Therefore, the discharge port 6 is formed with a leading opening portion 61 that is larger than the normal size shown by the chain line in FIG. 3 toward the outer working space X immediately before communicating with the discharge port 6, and the first opening portion 61 is formed. Immediately before the winding start ends of the second spiral bodies 22, 32 are opened, the outer working space X is opened to the preceding opening portion 61 prior to the inner working space Y as shown in FIG. The compressor gas fluid of X is discharged into the inner working space Y prior to the discharge port 6
When the inner working space Y and the outer working space X communicate with the discharge port 6, the pressures are made approximately the same.

The preceding opening portion 61 has a suction volume V1s of the outer working space X and a suction volume V2 of the inner working space Y.
s, the volume when the inner working space Y is minimized, that is, the winding start portion 201 of the outer wall surface 22d of the first scroll 22 of the first scroll 2 is the winding of the second scroll 32 of the second scroll 3. When the minimum volume of the inner working space Y in the state of being in contact with or closest to the inner wall surface 32f on the starting side (state of FIG. 5) is V2d, the outer working space X is
Volume V1d of

[0020]

[Equation 3]

In a state of being reduced to a size determined by, the outer peripheral wall surface 32g of the second scroll 32 of the second scroll 3 on the winding start side substantially coincides with the inner working space Y in advance of compression. It is preferable to provide a contour 61a at which the outer working space X starts to open to the discharge port 6. By doing so, the volume ratio (V1d / V1s) of the outer working space X and the volume ratio (V2d / V2s) of the inner working space Y become equal, and when each of the working spaces X and Y communicates with the discharge port 6. Since the pressures can be made equal, the power loss due to the different pressures, that is, the power loss due to the overcompression caused by the increase in pressure can be more effectively eliminated, and the two-dot chain line in FIGS. As shown, the port opening area can be increased as compared with the discharge port when the preceding opening portion 61 is not provided.
The loss of the discharge passage due to the increase in the flow velocity of the discharge fluid flowing through the discharge port 6 can be eliminated, and the power loss due to the loss of the discharge passage can be effectively eliminated.

In the embodiment shown in the drawings, the outer wall surface 32c of the winding end portion 32b of the second spiral body 32 is displaced toward the inner wall surface 32d toward the winding end portion 32a so that the thickness is continuous. Since the inner wall surface 22c in the extension portion of the first spiral body 22 can be moved closer to the center side, the weight can be reduced by thinning the wall without lowering the strength. The first scroll 2 can be made smaller than the conventional one in which the inner wall surface of the end portion of the spiral body 22 is simply extended to form the outer working space, and the end portion 32b of the second spiral body 32 is formed. Can be arbitrarily set within a range that can provide sufficient strength. Therefore, it is possible to easily correct the imbalance of the center of gravity by the spiral body. Also, the second
Since the thickness of the winding end portion 32b of the spiral body 32 can be continuously reduced and the terminal end portion can be formed thin,
It is possible to reduce the resistance of the suction gas flow by the winding end face 32e of the spiral body 32. By forming the winding end surface 32e of the second spiral body 32 into a curved surface as shown in FIG. 1, the resistance of the suction gas flow can be further reduced.

Further, as described above, since the suction volume of the outer working space X can be increased, by setting the suction volume when the performance is not increased, the volume of the spiral member per unit volume can be increased. Since the diameter of the first scroll 2 can be reduced, the size of the first scroll 2 can be further reduced in combination with the reduction in size by thinning the winding end portion 32b of the second spiral body 32, and the entire compressor can be reduced in size.

Further, as shown in FIG. 1, the suction port 7 is to be opened radially outward in the end plate 21 of the first scroll 2 continuously with the end of the inner wall surface 22c in the extension portion. As a result, the flow of the suction gas fluid introduced from the suction port 7 into the suction portion 2a can be made smooth, and the suction port 7 has a rectangular shape as compared with the conventional one in which the suction port 7 is formed in the plate thickness direction of the end plate 21. The passage is not changed, the suction resistance can be reduced accordingly, and the pressure loss of the suction gas fluid can also be reduced.

In FIG. 2, 41 is a counterweight integrally provided on the upper end of the drive shaft 4, 42 is a swing link driven by the counterweight 41, and 43 is an Oldham ring.

In the embodiment described above, the outer wall surface 32c of the winding end portion 32b of the second spiral body 32 is displaced toward the inner wall surface 32d toward the winding end edge 32a. The thickness may be the same. Further, the compressor in which the first scroll 2 is fixed to the casing 1 and the second scroll 3 is revolvable has been described, but in addition, the first and second scrolls 2 and 3 are each rotatable about the axis. It may be a compressor.

[0027]

As described above, the present invention has the end plates 21 and 31.
The scroll 2 and the scroll 3 are provided with a first scroll 2 and a second scroll 3, and the scroll end portions of the scrolls 2 and 32 are deviated by about 180 degrees. Direction of the discharge port in which the working space formed between the spiral bodies 22 and 32 by the relative orbital motion of the first and second scrolls 2 and 3 is overlapped with each other so as to mesh with each other at a central portion. In a scroll compressor configured to move while reducing its volume to perform a compression action, the inner wall surface of the winding end end of the first scroll body 22 in the first scroll 2 is moved to the second scroll in the second scroll 3. The inner wall surface of the extension of the first spiral body 22 extending near the end of the winding of the body 32 is defined by the envelope curve of the outer wall surface of the second spiral body 32 at the end of the winding of the second scroll 3. When formed To, the discharge port 6, the first
An outer working space X formed between the inner wall surface of the spiral body 22 and the outer wall surface of the second spiral body 32 is formed between the outer wall surface of the first spiral body 22 and the inner wall surface of the second spiral body 32. Since the preceding opening portion 61 that opens prior to the inner working space Y is provided, the suction volume of the outer working space X can be increased,
The discharge port 6 can be increased while increasing the discharge capacity.
Since the preceding opening portion 61 is provided in the above, the pressure when the outer working space X and the inner working space Y whose suction volumes are increased communicate with the discharge port 6 can be made almost the same pressure, and the power loss due to the different pressures, That is, it is possible to eliminate power loss due to overcompression of the compressed fluid in the outer working space X. Moreover, since the preceding opening 61 is provided, in order to increase the passage area of the discharge fluid, As a result, the flow velocity of the discharge fluid flowing through the discharge port 6 can be prevented from increasing, the discharge passage loss due to the increase in flow velocity can be suppressed, and the power loss due to the discharge passage loss can be eliminated.

The preceding opening portion 61 of the discharge port 6 is also provided.
In addition, in a state where the volume V1d of the outer working space X is reduced to a size determined by the equation 1, a contour 61a that substantially coincides with the outer wall surface 32g on the winding start side of the second spiral body 32.
Since the volume ratio (V1d / V1s) in the outer working space X and the volume ratio (V2d / V2s) in the inner working space Y can be made equal by providing the above, the respective working spaces X and Y are discharged. The pressure when communicating with the port 6 can be equalized, and the discharge port 6
Therefore, the power loss due to the difference in pressure and the power loss due to the increase in the discharge flow velocity can be effectively eliminated.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of only a main part of a compressor of the present invention.

FIG. 2 is a vertical cross-sectional view in which a part of the compressor is omitted.

FIG. 3 is an enlarged sectional view of only a portion on a discharge port side.

FIG. 4 is an explanatory diagram of a state where the discharge stroke of FIG. 3 has progressed.

FIG. 5 is an explanatory diagram showing a state where the discharge stroke of FIG. 4 has further advanced.

6 is an explanatory view of a state where the discharge stroke of FIG. 5 has further advanced.

FIG. 7 is a cross-sectional view showing only a main part of a conventional example.

FIG. 8 is a cross-sectional view showing only a main part of a conventional example.

[Explanation of symbols]

 2 1st scroll 21 End plate 22 1st spiral body 3 2nd scroll 31 End plate 32 2nd spiral body 32g Outer wall surface on the winding start side 6 Discharge port 61 Preceding opening part 61a Contour

Claims (2)

[Claims] 1. A first scroll 2 and a second scroll 3 having end plates 21 and 31 and spiral bodies 22 and 32 are provided, and these scrolls 2 and 3 are provided at the end of winding of the spiral bodies 22 and 32. The parts are overlapped so as to mesh with each other at a position deviated by about 180 degrees, and the working space formed between the spiral bodies 22 and 32 is formed by the relative revolution movement of the first and second scrolls 2 and 3. In a scroll compressor in which the volume is reduced in the direction of the discharge port provided in the central portion to perform the compression action, the inner wall surface of the winding end end portion of the first scroll 22 in the first scroll 2 is The second
The scroll 3 extends near the winding end of the second scroll 32, and the inner wall surface of the extension of the first scroll 22 is the outer wall surface of the second scroll 32 at the winding end of the second scroll 3. The discharge port 6 is formed by an envelope along with orbital motion, and the outer working space X formed between the inner wall surface of the first spiral body 22 and the outer wall surface of the second spiral body 32 forms the first working space. A scroll compressor, comprising: a leading opening portion 61 that is opened prior to an inner working space Y formed between the outer wall surface of the spiral body 22 and the inner wall surface of the second spiral body 32. 2. The preceding opening portion 61 of the discharge port 6 has a suction volume of the outer working space X of V1s, a suction volume of the inner working space Y of V2s, and a volume when the inner working space Y is minimum, V2d. And the volume V of the outer working space X
1d is The outer wall surface 32 on the winding start side of the second scroll 32 of the second scroll 3 in a state of being reduced to a size determined by
The scroll compressor according to claim 1, further comprising a contour 61a which substantially coincides with g and which starts to open the outer working space X to the discharge port 6 prior to the inner working space Y.