KR101208141B1 - Scroll compressor - Google Patents

Abstract

In the case of overcompression, a high-pressure refrigerant can be discharged from the bypass hole. However, when the refrigerant passes through the bypass hole, a loss called discharge pressure loss inversely proportional to the cross-sectional area of the bypass hole occurs. An object of the present invention is to increase the compression efficiency of the overcompression region.
Two compression chambers paired with respect to the spiral center, each having two release valve devices provided in two compression chambers closest to the discharge port, and each release valve device is disposed asymmetrically with respect to the spiral center; Both of the two compression chambers in a state immediately before the two compression chambers communicate with the discharge port, and the two compression chambers communicated with the discharge port with the two compression chambers advanced 180 degrees from the state. A compression compressor in a state, wherein at least one of the respective release valve devices is disposed at a position in communication with the discharge port.

Description

[0001] SCROLL COMPRESSOR [0002]

TECHNICAL FIELD This invention relates to the scroll compressor used for a refrigeration air conditioning apparatus.

In the scroll compressor having low vibration and low noise characteristics, the suction chamber is located at the outer periphery of the wrap forming the compression space, and the discharge port is provided at the center of the wrap, and the volume ratio determined by the suction volume and the final compression chamber volume is constant. In particular, in the case where the variation in the compression ratio determined by the suction pressure and the discharge pressure is small, by setting the volume ratio according thereto, it is possible to perform compression with high efficiency without requiring a discharge valve device. In a reciprocating compressor or a rotary compressor, a discharge valve device is required.

When the scroll compressor is used as a refrigerant compressor for a refrigeration air conditioner, the suction pressure and the discharge pressure of the refrigerant are changed by the variable speed operation or the change of the air conditioning load. Then, under compression and overcompression operation occur due to the difference between the actual compression ratio and the set compression ratio.

In the under compression, the high pressure refrigerant gas in the discharge chamber intermittently flows back from the discharge port to the compression chamber, causing an increase in the compression input. In addition, at the time of overcompression, since there is a compression chamber which becomes a pressure larger than the discharge pressure during compression, unnecessary operating torque is required by that, resulting in an increase in compression input.

Therefore, in the compression space which has a compression chamber which always becomes a sealed space which does not intermittently pass through neither a suction chamber nor a discharge chamber, a bypass hole arrange | positioned at the symmetrical position from the said compression chamber to the discharge chamber is formed, and the exit of a bypass hole is made. Means for preventing overcompression by providing a bypass valve device allowing only fluid outflow to the discharge chamber on the side. For example, Patent Document 1. In addition, symmetry here means point symmetry with respect to a spiral center.

[Patent Document 1] Japanese Patent Application Laid-open No. Hei 9-170574

In the case of overcompression, a high-pressure refrigerant can be discharged from the bypass hole, but when the refrigerant passes through the bypass hole, a loss called discharge pressure loss inversely proportional to the cross-sectional area of the bypass hole occurs. If the bypass hole is enlarged to reduce the discharge pressure loss, a problem of residual gas described later occurs. Alternatively, when the discharge port is reduced and the discharge port is increased, the number of spiral windings decreases, and the desired pressure cannot be obtained.

In the asymmetrical scroll wrap, the volume change of the pair of swing scroll inner compression chambers and the outer compression chambers is different, and when the bypass holes are symmetrically arranged, if the bypass holes are always connected to the compression chambers, the swing scroll It is necessary to provide a bypass hole unnecessarily in the compression chamber peculiar to the asymmetric wrap formed at the completion of suction by the wrap outermost peripheral portion and the fixed scroll inner peripheral wall.

An object of the present invention is to increase the compression efficiency of the overcompression region. In addition, an object of the present invention is to increase the overall compression efficiency through the under compression region and the over compression region, i.e., the overall operation compression ratio region.

SUMMARY OF THE INVENTION [0006]

A release valve device for forming a compression chamber by each of the swivel scrolls and the fixed scrolls to discharge the refrigerant compressed from the discharge port, and to discharge the pressure from the compression chamber so that the pressure in the compression chamber is not too high. In one scroll compressor,

Two compression chambers paired with respect to a spiral center, and having two said release valve devices respectively installed in two compression chambers closest to said discharge port,

Each of the release valve devices is arranged asymmetrically with respect to a spiral center, and the two compression chambers and the two compression chambers advanced 180 degrees from the state immediately before the two compression chambers communicate with the discharge port. It is a compression chamber of both states of the said two compression chambers which communicated with the said discharge port in the state, Comprising: At least one of each said release valve apparatus is achieved by the scroll compressor arrange | positioned in the position which communicates with the said discharge port.

According to the present invention, the compression efficiency of the overcompression region can be increased. In addition, according to the present invention, it is possible to increase the overall compression efficiency through the entire operating compression ratio region.

1 is a cross-sectional view of a vertical scroll compressor of the present embodiment.
2 is a cross-sectional view taken along line AA in FIG. 1.
3 is a cross-sectional view when the compression space in FIG. 2 is advanced 180 degrees.
4 is a cross-sectional view showing a sequential change in the compression space in FIG.
5 is a layout view of the release valve device.
6 is a layout view of a retainer and a release valve device on a fixed scroll;
7 is a characteristic diagram showing a volume change and a pressure change state of the compression chamber.
8 is a characteristic diagram showing a relationship between a discharge space and a discharge pressure loss;

EMBODIMENT OF THE INVENTION Hereinafter, one Embodiment of this invention is described, referring FIGS. 1-3.

1 is a cross-sectional view of a vertical scroll compressor. As a main structure, the mixed motor which mixed at least 1 type, or 2 or more types of carbon fluoride-type refrigerant | coolant group as a refrigerant | coolant is used, The electric motor 2 and this electric motor 2 are contained in the inside of the airtight container 1. A scroll compression mechanism 3 for compressing the mixed refrigerant is disposed between the swing scroll 13 and the fixed scroll 14 driven by the swing scroll 13, and the swing scroll 13 is pivoted without rotating against the fixed scroll 14. It has an Oldham ring 15 as a rotation regulating member which guides and guides between the fixed scroll 14 and the fixed member 16 so that it can move.

The compression mechanism 3 is configured by engaging the fixed scroll 13 and the revolving scroll 14. The swinging scroll 14 is driven while being rotated by the Oldham ring 15 by receiving the rotation of the electric motor 2 through the crankshaft 8. By this series of operations, the refrigerant gas sucked from the suction pipe 17 is compressed and discharged from the discharge port 7 into the chamber which is the discharge pressure space 27, and the refrigerant in the chamber is sealed from the discharge pipe 18. (1) It is discharged to the outside.

In the hard plate portion of the fixed scroll 14, the discharge valve device is not disposed at the outlet of the discharge port 7. If this exists, the refrigerant cannot be discharged unless the pressure of the compressed refrigerant becomes higher than the pressure of the discharge space, that is, the discharge chamber, so that insufficient compression does not occur. However, since obstacles may be placed in the flow path, it is not preferable to arrange the discharge valve device from the viewpoint of reducing discharge pressure loss. Therefore, the discharge valve device is not arranged, and the outlet of the discharge port 7 is directly communicated with the discharge chamber.

The discharged refrigerant circulates in the refrigerating cycle and is sucked into the sealed container 1 from the suction pipe 17 again. The airtight container 1 is comprised by the lid chamber 4 and the bottom chamber 5 welded up and down to the cylindrical case 6.

The whole inside of the steel sealed container 1, ie, the discharge chamber shown in FIG. 1, is a compressor of the so-called high pressure chamber type which becomes a high pressure atmosphere in communication with the discharge pipe 18. As shown in FIG. As the electric motor 2 rotates, the refrigerant gas is discharged from the discharge port 7 in the center of the fixed scroll 14 to the top of the sealed container 1. The swinging scroll 13 which meshes with the fixed scroll 14 and forms a compression chamber consists of the spiral-shaped swinging scroll wrap 11S and the lap support disk 9 (not shown) which made the pivoting shaft upright. The fixed scroll 14 consists of the hard board 10 and the spiral fixed scroll wrap 11F, and the discharge port 7 is arrange | positioned at the center part of the fixed scroll wrap 11F, and the suction port 12 is arrange | positioned at the outer peripheral part.

Reference numeral 26 is a release valve device, for discharging the pressure from the compression chamber so that the pressure in the compression chamber is not too high.

FIG. 2 is a diagram illustrating a cross section taken along a line A-A in FIG. 1. Reference numeral 50a denotes a first compression chamber, 51a denotes a second compression chamber, 51b denotes a third compression chamber, and the release passage is sequentially from the outer diameter side, 22 is the first release passage, 23 is the second release passage, and 24 is the third release. The flow path 25 is the fourth release flow path.

Four or more release valve | bulb apparatuses 26 are provided so that at least 1 or more release flow path may be arrange | positioned in the compression chamber during compression. This is to prevent overcompression and to improve the compression efficiency in an operating state with a high compression ratio.

FIG. 2 shows the state of the compression space immediately before the second compression chamber 51a and the third compression chamber 51b which are intermittently communicating with the discharge port 7 are opened with the discharge port 7. In the release flow path 28 (refer FIG. 5), the opening part to a compression chamber is set smaller than the width | variety of 11 S of turning scroll wraps, ie, the end, and is paired 2nd compression chamber 51a and 3rd compression chamber 51b. ), The third release flow passage 24 and the fourth release flow passage 25 are arranged.

FIG. 3 shows the state of the compression space when the turning scroll wrap in FIG. 2 is advanced 180 degrees at the rotation angle of the crankshaft 8. In this state, the discharge port 7, the 2nd compression chamber 51a, and the 3rd compression chamber 51b are all in communication (60). At this time, since the second compression chamber 51a and the third compression chamber 51b are not completely closed spaces, the second compression chamber 51a and the third compression chamber 51b are not compressed spaces. Moreover, the 4th release flow path 25 also communicates with this space, and FIG. 3 has shown the state just before the 4th release flow path 25 was closed.

That is, the 3rd release flow path 24 and the 4th release flow path 25, ie, each release valve apparatus corresponding to these, are two compression chambers paired with respect to the spiral center, and are the two closest to the discharge port 7 It is provided in compression chamber 51a, 51b, respectively, and is arrange | positioned asymmetrically with respect to a spiral center. In addition, each release valve apparatus has two compression chambers 51a and 51b which are in the state just before two compression chambers 51a and 51b communicate with the discharge port 7, and two compression chambers advance 180 degrees from the state. It is a compression chamber in both states of the two compression chambers 60 which communicate with the discharge port 7 in one state, and at least one of each release valve apparatus is arrange | positioned in the position which communicates with the discharge port 7. According to this configuration, the discharge passages 24 and 25 can be discharged in addition to the discharge port 7 at the time of overcompression, and the effect of expanding the discharge port without reducing the spiral number is obtained. That is, discharge pressure loss can be reduced.

4 is a view showing a state in which the third release flow passage 24 and the fourth release flow passage 25 in FIGS. 2 and 3 are opened and closed sequentially with the swing movement of the swing scroll wrap 11S. The rotation angle of the turning scroll wrap 11S advances in the order of (a)? (b)? (c)? (d)? (a)? (b)? (B) shows an intermediate state between (a) which is the state of FIG. 2 and (c) which is the state of FIG. 3, and (d) is (c) which is the state of FIG. The intermediate state of a) is shown.

In the next instant of (a), the third release flow passage 24 communicates with the discharge port 7. The third compression chamber 51b communicates with the discharge port 7 just before the rotation angle is advanced to (b). At this time, the fourth release passage 25 communicates with the discharge port 7. Thereafter, the communication between the third release flow passage 24 and the discharge port 7 is cut off, resulting in (b).

While the rotation angle is advanced from (b) to (c), the fourth release flow passage 25 communicates with the discharge port 7. At the next instant in (c), the communication between the fourth release flow path 25 and the discharge port 7 is cut off. And although the rotation angle advances to (d), there is no release flow path which communicates with the discharge port 7. After that, when the rotation angle further advances to the state of (a), the third release flow passage 24 communicates with the discharge port 7 at the next instant. The same situation is repeated below.

By this structure, in the section of FIG. 2, FIG. 3, the 3rd release flow path 24 and the 4th release flow path 25 are always opened with respect to the compression chamber which communicates with the discharge port 7. As shown in FIG. . That is, as shown in FIG. 8, when the volume opened to the discharge port 7, ie, the space which becomes discharge pressure, a release flow path functions. On the contrary, the release flow path does not function when the space of discharge pressure is small.

Next, the release valve device 26 will be described with reference to FIG. 5. 5 is an enlarged cross-sectional view in a closed state of the release valve device 26 of FIG. 1. The release valve device 26 is for discharging from the compression chamber to the discharge pressure space 27 when the pressure in the compression chamber becomes equal to or greater than the discharge pressure, and the plurality of compression chambers formed in the portion of the scroll compression mechanism 3. In response to this, the plurality of fixed scrolls 14 are provided. This release valve device 26 is normally closed, and the gas coolant, the liquid coolant, the mist-like lubricating oil, etc. are sucked into the compression chamber as the working fluid from the suction port 12, and the swing scroll 13 is rotated by the turning motion. When the pressure in the compression chamber becomes equal to or higher than the discharge pressure in the process of compressing these working fluids, the release valve device 26 is opened to communicate the compression chamber and the discharge pressure space 27 in the sealed container 1.

The release valve apparatus 26 is provided with the release flow path 28, the release valve 29, the valve press body 30, the retainer 31, and the elastic part 33. As shown in FIG. The guide part 32 guides the movement of the valve press body 30. Among these, the release flow path 28, the release valve 29, the valve press body 30, and the elastic part 33 of the hard plate 10 of the fixed scroll 14 so that the compression chamber and the discharge pressure space 27 may communicate. It is formed in the part. The release valve 29 opens and closes the release flow path 28 formed of a circular steel sheet to block communication between the compression chamber and the guide portion. The valve pressing body 30 is for applying an elastic pressing force when the release valve 29 is closed by the elastic portion 33 and is disposed between the release valve 29 and the retainer 31. The elastic part 33 adds an elastic pressing force to the release valve 29 and also adds an elastic pressing force to the valve press body 30. The valve pressing body 30 is moved by this force, but the movement of the valve pressing body 30 is limited by the retainer 31. The retainer 31 is fixed to the fixed scroll 14.

Since the valve presser 30 is disposed between the release valve 29 and the retainer, the valve presser 30 is arbitrarily attached to the fixed scroll plate to release the pressurized chamber volume immediately before communication with the discharge port 7. It is possible to easily set the volume of the flow path 28 to be small. Thereby, the backflow of the high pressure refrigerant gas from the release flow path at the time of under compression can be reduced compared with a bypass hole.

Forming a bypass hole in the compression chamber at high pressure near the discharge port is likely to cause gas during compression to remain in the release flow path in the compression chamber, leading to a decrease in compression efficiency. Therefore, only by specifying the angle range of the bypass hole installation, the residual gas remaining in the bypass hole cannot be essentially zero. In addition, it is not necessary to reduce the bypass hole flow path volume, that is, the release flow path, by only specifying the bypass hole installation position. Depending on the thickness of the fixed scroll board, it is also possible to lengthen the bypass hole, and as a result, the release flow path cannot be suppressed small, and the amount of residual gas can fluctuate. Therefore, the effect of increasing the compression efficiency cannot be expected.

Therefore, compared with the bypass hole structure, by applying the said release valve apparatus, it became possible to reduce the volume of the release flow path 28 to 1/5 or less. The suppression of such a small volume depends on the configuration of the release valve device 26 including the valve press body 30 and the like. Thereby, the re-expansion loss of the fluid remaining in the compression stroke at the time of closing the release valve 29 can be suppressed below the allowable range.

In addition, at the time of opening of the release valve 29, since it becomes a flow path which discharges a compressed fluid in addition to the discharge port 7, discharge pressure loss can be reduced.

In the overcompression region, the volume of the release flow passage is largely irrelevant to the improvement in efficiency, but the above-described configuration can increase the compression efficiency in the undercompression region.

6 shows the fixed scroll 14 drawn from the lid chamber 4 side, and designs the retainer 31 in the form along the plurality of release flow paths 28 and the discharge port 7.

FIG. 7 is a P-V diagram of a scroll compressor showing changes in the volume of the compression chamber on the horizontal axis and changes in the pressure of the compression chamber on the vertical axis. The dashed-dotted line shows the theoretical adiabatic compression line diagram.

In particular, in refrigeration and air-conditioning equipment for home use and vehicle mounting, the pressure ratio in intermediate conditions (JIS C9612: 2005, JIS B8616: 2006), such as during low-speed operation of the compressor, which is said to have a high occurrence frequency during actual use, is rated load. It becomes smaller than the pressure ratio set in the operation state, and becomes overcompression state. In this case, the release valve 29 which closes the 3rd release flow path 24 and the 4th release flow path 25 is opened, and a compressed fluid flows out into the discharge pressure space 27, and a rise of a compression chamber pressure discharges it. It is limited to the pressure, and the increase in the compression load can be suppressed.

At the time of closing the release valve 29, in the ideal state in which there is no re-expansion loss of the fluid remaining in the compression stroke, the loss of the compression chamber pressure is a major factor of the discharge pressure loss, otherwise the fixed scroll wrap 11F and the swing scroll wrap Leakage of the refrigerant between 11S is a factor. 2, 3, and 8, in each compression chamber 60 communicated with the discharge port 7, the release flow path can function when the volume opened to the discharge port 7 is large. Position, and the release valve device 26 is arrange | positioned in the position where the release flow path 28 is not occluded by the turning scroll wrap 11S, respectively, and these two release valve devices 26 are installed asymmetrically with respect to a spiral center. do.

In other words, the third release flow passage 24 and the fourth release flow passage 25, that is, the respective release valve devices corresponding to these, are two compression chambers paired with respect to the spiral center, It is provided in two adjacent compression chambers 51a and 51b, respectively, and is arrange | positioned asymmetrically with respect to a spiral center. In addition, each release valve apparatus has two compression chambers 51a and 51b which are in the state just before two compression chambers 51a and 51b communicate with the discharge port 7, and two compression chambers advance 180 degrees from the state. It is a compression chamber in both states of the two compression chambers 60 which communicate with the discharge port 7 in one state, and at least one of each release valve apparatus is arrange | positioned in the position which communicates with the discharge port 7.

Thereby, in the overcompression region, in addition to the discharge port 7, the discharge effect from the release flow path 28 can also be obtained, and reduction of discharge pressure loss can be expected. In addition, the application of the release valve device can reduce the re-expansion loss remaining in the compression stroke, and the effect of suppressing the leakage of the high-pressure refrigerant gas into the compression chamber can be expected. . Therefore, the compression line A of the outer side shown in FIG. 7 can be made closer to the compression line B which is closer to a theoretical thermal insulation compression line. In this case, the asymmetrical installation may include a release passage 28 communicating with the discharge port 7 when the maximum sealed space of the paired compression chambers is different, that is, in the case of a scroll compressor having a so-called asymmetric wrap type compression mechanism. This is because it can be set effectively.

By the above structure, since the re-expansion loss in a compression process can be reduced and discharge pressure loss can be reduced, the compression efficiency in an overcompression area | region can be improved. Therefore, in addition to the above configuration, it is possible to increase the overall compression efficiency through the entire operation compression ratio region.

1: sealed container
2: electric motor
3: compression mechanism
4: cover chamber
5: bottom chamber
6: case
7: discharge port
8: crankshaft
9: lap support disk
10: hard board
11F: Fixed Scroll Wrap
11S: Turning Scroll Wrap
12: suction port
13: turning scroll
14: fixed scroll
15: Oldham Ring
16: fixed member
17: suction pipe
18: discharge pipe
50a: first compression chamber
51a: second compression chamber
51b: third compression chamber
22: first release euro
23: second release euro
24: third release euro
25: fourth release euro
26: release valve device
27: discharge pressure space
28: release euro
29: release valve
30: valve pressing body
31: Retainer
32: guide part
33: elastic part
60: each compression chamber connected to the discharge port

Claims (5)

A release valve device for forming a compression chamber by each of the swivel scrolls and the fixed scrolls to discharge the compressed refrigerant from the discharge port, and to discharge the pressure from the compression chamber so that the pressure in the compression chamber is not too high. In one scroll compressor,
Two compression chambers paired with respect to a spiral center, and having two said release valve devices respectively installed in two compression chambers closest to said discharge port,
Each of the release valve devices is arranged asymmetrically with respect to a spiral center, and the two compression chambers and the two compression chambers advanced 180 degrees from the state immediately before the two compression chambers communicate with the discharge port. A compression chamber in both states of the two compression chambers in communication with the discharge port in a state, and at least one of the respective release valve devices is disposed at a position in communication with the discharge port,
In the hard plate portion of the fixed scroll, the outlet of the discharge port and the discharge chamber of the scroll compressor are directly communicated with each other without a discharge valve device for avoiding under compression at the outlet of the discharge port.
Scroll compressor. The method of claim 1,
The said release valve apparatus is provided in the said fixed scroll in which the release flow path and the guide part larger in volume are formed,
A valve press member whose movement is guided by the guide portion,
A release valve for blocking communication between the compression chamber and the guide part;
An elastic portion disposed between the valve pressing member and the release valve and generating an elastic force;
And a retainer disposed on said fixed scroll to limit movement of said valve press body.
Scroll compressor. The method of claim 1,
At least four said release valve apparatus is provided, It is characterized by the above-mentioned.
Scroll compressor. The method of claim 1,
The compression mechanism of the scroll compressor is characterized in that the asymmetric wrap type.
Scroll compressor. delete

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