JP5396235B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor used in a refrigeration air conditioner or the like.

  A scroll compressor with low vibration and low noise characteristics has a suction chamber at the outer periphery of the wrap that forms the compression space, and a discharge port is provided at the center of the wrap, determined by the suction volume and the final compression chamber volume. The volume ratio is constant. In particular, when the fluctuation of the compression ratio determined by the suction pressure and the discharge pressure is small, by setting the volume ratio according to the change, the discharge valve device is not required, and highly efficient compression can be performed. A reciprocating compressor or a rotary compressor requires a discharge valve device.

  When this scroll compressor is used as a refrigerant compressor for a refrigeration air conditioner, the refrigerant suction pressure and the discharge pressure change due to variable speed operation or fluctuations in the air conditioning load. And undercompression and overcompression operation occur due to the difference between the actual compression ratio and the set compression ratio.

  At the time of insufficient compression, the high-pressure refrigerant gas in the discharge chamber flows back intermittently from the discharge port to the compression chamber, leading to an increase in compression input. Further, at the time of over-compression, there is a compression chamber that becomes a pressure larger than the discharge pressure during the compression, so that an extra operating torque is required and the compression input increases.

  For this reason, in a compression space having a compression chamber that is a constantly sealed space that does not intermittently communicate with either the suction chamber or the discharge chamber, a bypass hole is provided at a symmetrical position that leads from the compression chamber to the discharge chamber. Means for preventing over-compression by providing a bypass valve device that allows only fluid outflow to the discharge chamber on the outlet side is known. For example, it is patent document 1. FIG. Note that the symmetry here means point symmetry with respect to the spiral center.

JP-A-9-170574

  During over-compression, high-pressure refrigerant may be allowed to escape from the bypass hole, but when the refrigerant passes through the bypass hole, a loss called discharge pressure loss that is inversely proportional to the cross-sectional area of the bypass hole occurs. If the bypass hole is enlarged so as to reduce the discharge pressure loss, a problem of residual gas described later arises. Alternatively, if it is attempted to increase the discharge port in order to reduce the discharge pressure loss, the number of turns of the spiral decreases, and a desired pressure cannot be obtained.

  Further, in the asymmetric scroll wrap, since the volume changes of the paired orbiting scroll inner line side compression chamber and the outer line side compression chamber are different, when the bypass holes are arranged symmetrically, if the bypass holes are constantly communicated with the compression chambers, Further, it is necessary to install an extra bypass hole in the compression chamber unique to the asymmetric wrap formed when the suction is completed between the outermost peripheral portion of the wrap of the orbiting scroll and the inner peripheral wall of the fixed scroll.

  An object of this invention is to improve the compression efficiency of an overcompression area | region. Another object of the present invention is to increase the overall compression efficiency through the under-compression region and the over-compression region, that is, the entire operation compression ratio region.

The purpose of the present invention is to
A compression chamber is formed by the wraps of the orbiting scroll and the fixed scroll to discharge the compressed refrigerant from the discharge port, and from the compression chamber through the release flow path so that the pressure in the compression chamber does not become too high. In a scroll compressor equipped with a release valve device for releasing pressure,
Two compression chambers that are paired with respect to the center of the vortex, each including two release passages and two release valve devices, each provided in two compression chambers closest to the discharge port,
The release valve devices are arranged asymmetrically with respect to the center of the spiral, and the two compression chambers in a state immediately before the two compression chambers communicate with the discharge port and the two compression chambers from the state are 180 degrees. And the two compression chambers that are in communication with the discharge port in a state of being forwardly moved, at least one of the release valve devices is disposed at a position that communicates with the discharge port. ,
The fixed scroll end plate portion is not provided with a discharge valve device for avoiding insufficient compression at the outlet of the discharge port, and the outlet of the discharge port and the discharge chamber of the scroll compressor are directly communicated with each other. Achieved by a scroll compressor .

  According to the present invention, the compression efficiency in the overcompressed region can be increased. Moreover, according to this invention, the whole compression efficiency through the whole driving | operation compression ratio area | region can be improved.

Sectional drawing of the vertical scroll compressor of this embodiment. Sectional drawing along the AA line in FIG. Sectional drawing when the compression space in FIG. 2 advances 180 degrees. Sectional drawing which showed the sequential change of the compression space in FIG. FIG. 6 is a layout view of a release valve device. Arrangement of retainer and release valve device to fixed scroll. The characteristic view which shows the volume change and pressure change state of a compression chamber. The characteristic view which shows the relationship between discharge space and discharge pressure loss.

  Hereinafter, an embodiment of the present invention will be described with reference to FIGS.

  FIG. 1 is a sectional view of a vertical scroll compressor. As a main configuration, a refrigerant mixture in which at least one or two or more of a fluorocarbon hydrogen refrigerant group is mixed as a refrigerant is used. An electric motor 2 is driven inside the hermetic container 1 by the electric motor 2. A scroll compression mechanism 3 that compresses the mixed refrigerant is disposed between the orbiting scroll 13 and the fixed scroll 14, and the fixed scroll 14 is configured to perform the orbiting motion without rotating the orbiting scroll 13 relative to the fixed scroll 14. And an Oldham ring 15 as a rotation restricting member that supports and guides between the rotating member and the fixing member 16.

  The compression mechanism 3 is configured by meshing a fixed scroll 13 and a turning scroll 14. The orbiting scroll 14 is rotated by the rotation of the electric motor 2 via the crankshaft 8 while being restricted by the Oldham ring 15. 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 discharged from the discharge pipe 18 to the outside of the sealed container 1. Discharged.

  A discharge valve device is not disposed at the outlet of the discharge port 7 in the end plate portion of the fixed scroll 14. If this is present, the refrigerant cannot be discharged unless the pressure of the compressed refrigerant is higher than the pressure in the discharge space, that is, the discharge chamber, so that insufficient compression does not occur. However, since an obstacle is also placed in the flow path, it is not preferable to dispose the discharge valve device from the viewpoint of reducing the discharge pressure loss. Accordingly, no discharge valve device is provided, and the outlet of the discharge port 7 is directly communicated with the discharge chamber.

  The discharged refrigerant circulates in the refrigeration cycle and is sucked again into the sealed container 1 from the suction pipe 17. The hermetic container 1 is configured by welding a lid chamber 4 and a bottom chamber 5 up and down to a cylindrical case 6.

  The entire inside of the iron hermetic container 1 shown in FIG. 1, that is, the discharge chamber is a so-called high pressure chamber type compressor in which a high pressure atmosphere communicating with the discharge pipe 18 is formed. As the electric motor 3 rotates, the refrigerant gas is discharged from the discharge port 7 at the center of the fixed scroll 14 to the upper part of the sealed container 1. The orbiting scroll 13 that meshes with the fixed scroll 14 to form a compression chamber includes a spiral orbiting scroll wrap 11S and a lap support disk 9 (not shown) in which an orbiting shaft is upright. The fixed scroll 14 includes an end plate 10 and a spiral fixed scroll wrap 11F. A discharge port 7 is disposed at the center of the fixed scroll wrap 11F, and a suction port 12 is disposed at the outer peripheral portion.

  Reference numeral 26 denotes a release valve device for releasing pressure from the compression chamber so that the pressure in the compression chamber does not become too high.

  FIG. 2 is a view showing a cross section taken along line AA in FIG. 50a is a first compression chamber, 51a is a second compression chamber, 51b is a third compression chamber, the release flow path is in order from the outer diameter side, 22 is a first release flow path, 23 is a second release flow path, 24 Is a third release channel, and 25 is a fourth release channel.

  Four or more release valve devices 26 are provided so that at least one release channel is disposed in the compression chamber in the middle of compression. This is to prevent over-compression and improve the compression efficiency in an operating state where the compression ratio is large.

  FIG. 2 shows a state of the compression space immediately before the second compression chamber 51 a and the third compression chamber 51 b that intermittently communicate with the discharge port 7 are opened with the discharge port 7. The release channel 28 (see FIG. 5) has an opening to the compression chamber set to be smaller than the width of the orbiting scroll wrap 11S, that is, the tooth tip, and the second compression chamber 51a and the third compression chamber 51b are paired. Correspondingly, a third release channel 24 and a fourth release channel 25 are arranged.

  FIG. 3 shows the state of the compression space when the orbiting scroll lap in FIG. 2 advances 180 degrees at the rotation angle of the crankshaft 8. In this state, the discharge port 7, the second compression chamber 51a, and the third 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 closed spaces, they can no longer be called compression chambers, but they are called compression chambers for convenience. Further, the fourth release flow path 25 is also communicated with this space, and FIG. 3 shows a state immediately before the fourth release flow path 25 is closed.

  That is, the third release flow path 24 and the fourth release flow path 25, that is, the release valve devices corresponding to these, are two compression chambers that are paired with respect to the center of the spiral, and are closest to the discharge port 7. The two compression chambers (51a, 51b) are provided asymmetrically with respect to the spiral center. Each release valve device has two compression chambers (51a, 51b) immediately before the two compression chambers (51a, 51b) communicate with the discharge port 7, and the two compression chambers advance 180 degrees from that state. The two compression chambers (60) communicating with the discharge port 7 in a state where the release valve device is in a state where at least one of the release valve devices communicates with the discharge port 7. Yes. And according to this structure, in addition to the discharge port 7 at the time of overcompression, discharge | release from the release flow paths 24 and 25 is attained, and the effect which expands a discharge port, without making the number of spirals small is acquired. That is, the discharge pressure loss can be reduced.

  FIG. 4 is a view showing a state in which the third release flow path 24 and the fourth release flow path 25 in FIGS. 2 and 3 are sequentially opened and closed as the orbiting scroll wrap 11S moves. ) → (c) → (d) → (a) → (b) → The rotational angle of the orbiting scroll wrap 11S advances in the order of. 2B shows an intermediate state between FIG. 2A and FIG. 3C, and FIG. 3D shows the state of FIG. 3C. 2 shows an intermediate state with respect to (a) which is the state of 2.

  At the next moment (a), the third release channel 24 communicates with the discharge port 7. The third compression chamber 51b communicates with the discharge port 7 shortly before the rotation angle advances (b). At this time, the fourth release flow path 25 communicates with the discharge port 7. After that, the communication between the third release flow path 24 and the discharge port 7 is cut off to become (b).

  While the rotation angle advances from (b) to (c), the fourth release flow path 25 communicates with the discharge port 7. At the next moment of (c), the communication between the fourth release flow path 25 and the discharge port 7 is cut off. Then, although the rotation angle advances to (d), there is no release flow path communicating with the discharge port 7. Thereafter, when the rotation angle further advances to the state (a), the third release flow path 24 communicates with the discharge port 7 at the next moment. Hereinafter, the same situation is repeated.

  With this configuration, the third release channel 24 and the fourth release channel 25 are always open with respect to the compression chamber communicating with the discharge port 7 in the section of FIGS. That is, as shown in FIG. 8, when the volume opened to the discharge port 7, that is, the space serving as the discharge pressure is large, the release flow path functions. On the contrary, the release flow path does not function when the space serving as the discharge pressure is small.

  Next, the release valve device 26 will be described with reference to FIG. FIG. 5 is an enlarged cross-sectional view of the release valve device 26 of FIG. 1 in a closed state. 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 higher than the discharge pressure. The release valve device 26 has a plurality of compression chambers formed in the scroll compression mechanism 3 portion. Correspondingly, it is installed at a plurality of locations of the fixed scroll 14. The release valve device 26 is normally closed, and gas or liquid refrigerant, mist-like lubricating oil or the like is sucked into the compression chamber as a working fluid from the suction port 12, so that the orbiting scroll 13 performs the orbiting 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 opens to connect the compression chamber and the discharge pressure space 27 in the sealed container 1.

  The release valve device 26 includes a release flow path 28, a release valve 29, a valve pressing body 30, a retainer 31, and an elastic portion 33. The guide part 32 guides the movement of the valve pressing body 30. Among these, the release flow path 28, the release valve 29, the valve pressing body 30, and the elastic portion 33 are formed in the end plate 10 portion of the fixed scroll 14 so as to communicate the compression chamber and the discharge pressure space 27. The release valve 29 opens and closes a release flow path 28 formed of a circular thin iron plate, and blocks 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 portion 33 applies an elastic pressing force to the valve pressing body 30 at the same time as applying an elastic pressing force to the release valve 29. The valve pressing body 30 is moved by this force, but the movement of the valve pressing body 30 is restricted by the retainer 31. The retainer 31 is fixed to the fixed scroll 14.

  Since the valve pressing body 30 is disposed between the release valve 29 and the retainer, the valve pressing body 30 is arbitrarily installed on the fixed scroll end plate, so that the compression chamber volume immediately before communicating with the discharge port 7 can be obtained. It is possible to easily set the volume of the release channel 28 small. Thereby, when compared with the bypass hole, the backflow of the high-pressure refrigerant gas from the release flow path at the time of insufficient compression can be reduced.

  The installation of a bypass hole in the compression chamber near the discharge port that has a high pressure means that gas during compression remains in the release flow path in the compression chamber, which tends to reduce the compression efficiency. Therefore, the residual gas remaining in the bypass hole cannot be reduced to zero basically only by designating the angle range of the bypass hole. In addition, simply specifying the bypass hole installation position does not necessarily reduce the bypass hole channel volume, that is, the release channel. Depending on the thickness of the fixed scroll end plate, it is possible to make the bypass hole long.If so, the release flow path cannot be kept small, and the amount of residual gas can fluctuate. The effect of increasing cannot be expected.

  Therefore, by applying the release valve device, the volume of the release flow path 28 can be reduced to 1/5 or less as compared with the bypass hole structure. Such a small volume is controlled by the configuration of the release valve device 26 including the valve pressing body 30 and the like. Thereby, when the release valve 29 is closed, the re-expansion loss of the fluid remaining in the compression stroke can be suppressed to an allowable range or less.

  Further, when the release valve 29 is opened, the discharge pressure loss can be reduced because the release fluid 29 becomes a flow path for discharging the compressed fluid in addition to the discharge port 7.

  In the overcompression region, the volume of the release channel is almost unrelated to the efficiency improvement, but with the above configuration, the compression efficiency can be increased in the undercompression region.

  FIG. 6 shows the fixed scroll 14 from the lid chamber 4 side, and the retainer 31 is designed so as to follow the plurality of release flow paths 28 and the discharge ports 7.

  FIG. 7 is a PV diagram of a scroll compressor in which the horizontal axis represents the volume change of the compression chamber and the vertical axis represents the pressure change of the compression chamber. A one-dot chain line shows a theoretical adiabatic compression diagram.

  In particular, the pressure ratio under an intermediate condition such as during low-speed operation of the compressor becomes smaller than the pressure ratio set in the rated load operation state, resulting in an overcompression state. In such a case, the release valve 29 that closes the third release flow path 24 and the fourth release flow path 25 is opened, and the compressed fluid flows out into the discharge pressure space 27, and the increase in the compression chamber pressure reaches the discharge pressure. It is limited and the increase in compression load can be suppressed.

  In an ideal state where there is no re-expansion loss of the fluid remaining in the compression stroke when the release valve 29 is closed, the compression chamber pressure loss is mainly caused by the discharge pressure loss, and the rest is the fixed scroll wrap 11F and the orbiting scroll wrap. This is caused by the leakage of the refrigerant with 11S. As shown in FIGS. 2, 3, and 8, each compression chamber 60 communicating with the discharge port 7 is a position where the release flow path can function when the volume opened to the discharge port 7 is large. Thus, the release valve device 26 is disposed at a position where the release flow path 28 is not blocked by the orbiting scroll wrap 11S, and the two release valve devices 26 are provided asymmetrically with respect to the spiral center.

  In other words, the third release channel 24 and the fourth release channel 25, that is, the release valve devices corresponding to these, are two compression chambers that are paired with respect to the center of the spiral, 7 are provided in the two compression chambers (51a, 51b) closest to 7, respectively, and are arranged asymmetrically with respect to the spiral center. Each release valve device has two compression chambers (51a, 51b) immediately before the two compression chambers (51a, 51b) communicate with the discharge port 7, and the two compression chambers advance 180 degrees from that state. The two compression chambers (60) communicating with the discharge port 7 in a state where the release valve device is in a state where at least one of the release valve devices communicates with the discharge port 7. Yes.

  As a result, in the overcompression region, it is possible to obtain the effect of discharging from the release flow path 28 in addition to the discharge port 7 and to expect a reduction in discharge pressure loss. Furthermore, by applying the release valve device, the re-expansion loss remaining in the compression stroke can be reduced, and the effect of suppressing leakage of the high-pressure refrigerant gas to the compression chamber can be expected. it can. Therefore, the outer compression line A shown in FIG. 7 can be brought closer to the compression line B closer to the theoretical adiabatic compression line. Here, the reason why the asymmetrical arrangement is provided is that the release chamber communicated 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 the channel 28 can be set effectively.

  With the above configuration, the re-expansion loss in the compression process can be reduced and the discharge pressure loss can be reduced, so that the compression efficiency in the overcompression region can be increased. Therefore, the overall compression efficiency through the entire operation compression ratio region can be increased in combination with the above configuration.

DESCRIPTION OF SYMBOLS 1 Airtight container 2 Electric motor 3 Compression mechanism 4 Lid chamber 5 Bottom chamber 6 Case 7 Discharge port 8 Crankshaft 9 Lap support disk 10 End plate 11F Fixed scroll lap 11S Orbiting scroll wrap 12 Suction port 13 Orbiting 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 channel 23 Second release channel 24 Third release channel 25 Fourth release channel 26 Release valve device 27 Discharge pressure space 28 Release flow path 29 Release valve 30 Valve pressing body 31 Retainer 32 Guide part 33 Elastic part 60 Each compression chamber communicated with the discharge port

Claims (4)

A compression chamber is formed by the wraps of the orbiting scroll and the fixed scroll to discharge the compressed refrigerant from the discharge port, and from the compression chamber through the release flow path so that the pressure in the compression chamber does not become too high. In a scroll compressor equipped with a release valve device for releasing pressure,
Two compression chambers that are paired with respect to the center of the vortex, each including two release passages and two release valve devices, each provided in two compression chambers closest to the discharge port,
The release valve devices are arranged asymmetrically with respect to the center of the spiral, and the two compression chambers in a state immediately before the two compression chambers communicate with the discharge port and the two compression chambers from the state are 180 degrees. And the two compression chambers that are in communication with the discharge port in a state of being forwardly moved, at least one of the release valve devices is disposed at a position that communicates with the discharge port. ,
The fixed scroll end plate portion is not provided with a discharge valve device for avoiding insufficient compression at the outlet of the discharge port, and the outlet of the discharge port and the discharge chamber of the scroll compressor are directly communicated with each other. A scroll compressor characterized by that. In claim 1,
The release valve device is provided in the release passage and a large guide portion of the volume than this is formed within the fixed scroll,
A valve pressing body whose movement is guided by the guide portion;
A release valve that blocks communication between the compression chamber and the guide portion;
An elastic portion that is disposed between the valve pressing body and the release valve and generates an elastic force;
A scroll compressor comprising a retainer disposed on the fixed scroll for restricting the movement of the valve pressing body. In claim 1,
A scroll compressor characterized in that at least four release valve devices are provided. In claim 1,
The scroll compressor is characterized in that a compression mechanism of the scroll compressor is an asymmetric wrap type.

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