JP2012117392A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a scroll compressor capable of reducing high-frequency noise produced due to backflow of a high-pressure gas into a compression chamber when a discharge valve is closed.SOLUTION: In the scroll compressor 1 in which a fixed scroll 21 and a revolving scroll 22 are provided and gas compressed by a pair of compression chambers 23 formed between the scrolls 21, 22 is discharged from a center compression chamber 23A where both compression chambers 23 are joined, through discharge ports 26A, 26B and a discharge valve 27 into a discharge chamber 25, the discharge ports 26A, 26B, of at least two routes having route lengths L1, L2 different from each other, which are opened and closed by the discharge valve 27 are provided between the center pressure chamber 23A and a discharge chamber 25.

Description

  The present invention relates to a scroll compressor that can reduce noise generated due to the backflow of high-pressure gas when a discharge valve is closed.

  The scroll compressor includes a pair of fixed scrolls and a turning scroll, and a pair of compression chambers formed by meshing both scrolls is moved from the outer peripheral position to the center side along with the revolution turning motion of the turning scroll. It is configured to move while reducing the volume, thereby compressing the low-pressure gas into high-pressure gas, and discharging the compressed gas into the discharge chamber via a discharge port and a discharge valve provided at the center of the fixed scroll.

  In the scroll compressor, a discharge valve is provided at the discharge port as described above to prevent backflow of high-pressure gas from the discharge chamber side to the compression chamber side. However, it is known that noise is generated when the discharge valve is closed by installing the discharge valve. One of the noises is an impact sound caused by a collision with the seating surface when the discharge valve is closed, and the other is a part of the high-pressure gas from the discharge chamber side when the discharge valve is closed. This is a high-frequency sound caused by pulsation caused by the reverse flow, and the compressor body being vibrated by the pulsation.

  In order to reduce the noise when the discharge valve is closed, Patent Document 1 includes a plurality of discharge ports that communicate with the discharge port provided in the fixed scroll and the discharge chamber. A discharge valve made up of an integral elastic plate capable of opening and closing a port is shown with its base end fixed to a discharge cover.

JP 2002-242863 A

The thing shown by the said patent document 1 is set as the structure by which the some discharge port was provided side by side. However, this increases the flow rate when the gas discharged from any of the plurality of discharge ports flows along the discharge valve, and closes the discharge valve by applying a negative lift to the discharge valve in the vicinity of the discharge port. The impact noise caused by the collision with the seating surface at the time is reduced, and pulsation is generated by the backflow of high-pressure gas from the discharge chamber side into the compression chamber, and the compressor body is excited by the pressure wave. It was not possible to reduce the noise caused by the operation.
Thus, as for the noise generated due to the backflow of the high-pressure gas into the compression chamber when the discharge valve is closed, there is actually no effective solution yet.

  The present invention has been made in view of such circumstances, and is a scroll compression that can reduce high-frequency sound generated due to the backflow of high-pressure gas into the compression chamber when the discharge valve is closed. The purpose is to provide a machine.

In order to solve the above problems, the scroll compressor of the present invention employs the following means.
That is, a scroll compressor according to the present invention includes a fixed scroll and a turning scroll, and a center formed by a combination of gas compressed by a pair of compression chambers formed between the two scrolls. In a scroll compressor that discharges from a compression chamber to a discharge chamber via a discharge port and a discharge valve, at least two discharge ports having different path lengths opened and closed by the discharge valve are provided between the central compression chamber and the discharge chamber. It is provided.

  According to the present invention, between the central compression chamber formed by the pair of compression chambers formed by the fixed scroll and the orbiting scroll and the discharge chamber, the path length opened and closed by the discharge valve is different. Since the discharge port is provided, when the discharge valve is closed, the pulsation generated by the high-pressure gas flowing back from the discharge chamber side into the central compression chamber increases the time difference through at least two discharge ports having different path lengths. It will be generated at least twice. Accordingly, the pressure wave propagating into the central compression chamber by each pulsation can be reduced to about ½, and the scroll compressor is reduced in noise by preventing the compressor body from being vibrated to the high frequency range. be able to.

  Furthermore, the scroll compressor of the present invention is the above scroll compressor, wherein the discharge port of the first path among the discharge ports of the at least two paths is provided perpendicular to the end plate of the fixed scroll, The two-path discharge port is provided obliquely with respect to the first-path discharge port.

  According to the present invention, the discharge port of the first path among the discharge ports of the two paths is provided perpendicular to the end plate of the fixed scroll, and the discharge port of the second path is the discharge port of the first path. In contrast, since the discharge port of the second route is provided obliquely with respect to the discharge port of the first route provided vertically, a difference in the path length can be ensured between the discharge ports of the two routes. Can be secured. Therefore, the pressure wave propagated into the central compression chamber by the high-pressure gas flowing backward from the discharge chamber side into the central compression chamber can be reduced to about ½, and the scroll compressor can be reduced in noise.

  Furthermore, in the scroll compressor according to the present invention, in the scroll compressor, the discharge port of the second path has an opening end on the side of the central compression chamber joined with the discharge port of the first path. It is provided obliquely toward the discharge chamber side.

  According to the present invention, the discharge port of the second path has the opening end on the central compression chamber side joined with the discharge port of the first path, and is provided obliquely from there to the discharge chamber side. A required path length difference can be secured between the two discharge ports while reducing the distance between the opening ends of the two discharge ports opened to the discharge chamber side. Therefore, the pressure wave propagated into the central compression chamber by the high-pressure gas flowing back from the discharge chamber into the central compression chamber can be reduced without making the discharge valve large, and the scroll compressor can be reduced in noise.

  Furthermore, the scroll compressor of the present invention is the above-described scroll compressor, wherein the discharge port of the second path has the opening end on the discharge chamber side joined with the discharge port of the first path, and from there It is characterized by being provided obliquely toward the central compression chamber side.

  According to the present invention, the discharge port of the second path has the opening end on the discharge chamber side joined with the discharge port of the first path, and is provided obliquely from there toward the central compression chamber side. While reducing the distance between the open ends of the two-path discharge ports opened to the central compression chamber side, the two-path discharge ports are opened in the central compression chamber, and the required path length difference is set between the two-path discharge ports. Can be secured. Therefore, by simply improving the discharge port of the second path, the pressure wave propagated into the central compression chamber by the high-pressure gas flowing backward from the discharge chamber side into the central compression chamber is reduced, and the scroll compressor is made low in noise. Can be

  Furthermore, the scroll compressor of the present invention is the above scroll compressor, wherein the discharge port of the first path among the discharge ports of the at least two paths is provided perpendicular to the end plate of the fixed scroll, The two-path discharge port is provided so as to be bent in parallel with the discharge port of the first path.

  According to the present invention, the discharge port of the first path among the discharge ports of the two paths is provided perpendicular to the end plate of the fixed scroll, and the discharge port of the second path is connected to the discharge port of the first path. Since it is bent in parallel, the discharge port of the second path is bent and provided with respect to the discharge port of the first path provided vertically, so that the path can be reliably routed between the two discharge ports. A long difference can be secured. Therefore, the pressure wave propagated into the central compression chamber by the high-pressure gas flowing backward from the discharge chamber side into the central compression chamber can be reduced to about ½, and the scroll compressor can be reduced in noise.

  Furthermore, in the scroll compressor according to any one of the above-described scroll compressors, the at least two paths of the discharge ports may be compressed in the center by pulsation of high-pressure gas that flows backward from the discharge chamber into the center compression chamber. It is characterized in that the pressure wave propagated into the room is provided with a required path length difference so as to be propagated at least twice.

  According to the present invention, at least two paths of the discharge port cause the pressure wave propagating into the central compression chamber by the pulsation of the high pressure gas flowing back from the discharge chamber side into the central compression chamber to be propagated at least twice. Therefore, the central compression is performed by the high-pressure gas flowing backward from the discharge chamber side to the central compression chamber through the two discharge ports having the required path length difference. The pressure wave propagating into the room can be reliably propagated in two steps. Therefore, it is possible to reduce the pressure of the scroll compressor by reducing the pressure wave propagating into the central compression chamber to about ½ and preventing the compressor body from being vibrated to the high frequency range.

  According to the present invention, when the discharge valve is closed, the pulsation generated by the high pressure gas flowing backward from the discharge chamber side to the central compression chamber is caused at least twice with a time difference through the discharge ports of at least two paths having different path lengths. Therefore, the pressure wave propagating in the central compression chamber by each pulsation can be reduced to about ½, so that the compressor body is not vibrated to the high frequency range. The noise of the scroll compressor can be reduced.

It is the longitudinal cross-sectional view which abbreviate | omitted a part of scroll compressor which concerns on 1st Embodiment of this invention. It is explanatory drawing of the propagation state of the pressure wave which propagates in the center compression chamber of the scroll compressor shown in FIG. It is explanatory drawing of the noise reduction effect of the scroll compressor shown in FIG. It is a longitudinal cross-sectional view of the principal part of the scroll compressor which concerns on 2nd Embodiment of this invention. It is a longitudinal cross-sectional view of the principal part of the scroll compressor which concerns on 3rd Embodiment of this invention.

Embodiments according to the present invention will be described below with reference to the drawings.
[First Embodiment]
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. 1 to 3.
FIG. 1 is a longitudinal sectional view in which a part of the scroll compressor according to the first embodiment of the present invention is omitted.
The scroll compressor 1 includes a cylindrical housing 2 that constitutes an outer shell. This housing 2 is composed of a compressor housing 3 made of aluminum die casting each having a bottomed cylindrical shape, and a motor housing 4, and the flange portions 3A, 4A formed integrally with each other are connected to each other by O. It is integrated by fastening with a bolt 5 via a ring 6.

  A box-shaped inverter accommodating portion 7 is integrally provided on the outer periphery of the motor housing 4. In the inverter accommodating portion 7, an inverter that converts DC power supplied from a power supply unit (not shown) into three-phase AC power and applies it to the electric motor 10 provided in the motor housing 4 via the sealed terminal 8. A device (not shown) can be accommodated. The inverter device may be a well-known device and will not be described in detail.

  The electric motor 10 provided in the motor housing 4 includes a stator 11 and a rotor 12, and the stator 11 is fixed by being press-fitted into the inner peripheral surface of the motor housing 4. Between the stator 11 and the motor housing 4, gas passages (not shown) penetrating in the axial direction are provided at a plurality of locations in the circumferential direction. The low-pressure refrigerant sucked into the space 13 between the bottom surface of the motor housing 4 and the end surface of the electric motor 10 from the suction port (not shown) provided on the rear end side of the motor housing 4 through this gas passage. Gas can flow to the front side of the motor housing 4.

  A rotating shaft (crankshaft) 14 is integrally coupled to the rotor 12. The rear end portion of the rotary shaft 14 is rotatably supported by a bearing 15 provided on the bottom portion of the motor housing 4, and the front end portion thereof is freely rotatable by a main bearing 17 provided on the bearing member 16. It is supported. A crank pin 14 </ b> A that is eccentric by a predetermined dimension from the center of the rotating shaft is provided at the front end of the rotating shaft 14. The bearing member 16 is fixedly supported by a bolt 18 on the opening end side of the motor housing 4.

  On the other hand, a scroll compression mechanism 20 is provided in the compressor housing 3. The scroll compression mechanism 20 is a known compression mechanism configured by meshing a pair of fixed scrolls 21 and a turning scroll 22, and a pair of compression chambers 23 formed between both scrolls 21, 22 includes a turning scroll. The low-pressure refrigerant gas is compressed by being moved while reducing its volume from the outer peripheral position to the center side by the revolving and turning motion of 22.

  The fixed scroll 21 is fixedly installed on the bottom surface side of the compressor housing 3 with bolts 24, and a discharge chamber 25 is formed between the rear surface of the end plate and the bottom surface of the compressor housing 3. The discharge chamber 25 receives high-pressure gas from a central compression chamber 23 </ b> A formed by joining a pair of compression chambers 23 at the center through a plurality of first discharge ports 26 </ b> A and second discharge ports 26 </ b> B and discharge valves 27. The high pressure gas is discharged and discharged from the discharge chamber 25 to the outside through a discharge pipe connected to the discharge port 28. The discharge valve 27 is a reed valve that is configured by a leaf spring whose base end is fixed to the end plate of the fixed scroll 21 via a bolt, and the first and second discharge ports 26A and 26B open and close substantially simultaneously. It is possible.

  The orbiting scroll 22 is supported at its rear face by the thrust surface of the bearing member 16. In addition, a crank pin 14A of the rotary shaft 14 is connected to a boss portion 29 provided on the back surface of the end plate via a needle bearing 30 and a drive bush 31. It is configured to be. The orbiting scroll 22 is prevented from rotating through an Oldham ring 32 interposed between the rear face of the end plate and the bearing member 16. The drive bush 31 is integrally provided with a balance weight 33 for offsetting an unbalanced load accompanying the revolution turning drive of the turning scroll 22.

In the scroll compressor 1, the plurality of first discharge ports 26 </ b> A and second discharge ports 26 </ b> B provided in the fixed scroll 21 compress the high pressure gas from the discharge chamber 25 side when the discharge valve 27 is closed. In order to reduce the high-frequency sound generated due to the backflow in the chamber 23A, the following configuration is provided.
The first discharge port 26 </ b> A constitutes the discharge port of the first path among the discharge ports of at least two paths communicating between the central compression chamber 23 </ b> A and the discharge chamber 25. It is provided in the vertical direction. The path length of the first discharge port (discharge port of the first path) 26A is L1.

  The second discharge port 26B constitutes a discharge port of the second path among at least two discharge ports, and is inclined with respect to the first discharge port 26A constituting the discharge port of the first path. Is provided. The path length of the second discharge port (discharge port of the second path) 26B is L2. The path length L2 of the second discharge port 26B and the path length L1 of the first discharge port 26A are L1 <L2, and a required path length difference is secured.

  In the above, the required path length difference means that, when the discharge valve 27 is closed, the high pressure gas flows back into the central compression chamber 23A from the discharge chamber 25 side, and the pulsation generated accordingly causes the inside of the central compression chamber 23A. As shown in FIG. 2, there is a time difference between the pressure wave propagating to the first discharge port (first path discharge port) 26A and the second discharge port (second path discharge port) 26B. This means that it is provided with a path length difference that is propagated at least in a plurality of times (here, twice). This path length difference is desirably at least 7.6 mm or more from the analysis result.

  Further, the second discharge port 26B has an opening end on the central compression chamber 23A side joined with the first discharge port 26A, and is provided obliquely from there toward the discharge chamber 25 side. Thus, the distance between the opening ends of the first discharge port 26A and the second discharge port 26B that open on the discharge chamber 25 side is made as small as possible.

Thus, according to the present embodiment, the following operational effects are obtained.
In the scroll compressor 1, when the electric motor 10 is rotationally driven through the inverter device, low-pressure refrigerant gas is sucked into the space 13 through the suction port provided in the motor housing 4. The low-pressure gas passes through the gas passage between the stator 11 and the motor housing 4, cools the inverter device in the inverter housing portion 7 through the wall surface of the motor housing 4, and then enters the space between the electric motor 10 and the bearing member 16. From there, it circulates into the compressor housing 3 and is sucked into the pair of compression chambers 23 of the scroll compression mechanism 20.

  The low-pressure gas sucked into the pair of compression chambers 23 is compressed by moving both the compression chambers 23 toward the center side while reducing the volume in accordance with the revolving orbiting motion of the orbiting scroll 22. The compression chambers 23 are merged at the central portion, and the central compression chamber 23A is compressed by being communicated with the first discharge port 26A and the second discharge port 26B provided at the central portion of the fixed scroll 21. The high pressure gas pushes the discharge valve 27 open and is discharged into the discharge chamber 25. The high-pressure gas is sent to the refrigeration cycle side through the discharge port 28, circulates in the refrigeration cycle, and is then sucked into the scroll compressor 1 from the suction port again.

  In the above discharge stroke, when the pressure on the central compression chamber 23A side is lower than the pressure in the discharge chamber 25, the discharge valve 27 is closed. This prevents the high-pressure gas from flowing backward from the discharge chamber 25 side to the central compression chamber 23A side via the first discharge port 26A and the second discharge port 26B, but when the discharge valve 27 is closed. In addition, a part of the high-pressure gas flows back into the central compression chamber 23A.

  However, in the present embodiment, the path lengths L1 and L2 opened and closed by the discharge valve 27 between the central compression chamber 23A formed by joining the pair of compression chambers 23 at the center and the discharge chamber 25 are L1 <L2. The first discharge port 26A and the second discharge port 26B of at least two paths are provided. For this reason, when the discharge valve 27 is closed, the pulsation generated by the high-pressure gas flowing back from the discharge chamber 25 side into the central compression chamber 23A causes the first discharge port 26A and the first discharge port 26A of at least two paths having different path lengths L1 and L2. As shown in FIG. 2, the two discharge ports 26B are generated at least twice with a time difference.

  As a result, the pressure wave propagated in the central compression chamber 23A by each pulsation can be reduced to about ½, and as a result, as shown in FIG. The vibration of the scroll compressor 1 can be reduced and the noise can be reduced.

  In other words, in the present embodiment, the pressure waves propagated in the central compression chamber 23A by the high-pressure gas that flows back into the central compression chamber 23A from the discharge chamber 25 side in the first and second discharge ports 26A, 26B of at least two paths. Is provided with a path length difference so that it is propagated at least twice, so that the reverse flow flows from the discharge chamber 25 side into the central compression chamber 23A via the first and second discharge ports 26A and 26B. The pressure wave propagated in the central compression chamber 23A by the high-pressure gas to be transmitted can be reliably transmitted in two times. Accordingly, it is possible to reduce the noise of the scroll compressor 1 by reducing the pressure wave propagating into the central compression chamber 23A to about ½ and preventing the compressor body from being vibrated to a high frequency region.

  In addition, the first discharge port 26A of the two paths of discharge ports is provided perpendicular to the end plate of the fixed scroll 21, and the second discharge port 26B is provided obliquely with respect to the first discharge port 26A. Therefore, the path length L2 of the second discharge port 26B provided obliquely is longer than the path length L1 of the first discharge port 26A provided vertically, and the first and second discharge ports of the two paths are set. A difference in path length can be ensured between 26A and 26B. Therefore, the pressure wave propagated in the central compression chamber 23A by the high-pressure gas flowing back from the discharge chamber 25 into the central compression chamber 23A can be reduced to about ½, and the scroll compressor 1 can be reduced in noise. it can.

  Further, according to the present embodiment, the opening end of the second discharge port 26B on the central compression chamber 23A side is joined with the first discharge port 26A, and the second discharge port 26B is directed to the discharge chamber 25 side therefrom. It is provided diagonally. Therefore, the distance between the opening ends of the first and second discharge ports 26A and 26B of the two paths opened to the discharge chamber 25 side is made as small as possible while the distance between the first and second discharge ports 26A and 26B is reached. Therefore, it is possible to secure a required path length difference. This reduces the pressure wave propagated in the central compression chamber 23A by the high-pressure gas flowing backward from the discharge chamber 25 side into the central compression chamber 23A without increasing the discharge valve 27, and the scroll compressor 1 is Noise can be reduced.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG.
This embodiment differs from the first embodiment described above in the configuration of the second discharge port 26C in the two paths of discharge ports. Since other points are the same as those in the first embodiment, description thereof will be omitted.
In the present embodiment, the first discharge port 26A among the discharge ports of at least two paths is provided in the vertical direction with respect to the end plate of the fixed scroll 21 as described above, and the path length is L1. On the other hand, the second discharge port 26C is configured to be bent substantially parallel to the first discharge port 26A.

  As described above, the first discharge port 26A of the two discharge ports is provided perpendicular to the end plate of the fixed scroll 21, and the second discharge port 26C is bent substantially parallel to the first discharge port 26A. By providing, the path length L2 of the second discharge port 26C is made longer than the path length L1 of the first discharge port 26A provided vertically, and it is ensured between the first and second discharge ports 26A and 26C of the two paths. It is possible to secure a path length difference. For this reason, the pressure wave propagated in the central compression chamber 23A by the high-pressure gas flowing backward from the discharge chamber 25 side into the central compression chamber 23A is reduced to about ½, and the scroll compressor 1 is reduced in noise. Can do.

[Third Embodiment]
Next, a third embodiment of the present invention will be described with reference to FIG.
The present embodiment is different from the first embodiment in the configuration of the second discharge port 26D in the two paths of discharge ports. Since other points are the same as those in the first embodiment, description thereof will be omitted.
In the present embodiment, the first discharge port 26A among the discharge ports of at least two paths is provided in the vertical direction with respect to the end plate of the fixed scroll 21 as described above, and the path length is L1. The opening end on the central compression chamber 23A side of the second discharge port 26D provided obliquely with respect to the first discharge port 26A is joined with the first discharge port 26A, and the second discharge port 26D From there, it is provided obliquely toward the discharge chamber 25 side, and the path length L2 is configured to be longer than the path length L1 of the first discharge port 26A.

  In this way, the opening end of the second discharge port 26D on the discharge chamber 25 side is joined with the first discharge port 26A, and the second discharge port 26D is provided obliquely from there toward the central compression chamber 23A side. As a result, the first and second discharges in the two paths into the central compression chamber 23 while reducing the distance between the open ends of the first and second discharge ports 26A and 26D in the two paths opened to the central compression chamber 23A side. By opening the ports 26A and 26D, a required path length difference can be secured between the first and second discharge ports 26A and 26D of the two paths. Accordingly, the simple improvement by simply adding the second discharge port 26D reduces the pressure wave propagated in the central compression chamber 23A by the high-pressure gas flowing back into the central compression chamber 23A from the discharge chamber 25 side, and scroll compression The machine 1 can be reduced in noise.

  In addition, this invention is not limited to the invention concerning the said embodiment, In the range which does not deviate from the summary, it can change suitably. For example, in the above-described embodiment, an example in which at least two discharge ports, that is, the first discharge port 26A and the second discharge port 26B, 26C, or 26D are provided has been described. Of course.

  In the above-described embodiment, the electric scroll compressor 1 driven by the electric motor 10 has been described. However, the drive source is not built in, and is driven via a clutch by a drive source such as an external engine. Needless to say, the present invention can be applied to the open type scroll compressor.

DESCRIPTION OF SYMBOLS 1 Scroll compressor 20 Scroll compression mechanism 21 Fixed scroll 22 Orbiting scroll 23 A pair of compression chamber 23A Central compression chamber 25 Discharge chamber 26A 1st discharge port (discharge port of 1st path | route)
26B, 26C, 26D Second discharge port (discharge port of the second path)
27 Discharge valve L1 First discharge port path length L2 Second discharge port path length

Claims (6)

A fixed scroll and an orbiting scroll are provided, and a gas compressed by a pair of compression chambers formed between the scrolls is discharged from a central compression chamber formed by joining the compression chambers through a discharge port and a discharge valve. In the scroll compressor that discharges to the discharge chamber,
A scroll compressor characterized in that at least two discharge ports having different path lengths opened and closed by the discharge valve are provided between the central compression chamber and the discharge chamber.   The discharge port of the first path among the discharge ports of the at least two paths is provided perpendicular to the end plate of the fixed scroll, and the discharge port of the second path is relative to the discharge port of the first path. The scroll compressor according to claim 1, wherein the scroll compressor is provided obliquely.   The discharge port of the second path has an opening end on the central compression chamber side joined with the discharge port of the first path, and is provided obliquely from there to the discharge chamber side. The scroll compressor according to claim 2.   The discharge port of the second path has an opening end on the discharge chamber side joined with the discharge port of the first path, and is provided obliquely toward the central compression chamber side therefrom. The scroll compressor according to claim 2.   The discharge port of the first path among the discharge ports of the at least two paths is provided perpendicular to the end plate of the fixed scroll, and the discharge port of the second path is parallel to the discharge port of the first path. The scroll compressor according to claim 1, wherein the scroll compressor is bent. The at least two paths of the discharge ports are configured so that the pressure wave propagated in the central compression chamber by the pulsation of the high pressure gas flowing backward from the discharge chamber side into the central compression chamber is propagated at least twice. 6. The scroll compressor according to claim 1, wherein the scroll compressor is provided with a path length difference.

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