JP4918338B2 - Compressor and air conditioner - Google Patents

Description

  The present invention relates to a compressor and an air conditioner, and more particularly to a compressor and an air conditioner suitable for use in an in-vehicle air conditioner.

  Conventionally, in an air conditioner, a refrigeration apparatus, etc., a refrigeration cycle is configured by using a compressor that discharges fluid compressed in a compression chamber from a discharge port to the outside of the housing through a discharge chamber inside the housing. It has been broken. Such a compressor, for example, a scroll type compressor, is substantially the same as a fixed scroll in which a spiral wall body is erected on one side surface of an end plate in a housing, and a fixed scroll wall body on one side surface of the end plate. A fixed scroll having a compression mechanism combined with a orbiting scroll having a spiral wall body having the same shape and a driving means connected to the orbiting scroll via a drive shaft and causing the orbiting scroll to revolve orbitally. On the other hand, the revolving orbiting of the orbiting scroll gradually reduces the volume of the compression chamber formed between the walls, and compresses the fluid in the compression chamber.

  In such a compressor, in order to reduce the pulsation of the fluid generated by the compression mechanism, a discharge chamber as a volume part is formed in the upper part of the housing and the back surface of the end plate of the fixed scroll, and the compression mechanism compresses the discharge chamber. The discharged fluid is first discharged into the discharge chamber, and after reducing pulsation in the discharge chamber, the fluid is discharged out of the housing through the discharge port.

  By the way, the discharge chamber as described above has a limit in the function of attenuating the pulsation of the discharge gas from the structure in which the space in the housing is used as it is. For this reason, the pulsation of the fluid to be discharged cannot be sufficiently attenuated in the discharge chamber, and the pulsation wave may be propagated to the upper apparatus of the compressor, for example, the condenser of the air conditioner, through the pipe. Further, the pulsating wave propagates to the capacitor, so that the capacitor is vibrated. As a result, there is a possibility that a problem such as damage to the capacitor due to vibration may occur.

  Therefore, as a technique related to the reduction of such pressure pulsation, for example, in the compressor described in Patent Document 1, a muffler space as a volume part separate from a discharge chamber in which fluid is directly discharged from a compression mechanism. By providing, the pulsation of the fluid is reduced.

Japanese Patent No. 36977782

  However, in the muffler structure of the compressor described in Patent Document 1, since the muffler space is provided separately from the discharge chamber, the apparatus becomes large and the structure becomes complicated. As a result, the cost also increases.

  Accordingly, an object of the present invention is to provide a compressor and an air conditioner that can sufficiently attenuate a pressure pulsation of a fluid and prevent damage to a host device with a simple structure.

In order to achieve the above object, a compressor according to the first aspect of the present invention includes a housing, a discharge port that is provided in the housing and discharges the fluid compressed in the compression chamber, and communicates with the discharge port to expand the fluid. A discharge chamber, a throttle portion communicating with the discharge chamber to restrict the flow area of the fluid, and a pipe-shaped fluid having a predetermined length communicating with the discharge port for discharging the fluid out of the housing and the throttle portion A passage , an end plate on which a spiral wall body is erected, a fixed scroll fixed inside the housing, and an end plate on which a spiral wall body is erected, A revolving scroll supported in the housing so as to be able to revolve while preventing rotation in a state where the wall body is engaged with the wall body of the fixed scroll, and a drive shaft for transmitting a rotational force to the revolving scroll, The compression chamber has the fixed scroll. Between the end plate and the end plate of the orbiting scroll, the orbiting scroll can revolve with respect to the fixed scroll to compress the fluid, and the discharge port is an end of the fixed scroll. The discharge chamber is formed by an end plate of the fixed scroll and the housing, a plurality of the fluid passages are provided, the drive shaft is provided along a horizontal direction, and the plurality of the fluid passages are provided. Of the fluid passages, the fluid passage below the vertical direction has a lubricating oil reservoir that can suppress passage of the fluid by storing lubricating oil contained in the fluid .

In the compressor according to the second aspect of the present invention, the discharge chamber is defined inside the rib and the fluid passage is formed outside the rib by erecting the end plate of the fixed scroll or the housing. It is characterized by being defined.

In the compressor according to the invention of claim 3, the housing has a cylindrical shape, and the curved fluid passage is provided around the discharge chamber by forming the curved rib on the inside. And

In a compressor according to a fourth aspect of the present invention, a plurality of the fluid passages are provided, and the plurality of fluid passages are set to have the same length.

In the compressor according to a fifth aspect of the present invention, a plurality of the fluid passages are provided, and the plurality of fluid passages are set to have unequal lengths.

In order to achieve the above object, an air conditioner according to claim 6 of the present invention includes a housing, a discharge port that is provided in the housing and discharges the refrigerant compressed in the compression chamber, and communicates with the discharge port. A discharge chamber that expands the flow path, a throttle that communicates with the discharge chamber and restricts the flow area of the refrigerant, a discharge port that discharges the refrigerant out of the housing, and a pipe having a predetermined length that communicates with the throttle A fluid passage , an end plate on which a spiral wall body is erected, a fixed scroll that is fixedly installed inside the housing, and an end plate on which the spiral wall body is erected An orbiting scroll supported in the housing so as to be able to revolve while preventing rotation in a state where the wall body is engaged with the wall body of the fixed scroll, and a drive shaft that transmits rotational force to the orbiting scroll. A compressor having the compressor A condenser that condenses and liquefies the discharged refrigerant, an expansion valve that decompresses and expands the refrigerant liquefied by the condenser to form a low-temperature and low-pressure liquid refrigerant, and a low-temperature and low-pressure liquid refrigerant that passes through the expansion valve and air. An evaporator for exchanging heat , and the compression chamber is provided between an end plate of the fixed scroll and an end plate of the orbiting scroll, and the orbiting scroll revolves around the fixed scroll so that the refrigerant The discharge port is formed on an end plate of the fixed scroll, the discharge chamber is formed by the end plate of the fixed scroll and the housing, and a plurality of fluid passages are provided. The drive shaft is provided along a horizontal direction, and a fluid passage below the vertical direction among the plurality of fluid passages stores lubricating oil contained in the refrigerant. In it characterized by having a lubricant reservoir capable of suppressing the passage of the refrigerant.

  According to the compressor of the first aspect of the present invention, the fluid compressed in the compression chamber and discharged to the discharge chamber through the discharge port is once expanded in the discharge chamber and attenuated by reflection and interference of the pressure pulsation component. Is done. Then, by providing a throttle portion that communicates with the discharge chamber and narrows the flow path area, pressure pulsation is reduced in the throttle portion. Further, by providing a fluid passage that connects the throttle portion and the discharge port and setting the length to a predetermined length, the pressure pulsation is further reduced when the fluid passes through the fluid passage. As a result, the pressure pulsation of the fluid can be sufficiently attenuated with a simple structure, and damage to the host device can be prevented. Moreover, various pulsation frequency characteristics can be easily handled by appropriately changing the length of the fluid passage.

According to the compressor of the first aspect of the present invention, by providing the compression chamber in which the orbiting scroll revolves with respect to the fixed scroll so that the fluid can be compressed, the revolving orbiting motion of the orbiting scroll is compressed and discharged. The fluid discharged into the discharge chamber through the port pulsates in the discharge chamber in accordance with the revolving orbiting motion of the orbiting scroll, but at this time, since the throttle portion and the fluid passage are provided in communication with the discharge chamber, The pressure pulsation at a specific frequency can be reduced.

According to the compressor of the second aspect of the present invention, since the fluid passage is formed outside the ribs standing on the end plate or the housing of the fixed scroll and defining the discharge chamber, the end plate or the housing of the fixed scroll is provided. With a simple configuration of providing ribs, it is possible to form a discharge chamber and to form a throttle portion and a fluid passage outside the discharge chamber. As a result, the manufacturing cost can be suppressed.

According to the compressor of the invention of claim 3 , since the fluid passage is provided in a curved shape around the discharge chamber, the length of the fluid passage can be set to an appropriate length while having a more compact configuration. .

According to the compressor of the fourth aspect of the present invention, by providing a plurality of fluid passages and setting the lengths of the plurality of fluid passages equal, pressure pulsation can be reduced in a plurality of flow paths. Therefore, the pressure pulsation of the fluid can be sufficiently reduced without reducing the flow path area at the throttle part, and the compression efficiency is reduced and the pressure loss is reduced because the flow path area is not reduced too much. The increase can be suppressed.

According to the compressor of the fifth aspect of the present invention, a plurality of fluid passages are provided, and the lengths of the plurality of fluid passages are set to be unequal lengths, so that the fluid flowing through each passage is upstream of the discharge port. The pressure pulsations of the fluid led out to the outside from the discharge port can be effectively attenuated because they interfere with each other and cancel each other's pulsations. In addition, this makes it possible to reduce pressure pulsations in a wide frequency band.

According to the compressor of the first aspect of the present invention, the lubricating oil reservoir is provided in the vertically downward fluid passage so that the lubricating oil is stored in the lubricating oil reservoir according to the operating state. Since the fluid passage is closed and the fluid passage can be changed, an appropriate pressure pulsation reduction characteristic can be obtained according to the operating state of the compressor.

According to the air conditioner of the invention of claim 6 , the refrigerant discharged from the compressor is condensed and liquefied by the condenser, and the liquefied refrigerant is decompressed and expanded by the expansion valve to obtain a low-temperature and low-pressure liquid refrigerant. Heat can be exchanged between the low-temperature and low-pressure liquid refrigerant and the air. During this time, the refrigerant compressed in the compression chamber and discharged to the discharge chamber via the discharge port is once expanded in the discharge chamber and attenuated by reflection and interference of the pressure pulsation component. Then, by providing a throttle portion that communicates with the discharge chamber and narrows the flow path area, pressure pulsation is reduced in the throttle portion. Furthermore, by providing a fluid passage that connects the throttle portion and the discharge port and setting the length to a predetermined length, the pressure pulsation is further reduced when the refrigerant passes through the fluid passage. As a result, the pressure pulsation of the refrigerant can be sufficiently attenuated with a simple structure, and damage to the host device can be prevented. Moreover, various pulsation frequency characteristics can be easily handled by appropriately changing the length of the fluid passage.

Below, the reference example and Example of the scroll compressor and air conditioning apparatus which concern on this invention are demonstrated in detail based on drawing. In addition, this invention is not limited by this reference example and Example. In addition, constituent elements in the following reference examples and examples include those that can be easily replaced by those skilled in the art or those that are substantially the same.

[Reference Example 1]
FIG. 1 is a cross-sectional view of a discharge chamber of a scroll compressor according to Reference Example 1 of the present invention (cross section AA in FIG. 2), and FIG. 2 is a cross-sectional view of the scroll compressor according to Reference Example 1 of the present invention. FIG. 3 is a refrigerant circuit diagram of an air conditioner to which the scroll compressor according to Reference Example 1 of the present invention is applied. FIG. 1 is a partial cross-sectional view taken along the line AA shown in FIG. 2, and the illustration of the discharge valve 47 is omitted here.

In this reference example , as shown in FIG. 2 or FIG. 3, the scroll compressor 1 as a compressor is a scroll compressor suitable for use in an in-vehicle air conditioner or the like. Here, the scroll compressor 1 is applied to the air conditioner 2. The refrigerant gas is used as the fluid. The air conditioner 2 includes a scroll compressor 1, a condenser 100, an expansion valve 200, and an evaporator 300. The scroll compressor 1 compresses the refrigerant gas and sends it to the capacitor 100 as a high-temperature and high-pressure refrigerant gas. The condenser 100 cools and cools the high-temperature and high-pressure refrigerant gas supplied from the scroll compressor 1 by releasing heat to the outside air. The refrigerant liquefied by the condenser 100 is sent to the expansion valve 200, and is decompressed and expanded by the expansion valve 200 to be converted into a low-temperature and low-pressure liquid refrigerant and supplied to the evaporator 300. The evaporator 300 heat-exchanges this low-temperature and low-pressure liquid refrigerant and air to cool the air.

  Specifically, the scroll compressor 1 is supported in the housing 11 so as to be capable of revolving while preventing rotation and a housing 11 having a hollow inside, a fixed scroll 14 fixedly provided inside the housing 11 and being internally provided. A turning scroll 15. Furthermore, the scroll compressor 1 includes a drive shaft 16 having an eccentric portion 60 with which the orbiting scroll 15 engages at one end and a drive device 13 provided at the other end.

  The housing 11 is disposed horizontally and is configured as a sealed container having a substantially cylindrical shape surrounding each part of the scroll compressor. The housing 11 includes a front case 21 and a rear case 22 disposed adjacent to the front case 21. The front case 21 is formed in a substantially cylindrical shape, and the rear case 22 is formed in a substantially cylindrical shape with one end closed. The rear case 22 is fixed to the front case 21 with a plurality of fastening bolts 23 in a state where the open end is fitted to the front case 21. In the housing 11, a suction port 26 is formed in the front case 21, and a discharge port 27 is formed in the rear case 22. The suction port 26 and the discharge port 27 are connected to a refrigerant gas path outside the scroll compressor 1, and the discharge port 27 is connected to the capacitor 100 described above.

  The fixed scroll 14 has an end plate 44 on which a spiral wrap 45 as a spiral wall body is erected. The orbiting scroll 15 has an end plate 50 on which a spiral wrap 51 as a spiral wall body is erected, and the spiral wrap 51 is engaged with the spiral wrap 45 of the fixed scroll 14 as will be described later. It is supported so that it can revolve. The fixed scroll 14 and the orbiting scroll 15 constitute a compression mechanism 12. The fixed scroll 14 is provided by being fitted to the inner peripheral surface of the rear case 22 in a state where the spiral wrap 45 is engaged with the spiral wrap 51 of the orbiting scroll 15. In the fixed scroll 14, the end plate 44 is fixed to the rear case 22 by the fastening bolt 23 described above.

  The orbiting scroll 15 is disposed such that an end plate 50 formed in a substantially disk shape faces the eccentric portion 60 of the drive shaft 16. The spiral wrap 51 is erected on the surface of the end plate 50 on the fixed scroll 14 side. The orbiting scroll 15 is thrust supported by a thrust bearing 61 formed integrally with the front case 21 so that the end plate 50 can rotate. Further, the orbiting scroll 15 is formed with a boss portion 53 for the eccentric portion 60 to engage with the back surface of the end plate 50 (the surface opposite to the surface on which the spiral wrap 51 is erected). The boss portion 53 is formed so as to protrude from the back surface of the end plate 50 toward the eccentric portion 60. The boss portion 53 is formed in a substantially cylindrical shape having a hollow inside. A rolling bearing 56 is provided inside the boss portion 53.

  The drive shaft 16 is formed with an eccentric part 60 at one end and a drive device 13 at the other end. The eccentric part 60 is configured by an eccentric drive pin 54 and a drive bush 55. The eccentric drive pin 54 is formed in a substantially cylindrical shape. Further, the eccentric drive pin 54 is positioned so that the center axis of the eccentric drive pin 54 and the center axis of the drive shaft 16 are parallel, and the center axis of the eccentric drive pin 54 is separated from the center axis of the drive shaft 16 by a predetermined amount. To be provided. Therefore, the eccentric drive pin 54 is eccentric by a predetermined amount with respect to the central axis that is the center of rotation of the drive shaft 16. The drive bush 55 is fitted to the eccentric drive pin 54 so as to cover the outer peripheral side of the eccentric drive pin 54. The drive shaft 16 is connected to a balance weight 58 for canceling the unbalance amount given to the orbiting scroll 15 by the revolving orbiting motion.

  The eccentric part 60 is engaged with the orbiting scroll 15 via the rolling bearing 56 described above. The eccentric drive pin 54 is rotatably supported by the boss portion 53 via a drive bush 55 and a rolling bearing 56. As a result, the orbiting scroll 15 can revolve by the rotation of the drive shaft 16. Further, an anti-rotation mechanism 57 is interposed between the front case 21 and the orbiting scroll 15, and the orbiting scroll 15 is revolved with the center axis of the drive shaft 16 as the revolution axis while being prevented from rotating by these structures. It can be swiveled.

  Here, the front case 21 is formed with a ring-shaped support portion 28 with a reduced diameter at the end opposite to the rear case 22. The drive shaft 16 is provided in the housing 11 in a direction and position where the central axis that is the center of rotation substantially coincides with the central axis of the front case 21. A lip seal 31 that seals the gap between the front case 21 and the drive shaft 16 and suppresses leakage of the refrigerant gas to the outside of the housing 11 is attached to the inner periphery of the front case 21. Further, a rolling bearing 30 and a ball bearing 29 are mounted on the inner peripheral portion of the front case 21. The ball bearing 29 is provided so as to be adjacent to the lip seal 31 and rotatably supports the drive shaft 16 as a rotation shaft at an outer end portion of the lip seal 31. The rolling bearing 30 rotatably supports the large-diameter portion 16a (end portion on the eccentric portion 60 side) of the drive shaft 16 inside the lip seal 31.

  The drive device 13 is provided at the end of the drive shaft 16 opposite to the eccentric portion 60. A rotating plate 32 is fixed to this end portion of the drive shaft 16 by a connecting bolt 33. A ring-shaped support ring 34 is connected to the outer peripheral portion of the rotating plate 32 by a plurality of connecting pins 35. And the end surface of the driven pulley 36 is fixed to this support ring 34, and it is rotatably supported by the support part 28 of the front case 21 via a bearing. A magnet clutch is configured by mounting an electromagnet 38 in the driven pulley 36. The driven pulley 36 is connected to a drive source (for example, an engine) via a drive belt (not shown).

  The fixed scroll 14 and the orbiting scroll 15 are combined so that the spiral wrap 45 of the fixed scroll 14 and the spiral wrap 51 of the orbiting scroll 15 are engaged with each other between the end plate 44 and the end plate 50. A compression chamber 40 is formed between the wraps 45 and 51. The fixed scroll 14, the orbiting scroll 15, and the compression chamber 40 constitute the compression mechanism 12. A suction chamber 39 is formed between the compression mechanism 12 and the front case 21. Further, on the opposite side of the fixed scroll 14 from the spiral wrap 45, a discharge chamber 41 is defined by the end plate 44 and the inner peripheral surface of the rear case 22. The discharge chamber 41 is defined by a recess formed on the end plate 44 of the fixed scroll 14 and a recess formed on the inner peripheral surface of the rear case 22 facing each other.

  A suction chamber 39 as a low-pressure chamber, a compression chamber 40, and a discharge chamber 41 as a high-pressure chamber communicate with each other. Specifically, the above-described suction port 26 opens into the suction chamber 39, and the suction chamber 39 introduces a refrigerant gas containing lubricating oil into the compression chamber 40. The compression chamber 40 compresses the refrigerant gas introduced into the suction chamber 39 when the orbiting scroll 15 revolves around the fixed scroll 14. The compression chamber 40 communicates with the discharge chamber 41 through a discharge port 46 provided in the center of the end plate 44 of the fixed scroll 14. The discharge port 46 discharges the refrigerant gas compressed in the compression chamber 40 to the discharge chamber 41, and a discharge valve 47 is provided at the end of the discharge chamber 41. The discharge valve 47 is an opening / closing means that opens when the inside of the compression chamber 40 reaches a predetermined pressure, and prevents backflow of refrigerant gas from the discharge chamber 41 side to the compression chamber 40 side. The discharge chamber 41 functions as a volume portion that temporarily expands the refrigerant gas discharged from the discharge port 46.

  The reason why the suction port 26 is opened so as to substantially face the compression mechanism 12 is that the refrigerant gas taken into the housing 11 from the suction port 26 is directly introduced into the compression chamber 40, thereby reducing the compression efficiency and pressure. This is to suppress an increase in loss. The refrigerant gas compressed in the compression chamber 40 contains a lubricating oil that lubricates each part in the housing 11 of the scroll compressor 1 in a mist state. Each sliding part is lubricated.

  In the scroll compressor 1 configured as described above, when the drive source is driven, the drive force is transmitted to the driven pulley 36 of the drive device 13, the drive shaft 16 rotates, and this rotational force is transmitted via the eccentric portion 60 and the like. Is transmitted to the orbiting scroll 15, and the orbiting scroll 15 revolves on the revolution track while being prevented from rotating by the rotation preventing mechanism 57. Then, refrigerant gas containing mist of lubricating oil is sucked into the suction chamber 39 in the housing 11 from the suction port 26 and introduced into the compression chamber 40.

  As the orbiting scroll 15 continues to rotate, the compression chamber 40 is gradually narrowed accordingly, and the refrigerant gas inside reaches the center while being compressed, and is discharged to the discharge chamber 41 through the discharge port 46. The discharge valve 47 opens and closes due to the differential pressure between the compression chamber 40 and the discharge chamber 41. That is, when the pressure of the refrigerant gas in the compression chamber 40 becomes higher than the pressure in the discharge chamber 41, the discharge valve 47 is pushed open and the high-pressure refrigerant gas flows out into the discharge chamber 41.

  At this time, the refrigerant gas which is compressed in accordance with the revolution turning motion of the orbiting scroll 15 and is discharged into the discharge chamber 41 by opening the discharge valve 47 is discharged according to the revolution turning of the orbiting scroll 15 and the opening and closing of the discharge valve 47. Pulsates in chamber 41. However, the discharge chamber 41 functions as a volume portion that temporarily expands the refrigerant gas discharged from the discharge port 46. That is, the pressure pulsation component of the refrigerant gas is attenuated by reflection and interference of the pressure pulsation component of the refrigerant gas in the discharge chamber 41 as the volume portion.

  By the way, since such a discharge chamber 41 is provided in the space in the rear case 22 of the housing 11, there is an upper limit in the space that can be secured as a volume portion, and thus a function of attenuating the pressure pulsation of the refrigerant gas. There are also limitations.

Therefore, in this reference example , as shown in FIG. 1 or FIG. 2, a throttle portion 70 that communicates with the discharge chamber 41 and narrows the flow area of the refrigerant gas, and a discharge port 27 that discharges the refrigerant gas to the outside of the housing 11. By providing a tubular gas passage 71 as a fluid passage communicating with the throttle portion 70, the pressure pulsation of the refrigerant gas is more effectively reduced. That is, the discharge port 27 communicates with the discharge chamber 41 as a high-pressure part via the pipe-like gas passage 71 and the throttle part 70.

  The throttle portion 70 and the pipe-like gas passage 71 are formed by a rear case side rib 72 standing on the rear case 22 of the housing 11 and a fixed scroll side rib 73 standing on the end plate 44 of the fixed scroll 14. The The rear case side rib 72 has a proximal end fixed to the inner surface of the rear case 22 and a distal end protruding toward the end plate 44, and the fixed scroll side rib 73 has a proximal end fixed to the back surface of the end plate 44 and a distal end. Protrudes toward the rear case 22. Then, the front end of the rear case side rib 72 and the front end of the fixed scroll side rib 73 are in contact with each other, so that the discharge chamber 41 is located inside the rear case side rib 72 and the fixed scroll side rib 73 (on the discharge port 46 side). While the throttle part 70 and the pipe-like gas passage 71 are defined outward.

  That is, the rear case side rib 72 is provided at a distance from the rear case 22 along the inner surface of the rear case 22, and a portion between the rear case 22 and the rear case side rib 72 is a pipe-like gas passage. 71 is defined. The fixed scroll side rib 73 is formed at a position corresponding to the rear case side rib 72. Accordingly, the discharge chamber 41 is formed with a simple configuration in which the rear case side rib 72 and the fixed scroll side rib 73 are provided, and the throttle portion 70 and the pipe-like gas passage 71 are formed outside the discharge chamber 41. . Further, since the rear case side rib 72 and the fixed scroll side rib 73 are formed in a curved shape, the pipe-like gas passage 71 is also provided in a curved shape around the discharge chamber 41, so that the configuration is more compact. Yes.

  Further, the rear case side rib 72 and the fixed scroll side rib 73 are extended from the discharge port 27 to a position substantially opposed to the discharge port 27 with the discharge port 46 interposed therebetween. A throttle portion 70 is provided at a position substantially opposite to the discharge port 27 across the discharge port 46, and the tubular gas passage 71 extends to the discharge port 27 continuously with the throttle portion 70. That is, the length L 1 of the tubular gas passage 71 is set by the position of the throttle portion 70 with respect to the discharge port 27.

  Here, the length L1 of the tubular gas passage 71 is set according to the frequency characteristics of the pressure pulsation in the discharge chamber 41. The pressure pulsation in the discharge chamber 41 changes according to the speed of the revolving orbiting motion of the orbiting scroll 15, that is, the number of rotations. However, since the frequency range in which the pressure pulsation is desired to be reduced is specified according to the specifications of the host device, here, the air conditioner 2, it is only necessary that the pressure pulsation can be reduced at this specific frequency. That is, the length L1 of the tubular gas passage 71 is set according to the frequency at which the pressure pulsation is to be suppressed, and at the frequency at which this pressure pulsation is to be reduced, the length L1 of the air column natural frequency in the tubular gas passage 71 By setting the length so as not to coincide with the pressure pulsation frequency, the resonance phenomenon is prevented from occurring and the attenuation rate is set to a peak length.

  Therefore, the refrigerant gas discharged into the discharge chamber 41 via the discharge port 46 is reflected and interfered with the pressure pulsation component of the refrigerant gas in the discharge chamber 41 serving as a volume portion, whereby the pressure pulsation of the refrigerant gas is attenuated. The When the refrigerant gas reaches the throttle part 70, the flow path area is reduced, so that resistance occurs when passing through the throttle part 70, thereby reducing pressure pulsation. Further, the refrigerant gas that has passed through the throttle portion 70 passes through the tubular gas passage 71 having a predetermined length L1 corresponding to the frequency of the pressure pulsation, and the pressure waves that are intermittently generated at this time cancel each other out. After the pulsation is further reduced, it is led out through the discharge port 27 and introduced into the capacitor 100 (see FIG. 3). That is, the pressure pulsation of the refrigerant gas discharged from the scroll compressor 1 is sufficiently attenuated in the throttle unit 70 and the pipe-like gas passage 71, and as a result, the pulsation wave is passed through the pipe and the condenser 100 of the air conditioner 2 is connected. And the pulsating wave propagates to the capacitor 100 to prevent the capacitor 100 from being vibrated and to prevent the capacitor 100 from being damaged by vibration.

According to the scroll compressor 1 and the air conditioner 2 according to the first embodiment of the present invention described above, the housing 11 and the discharge port 46 that discharges the refrigerant gas provided in the housing 11 and compressed in the compression chamber 40. A discharge chamber 41 that communicates with the discharge port 46 and expands the refrigerant gas; a throttle portion 70 that communicates with the discharge chamber 41 and restricts the flow area of the refrigerant gas; and a discharge port 27 that discharges the refrigerant gas outside the housing 11. A pipe-shaped gas passage 71 having a predetermined length communicating with the throttle unit 70 is provided.

  Therefore, the refrigerant gas compressed in the compression chamber 40 and discharged to the discharge chamber 41 via the discharge port 46 is once expanded in the discharge chamber 41 and attenuated by reflection and interference of the pressure pulsation component. Further, by providing the throttle portion 70 that communicates with the discharge chamber 41 and narrows the flow path area, pressure pulsation is reduced in the throttle portion 70. Furthermore, a pipe-like gas passage 71 that communicates between the throttle portion 70 and the discharge port 27 is provided, and the length L1 is set according to the frequency at which pressure pulsation is desired to be suppressed. When passing through the passage 71, the pressure pulsation is further reduced. As a result, the pressure pulsation of the refrigerant gas can be sufficiently attenuated with a simple structure, and damage to the air conditioner 2 as the host device can be prevented. Further, by appropriately changing the length L1 of the tubular gas passage 71, it is possible to easily cope with various frequency characteristics. In addition, since it is not necessary to provide a muffler space, for example, separately from the discharge chamber 41, it is possible to prevent the apparatus from becoming large and the structure from becoming complicated.

Furthermore, according to the scroll compressor 1 according to Reference Example 1 of the present invention described above, the scroll compressor 1 has the end plate 44 on which the spiral spiral wrap 45 is erected, and is fixedly installed inside the housing 11. The fixed scroll 14 and the end plate 50 on which the spiral spiral wrap 51 is erected, and rotation is prevented while the spiral wrap 51 is engaged with the spiral wrap 45 of the fixed scroll 14. The orbiting scroll 15 is supported in the housing 11 so as to be capable of revolving. The compression chamber 40 is provided between the end plate 44 of the fixed scroll 14 and the end plate 50 of the orbiting scroll 15, and the orbiting scroll 15 is fixed. The refrigerant gas can be compressed by revolving around the scroll 14, the discharge port 46 is formed in the end plate 44 of the fixed scroll 14, and the discharge chamber 41 is connected to the fixed scroll 1. It is formed by the end plate 44 and the housing 11 of the. Therefore, the refrigerant gas that is compressed in accordance with the revolution turning motion of the orbiting scroll 15 and discharged into the discharge chamber 41 through the discharge port 46 pulsates in the discharge chamber 41 in accordance with the revolution turning motion of the orbiting scroll 15. However, at this time, the pressure pulsation of a specific frequency can be reduced by the throttle portion 70 and the tubular gas passage 71.

Further, according to the scroll compressor 1 according to the reference example 1 of the present invention described above, the rear case side rib 72 and the fixed scroll side rib 73 stand on the end plate 44 of the fixed scroll 14 and the rear case 22 of the housing 11. By being provided, the discharge chamber 41 is defined inside the rear case side rib 72 and the fixed scroll side rib 73, and the tubular gas passage 71 is defined outside. Therefore, the discharge chamber 41 is formed with the simple configuration of providing the rear case side rib 72 and the fixed scroll side rib 73, and the throttle portion 70 and the pipe-like gas passage 71 are formed outside the discharge chamber 41. Can do. As a result, the manufacturing cost can be suppressed.

Furthermore, according to the scroll compressor 1 according to Reference Example 1 of the present invention described above, the housing 11 has a cylindrical shape, and the curved rear case side rib 72 and the fixed scroll side rib 73 are formed inside. Thus, a curved tubular gas passage 71 is provided around the discharge chamber 41. Therefore, the length L1 of the pipe-like gas passage 71 can be set to an appropriate length with a more compact configuration.

[Reference Example 2]
FIG. 4 is a cross-sectional view of the discharge chamber of the scroll compressor according to Reference Example 2 of the present invention. The scroll compressor according to the reference example 2 has substantially the same configuration as the scroll compressor according to the reference example 1 , but the reference example is provided with a plurality of pipe-like gas passages as fluid passages, two here. 1 is different from the scroll compressor according to 1 . In addition, about the structure, an effect | action, and effect which are common in the reference example 1 , while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected.

As shown in FIG. 4, the scroll compressor 201 according to the reference example 2 includes the throttle portion 274 and the fluid passage in addition to the throttle portion 70 and the tubular gas passage 71 as the fluid passage described above in the reference example 1 . A tubular gas passage 275 is provided.

  The throttle portion 274 and the pipe-like gas passage 275 are provided so as to face the throttle portion 70 and the pipe-like gas passage 71 with the discharge port 46 interposed therebetween. Here, the throttle portion 274 and the pipe-shaped gas passage 275 are formed by extending a rear case side rib 72 and a fixed scroll side rib 73 (see also FIG. 2). That is, the refrigerant gas discharged into the discharge chamber 41 through the discharge port 46 is a flow path that reaches the discharge port 27 through the throttle portion 70 and the pipe-like gas passage 71, and the throttle portion 274 and the pipe-like gas passage. The flow is divided into two channels, that is, the flow channel that reaches the discharge port 27 via the H.275, merges again upstream of the discharge port 27, and is led to the outside. The length L2 of the tubular gas passage 275 is set according to the position of the throttle 274 with respect to the discharge port 27, and is set equal to the length L1 of the tubular gas passage 71 here. In this way, by providing the two refrigerant gas flow paths, the pressure pulsation of the refrigerant gas is reduced without reducing the flow path area in the throttle part 274 with the throttle part 70 and the throttle part 274.

According to the scroll compressor 201 according to the reference example 2 of the present invention described above, the fluid passage is provided with two pipe gas passages 71 and 275, and the pipe gas passage 71 is provided. And the length of the tubular gas passage 275 is set equal. Therefore, there are provided two systems of flow paths, that is, a flow path that reaches the discharge port 27 via the tubular gas passage 71 and a flow path that reaches the discharge port 27 via the throttle portion 274 and the tubular gas passage 275. Thus, since the pressure pulsation can be reduced by the two systems of the flow paths, the pressure pulsation of the refrigerant gas can be reduced without excessively reducing the flow area in the throttle part 274 with the throttle part 70 and Further, since the flow channel area is not excessively reduced, it is possible to suppress a decrease in compression efficiency and an increase in pressure loss.

[Reference Example 3]
FIG. 5 is a cross-sectional view of the discharge chamber of the scroll compressor according to Reference Example 3 of the present invention. Scroll compressor according to Reference Example 3 has substantially the same structure as the scroll compressor according to the reference example 2, in Reference Example 2 in terms lengths of the two conduits shaped gas passage is unequal-length This is different from the scroll compressor. In addition, about the structure, an effect | action, and effect which are common in the reference example 2 , while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected.

As shown in FIG. 5, the scroll compressor 301 according to the reference example 3 is similar to the scroll compressor 201 according to the reference example 2 , and the throttle portion 70 and the pipe-like gas passage as the fluid passage described above also in the reference example 1. In addition to 71, a throttle part 376 and a pipe-like gas passage 377 as a fluid passage are provided.

  The throttle portion 376 and the pipe-like gas passage 377 are provided so as to be substantially opposed to the throttle portion 70 and the pipe-like gas passage 71 with the discharge port 46 interposed therebetween. Here, the throttle portion 376 and the pipe-like gas passage 377 are formed by extending the rear case side rib 72 and the fixed scroll side rib 73 (see also FIG. 1). That is, the refrigerant gas discharged into the discharge chamber 41 via the discharge port 46 is a flow path that reaches the discharge port 27 via the throttle portion 70 and the pipe-like gas passage 71, and the throttle portion 376 and the pipe-like gas passage. The flow is divided into two flow paths that reach the discharge port 27 via 377, flows again upstream of the discharge port 27, and is led to the outside.

  Further, the length L3 of the tubular gas passage 377 is set by the position of the throttle portion 376 with respect to the discharge port 27 as described above. However, the length L3 of the tubular gas passage 377 is set shorter than the length L1 of the tubular gas passage 71 here. In this way, the two refrigerant gas flow paths are provided, and the lengths of the two flow paths are made unequal, so that the refrigerant gas reaching the discharge port 27 via the throttle portion 70 and the pipe-like gas passage 71 Since the refrigerant gas reaching the discharge port 27 through the constricted portion 376 and the pipe-like gas passage 377 interferes with each other on the upstream side of the discharge port 27, the mutual pulsations cancel each other. The pressure pulsation of the refrigerant gas led out from the outlet 27 is effectively attenuated.

According to the scroll compressor 301 according to Reference Example 3 of the present invention described above, the fluid passage is provided with two pipe-like gas passages 71 and 377, and the pipe-like gas passage 71 is provided. And the length of the pipe-like gas passage 377 is set to unequal length. Therefore, there are provided two systems of flow paths, that is, a flow path that reaches the discharge port 27 via the tubular gas passage 71 and a flow path that reaches the discharge port 27 via the throttle portion 376 and the tubular gas passage 377. By making the lengths L1 and L3 of the two channels different, the refrigerant gas flowing in each channel interferes with the upstream side of the discharge port 27 and cancels out the pulsation of each other. The pressure pulsation of the refrigerant gas led to the outside can be effectively attenuated. In addition, this makes it possible to reduce pressure pulsations in a wide frequency band.

[Example 1]
FIG. 6 is a cross-sectional view of the discharge chamber of the scroll compressor according to the first embodiment of the present invention. The scroll compressor according to the first embodiment has substantially the same configuration as the scroll compressor according to the reference example 3 ,
It differs from the scroll compressor according to Reference Example 3 in that the fluid passage has a lubricating oil reservoir. In addition, about the structure, effect | action, and effect which are common in the reference example 3 , while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected.

As shown in FIG. 6, the scroll compressor 401 according to the first embodiment has a fluid passage that is positioned below the vertical direction when the entire scroll compressor 401 is installed so that the central axis of the drive shaft 16 is substantially horizontal. Here, a lubricating oil reservoir 478 is provided in the tubular gas passage 71.

  The lubricating oil reservoir 478 is provided at the lowest position in the vertical direction in the tubular gas passage 71 curved downward in the vertical direction. The lubricating oil reservoir 478 is formed so that the thickness t in the vertical direction is thinner than the other part of the tubular gas passage 71.

  Here, as described above, the refrigerant gas compressed in the compression chamber 40 contains lubricating oil that lubricates each part in the housing 11 of the scroll compressor 1 in a mist state. When the refrigerant gas is compressed in the compression chamber 40, it is separated from the refrigerant gas and adheres to the inner surface of the compression chamber 40. The lubricating oil adhering to the inner surface of the compression chamber 40 is scooped up along with the revolving orbiting motion of the orbiting scroll 15, and a part thereof is discharged together with the refrigerant gas into the discharge chamber 41 through the discharge port 46. The lubricating oil discharged to the discharge chamber 41 as the high pressure portion is returned to the suction chamber 39 as the low pressure portion through an oil return passage (not shown).

  When the scroll compressor 401 is operated at high speed, that is, when the speed of the revolving orbiting motion of the orbiting scroll 15 is high, the lubrication is scraped up and discharged into the discharge chamber 41 along with the orbiting orbiting motion of the orbiting scroll 15. The amount of oil refers to the amount of lubricating oil returned to the suction chamber 39 side. As a result, a part of the lubricating oil discharged into the discharge chamber 41 is introduced into the pipe-like gas passage 71 and moved downward in the vertical direction in the pipe-like gas passage 71 due to gravity. The oil is stored in the lubricating oil reservoir 478 located at the lowest vertical end in the passage 71. When the lubricating oil stored in the lubricating oil reservoir 478 reaches a predetermined amount, the pipe-like gas passage 71 is closed, and the derivation of the refrigerant gas through the pipe-like gas passage 71 is suppressed. As a result, the refrigerant gas is led out only by the flow path via the pipe-shaped gas passage 377 in the vertical direction among the two flow paths. Here, by setting the length L3 of the tubular gas passage 377 in accordance with the frequency characteristics of the pressure pulsation during the high speed operation, the pressure pulsation can be appropriately reduced during the high speed operation. At this time, the lubricating oil closing the tubular gas passage 71 becomes a damper and can absorb some pulsating waves. Further, the pulsation wave can be attenuated on the upstream side of the discharge port 27 and the upstream side of the throttle part 70 by the reflected wave from the tubular gas passage 71 serving as a closed end pipe.

  On the other hand, when the scroll compressor 401 is operated at low speed, that is, when the speed of the revolving orbiting motion of the orbiting scroll 15 is low, the amount of lubricating oil returned to the suction chamber 39 is lubricated to be discharged into the discharge chamber 41. Turn around the amount of oil. Thereby, the lubricating oil stored in the lubricating oil storage part 478 gradually decreases, and the closed state of the pipe-like gas passage 71 is eliminated. As a result, the refrigerant gas is led out by two systems of the flow path reaching the discharge port 27 via the pipe-shaped gas passage 71 and the flow path reaching the discharge port 27 via the throttle portion 376 and the pipe-shaped gas path 377. Done. As a result, the refrigerant gas that has flowed through the respective channels interferes with the upstream side of the discharge port 27 to cancel each other's pulsations, so that the pressure pulsations of the refrigerant gas led out from the discharge ports 27 are effectively attenuated. can do.

According to the scroll compressor 401 according to the first embodiment of the present invention described above, the drive shaft 16 that transmits the rotational force to the orbiting scroll 15 is provided, and the drive shaft 16 is provided along the horizontal direction, and the pipeline Of the gas channel 71 and the gas channel 377 in the vertical direction is a lubricating oil reservoir that can suppress the passage of the refrigerant gas by storing the lubricant contained in the refrigerant gas. 478. Therefore, by providing the lubricating oil reservoir 478 in the pipe-shaped gas passage 71 below in the vertical direction, the lubricating oil is stored in the lubricating oil reservoir 478 during high speed operation with a large amount of lubricant discharged into the discharge chamber 41. Then, the pipe-shaped gas passage 71 is closed, and the refrigerant gas is led out only by the flow path via the pipe-shaped gas path 377 in the upper vertical direction of the two systems. During low-speed operation with a small amount of lubricating oil discharged into the discharge chamber 41, the closed state of the tubular gas passage 71 in the lubricating oil reservoir 478 is eliminated, and the discharge port 27 is connected to the discharge port 27 via the tubular gas passage 71. Refrigerant gas is led out by two systems: a flow path to the discharge port 27 via a throttle section 376 and a tubular gas passage 377. As a result, the flow path of the refrigerant gas can be changed according to the operating state of the scroll compressor 401, and an appropriate pressure pulsation reduction characteristic can be obtained according to each operating state. Further, by appropriately changing the thickness t of the lubricating oil reservoir 478, it is possible to cope with the frequency at which the road gas passage 71 is desired to be closed.

The compressor and the air conditioner according to the above-described embodiments of the present invention are not limited to the above-described embodiments, and various modifications can be made within the scope described in the claims. In the above description, the case where the compressor of the present invention is applied to an air conditioner has been described. However, the compressor may be applied to a refrigeration apparatus or the like. In the above description, the compression mechanism 12 of the compressor of the reference example has been described as a scroll-type compression mechanism including the fixed scroll 14, the orbiting scroll 15, and the compression chamber 40, but is not limited thereto. For example, a rolling piston type compression mechanism may be used.

  In the above description, the discharge chamber, the throttle portion, and the fluid passage are described as being defined by the tip of the rear case side rib 72 and the tip of the fixed scroll side rib 73 being in contact with each other. For example, when a rib is provided only on the end plate 44, the tip may be in contact with the inner surface of the rear case 22.

  In the above description, the scroll compressors 201, 301, and 401 are described as having two fluid passages, but may be three or more. For example, when three pipes are provided, another fluid passage may be provided inside the pipe-like gas passage 71 along the pipe-like gas passage 71. Further, in the scroll compressor 401, the lubricating oil reservoir 478 stores the lubricating oil by making the vertical thickness t of the pipe-like gas passage 71 thinner than the other portions, so that the pipe-like gas passage 71. However, it is possible to make the lubricating oil easily collect and close by making the pipe-shaped gas passage 71 curved at an acute angle. Further, a throttle portion may be further provided in the middle of the fluid passage, and the passage section of the fluid passage may not be constant. Further, the fluid passage may be provided in a straight line.

  The compressor and the air conditioner according to the present invention have a simple structure to sufficiently attenuate the pressure pulsation of the fluid to prevent the damage of the apparatus, and are applied to various hermetic compressors and air conditioners. Useful.

It is sectional drawing of the discharge chamber of the scroll compressor which concerns on the reference example 1 of this invention. It is sectional drawing of the scroll compressor which concerns on the reference example 1 of this invention. It is a refrigerant circuit figure of the air harmony device to which the scroll compressor concerning reference example 1 of the present invention is applied. It is sectional drawing of the discharge chamber of the scroll compressor which concerns on the reference example 2 of this invention. It is sectional drawing of the discharge chamber of the scroll compressor which concerns on the reference example 3 of this invention. It is sectional drawing of the discharge chamber of the scroll compressor which concerns on Example 1 of this invention.

1, 201, 301, 401 Scroll compressor (compressor)
2 Air conditioner 11 Housing 12 Compression mechanism 13 Drive device 14 Fixed scroll 15 Orbiting scroll 16 Drive shaft 21 Front case (housing)
22 Rear case (housing)
27 Discharge port 40 Compression chamber 41 Discharge chamber 44, 50 End plate 45, 51 Spiral wrap 46 Discharge port 47 Discharge valve 60 Eccentric portion 70, 274, 376 Restriction portion 71, 275, 377 Pipe-shaped gas passage (fluid passage)
72 Rear case side rib (rib)
73 Fixed scroll side rib (rib)
100 Capacitor 200 Expansion valve 300 Evaporator 478 Lubricating oil reservoir

Claims (6)

A housing;
A discharge port provided in the housing for discharging the fluid compressed in the compression chamber;
A discharge chamber communicating with the discharge port and inflating the fluid;
A throttle portion that communicates with the discharge chamber and restricts the flow area of the fluid;
A pipe-shaped fluid passage having a predetermined length communicating the discharge port for discharging the fluid out of the housing and the throttle portion ;
A fixed scroll having an end plate on which a spiral wall body is erected and fixed to the housing;
An orbiting scroll having an end plate on which a spiral wall body is erected, and supported in the housing so as to be able to revolve while preventing rotation while the wall body is engaged with the wall body of the fixed scroll. When,
A drive shaft that transmits rotational force to the orbiting scroll,
The compression chamber is provided between an end plate of the fixed scroll and an end plate of the orbiting scroll, and the orbiting scroll can revolve with respect to the fixed scroll to compress the fluid.
The discharge port is formed on an end plate of the fixed scroll,
The discharge chamber is formed by an end plate of the fixed scroll and the housing,
A plurality of the fluid passages are provided,
The drive shaft is provided along a horizontal direction,
Of the plurality of fluid passages, the fluid passage below the vertical direction has a lubricating oil reservoir that can suppress passage of the fluid by storing lubricating oil contained in the fluid .
Compressor. The discharge chamber is defined on the inside of the rib and the fluid passage is defined on the outside by the rib being erected on the end plate of the fixed scroll or the housing,
The compressor according to claim 1 . The housing has a cylindrical shape, and the curved fluid passage is provided around the discharge chamber by forming the curved rib inside.
The compressor according to claim 2 . A plurality of the fluid passages are provided,
The plurality of fluid passages are set equal in length,
The compressor according to any one of claims 1 to 3 . A plurality of the fluid passages are provided,
The plurality of fluid passages are set to have unequal lengths,
The compressor according to any one of claims 1 to 3 . A housing, a discharge port that discharges the refrigerant compressed in the compression chamber provided in the housing, a discharge chamber that communicates with the discharge port and expands the refrigerant, and communicates with the discharge chamber; A throttle part for reducing the area, a discharge port for discharging the refrigerant out of the housing, a pipe-like fluid passage having a predetermined length communicating with the throttle part, and an end plate on which a spiral wall body is provided. And a fixed scroll installed inside the housing and an end plate on which a spiral wall body is erected, and the wall body rotates with the wall body meshed with the wall body of the fixed scroll. A compressor having a orbiting scroll supported in the housing so as to be able to revolve while being blocked, and a drive shaft that transmits a rotational force to the orbiting scroll ;
A condenser for condensing and liquefying the refrigerant discharged from the compressor;
An expansion valve that decompresses and expands the refrigerant liquefied by the condenser to form a low-temperature and low-pressure liquid refrigerant;
An evaporator that exchanges heat between the low-temperature and low-pressure liquid refrigerant that has passed through the expansion valve and air ;
The compression chamber is provided between an end plate of the fixed scroll and an end plate of the orbiting scroll, and the orbiting scroll can revolve with respect to the fixed scroll to compress the refrigerant.
The discharge port is formed on an end plate of the fixed scroll,
The discharge chamber is formed by an end plate of the fixed scroll and the housing,
A plurality of the fluid passages are provided,
The drive shaft is provided along a horizontal direction,
Of the plurality of fluid passages, a fluid passage below the vertical direction has a lubricating oil reservoir that can suppress passage of the refrigerant by storing lubricating oil contained in the refrigerant .
Air conditioner.

Images