JP2009007938A - Rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent incompressible lubricant oil to remain in a vane back-pressure chamber and its passage when a compressor is started after stopping the compressor. <P>SOLUTION: A lubricant oil-discharge passage 38, equipped with an opening and closing means, to communicate a first gas-supply passage 27 and a second pressure-introduction path 35 is provided within a vane back pressure-supply device 16, thereby the lubricant oil remaining in the vane back-pressure chamber 18 is discharged in a working chamber 8 and also displaced with a coolant gas in the working chamber 8 thus the vane goes out easily due to a centrifugal force and a high pressure gas from the vane back pressure-supply device 16. Consequently, inferior compression can be prevented and vane jumping can be inhibited. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a rotary compressor that sucks and compresses a fluid such as a refrigerant, and more particularly to a rotary compressor used in an air conditioner for automobiles.

  Conventionally, in this type of rotary compressor, high-pressure lubricating oil is supplied to the rear end of the vane by a pressure difference so that the vane always rotates and slides with the rotation of the rotor while the tip is in contact with the inner wall of the cylinder. The vane is pushed out, and fluid such as refrigerant gas is sucked, compressed, and discharged.

  However, the operation state of the compressor for a car air conditioner is various such as a low-speed operation state, a high-speed operation state, a rapid acceleration / deceleration state, and an operation state that is activated after the vehicle is left for a long time.

  Therefore, in order to control the vane back pressure under various operating conditions, the pressure drop in the vane back pressure chamber that occurs immediately after startup is prevented by supplying high-pressure refrigerant gas from the gas supply passage, and in steady operation A vane back pressure applying device is provided to prevent compression failure due to vane chattering phenomenon or popping failure by selectively switching the gas supply passage to shut off and supplying high-pressure lubricating oil to the vane back pressure chamber (for example, , See Patent Document 1).

  FIG. 7 is a longitudinal sectional view of a conventional rotary compressor described in Patent Document 1. 8 is a cross-sectional view taken along line YY of FIG. 7, and FIG. 9 is a detailed cross-sectional view of the vane back pressure applying device.

  As shown in FIG. 7, the compressor includes a cylinder 101, a front side plate 106, a rear side plate 107, a high pressure case 112, a high pressure chamber 114, and a vane back pressure applying device 116.

  As shown in FIG. 8, the cylinder 101 includes a rotor 102, a vane slot 103 provided in the rotor 102, a plurality of vanes 104 slidably inserted into the vane slot 103, and the cylinder 101. A vane back pressure chamber 118 and a working chamber 108 configured by the rotor 102, the vane 104, the front side plate 106, and the rear side plate 107 are configured.

Further, as shown in FIG. 9, the vane back pressure applying device 116 is disposed in the first piston chamber 122 and the first spherical seat 120 and the first spherical body 121 that constitute the valve body that communicates and blocks the oil supply passage 119. The first gas from the first piston 123 for releasing the one spherical body 121 from the first ball seat 120, the first pressure introduction passage 124 for communicating the first piston back pressure chamber 125 and the working chamber 108, and the vane back pressure chamber 118. A third sphere 137 that prevents backflow of fluid to the supply passage, a second sphere seat 129 and a second sphere 130 that constitute a valve body that communicates and blocks the first gas supply passage 127 and the second gas supply passage 128; A second piston 132 disposed in the second piston chamber 131 for releasing the second sphere 130 from the second ball seat 129; a second elastic body 134 for applying a load to the second piston 132; a second lower piston chamber 133; And it is configured and Doshitsu 108 from the second pressure introduction passage 135 communicating.
Japanese Patent Publication No. 7-45877

In recent years, automobiles have been required to reduce the noise in the passenger compartment, and vehicle parts such as the engine and the fan motor in the car have become quieter year by year. Therefore, in a rotary compressor for a vehicle, there has been a demand for reducing noise generated when a vane protrudes from a vane slot and collides with a cylinder. However, in the configuration of the conventional vane back pressure applying device, when the compressor is stopped and left, depending on the stop position and state of the vane according to the stop position of the rotor, any one of the vanes has its own weight or back pressure applied. Due to the influence of the control of the device, it may fall to the lower part of the vane slot. When the compressor is started in this state, the vane is less likely to jump out of the vane slot, resulting in poor compression. In addition, it suddenly jumps out of the vane slot and suddenly jumps out of the vane slot, collides with the cylinder (hereinafter referred to as vane jumping), and has a problem of causing minute noise.

  Here, a conventional rotary compressor and a vane back pressure applying device will be described with reference to FIGS. 7, 8, and 9.

  When the compressor stops operating and is left to stand, the pressure difference between the high pressure chamber 114 and the working chamber 108 reaches a predetermined pressure difference, and the load on the second elastic body 134 is more than the load applied to the second sphere 130 due to the pressure difference. The vane is increased until the second piston 132 moves upward, pushes up the second sphere 130, leaves the second ball seat 129, and the high pressure chamber 114 and the vane back pressure chamber 118 communicate with each other via the first gas supply passage 127. The high pressure refrigerant gas in the high pressure chamber 114 is not supplied to the back pressure chamber 118.

  Further, the first piston back pressure chamber 125 becomes the low pressure of the working chamber 108 via the first pressure introduction path 124, and the first piston 123 moves downward due to the pressure difference with the high pressure chamber 114, and the first sphere 121. Sits on the first ball seat 120 and shuts off the oil supply passage 119. Therefore, the lubricating oil accumulated in the oil reservoir (oil reservoir) of the high-pressure case 112 is not supplied to the vane back pressure chamber 118.

  When these states continue for a long time, at least one of the vanes positioned above among the plurality of vanes 104 is immersed in the vane slot 103 by its own weight. The vane back pressure chamber 118 and the oil supply passage 119 remain filled with lubricating oil of an incompressible fluid.

  Further, since the gap between the vane 104, the rotor 102, the front side plate 106, and the rear side plate 107 is very small, the gap is sealed with lubricating oil, and the lubricating oil is sealed in a back pressure chamber or the like. It becomes.

  Furthermore, the first gas supply passage 127 is also filled with lubricating oil due to slight leakage from the third sphere 137 and the third ball seat 136.

  When the compressor is started in such a state, even if a centrifugal force acts on the vane 104 due to the rotation of the rotor 102, it is affected by the lubricating oil (incompressible fluid) remaining in the vane back pressure chamber 118 and the oil supply passage 119. Negative pressure is generated, and in rare cases, the vane 104 cannot jump out of the vane slot 103, resulting in compression failure. In addition, the delay of the vane 104 popping out from the vane slot 103 causes the vane 104 to collide with the cylinder 101 during the suction or compression process, and minute noise is occasionally generated.

  The present invention solves the above-mentioned conventional problems, and an object thereof is to provide a rotary type compressor that suppresses the occurrence of compression failure due to vane popping failure at the time of starting the compressor and the generation of minute noise due to vane jumping. To do.

In order to solve the above-described conventional problems, a rotary compressor of the present invention is provided with a gas supply passage communicating with a vane back pressure chamber and a lubricating oil discharge passage communicating with a working chamber, and the lubricating oil discharge passage is provided as a compressor. It communicates when stopped, and shuts off when the compressor starts.

  As a result, the lubricating oil remaining in the vane back pressure chamber when the compressor is stopped is discharged to the working chamber, and when the compressor is next started, the non-compressible lubricating oil disappears in the back pressure chamber and the passage, and the vane is smooth. Therefore, the vane jumping phenomenon is suppressed without impact on the cylinder, and the compression failure due to the vane popping failure is also suppressed.

  The rotary compressor of the present invention can suppress the occurrence of minute noise due to compression failure and vane jumping at the time of starting the compressor, so that the rotary compressor having high commerciality to cope with the recent reduction in noise. Can be provided.

  According to a first aspect of the present invention, the back pressure applying device is provided with a passage for shutting off the gas supply passage and the working chamber, and the passage is communicated when the compressor is stopped and shut off when the compressor is started. Since the lubricating oil remaining in the passage is discharged to the working chamber, the non-compressible lubricating oil does not remain in the back pressure chamber and the oil supply passage when the compressor is started next time. The vane is smoothly discharged from the vane slot by the high-pressure refrigerant gas pressure applied to the back pressure chamber, and the occurrence of compression failure and vane jumping due to vane popping failure can be suppressed.

  In the second invention, the communication blocking means of the passage that communicates the gas supply passage and the working chamber is constituted by the valve body and the elastic body, and the same effect as the first invention can be obtained.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment)
FIG. 1 is a longitudinal sectional view of a compressor according to a first embodiment of the present invention. FIG. 2 is a sectional view taken along line XX of FIG. 1, and FIG. 1 and FIG. The configuration will be described.

  In a cylinder 1 having a cylindrical inner wall, a substantially cylindrical rotor 2 is housed and disposed so that a part of its outer periphery forms a minute gap with the inner wall of the cylinder 1 and is rotatably supported. A plurality of (three in the illustrated embodiment) vane slots 3 are provided in the rotor 2 at equal intervals in the circumferential direction, and vanes 4 are slidably inserted into the vane slots 3, respectively. A drive shaft 5 is integrally coupled to the rotor 2, and the rotor 2 is rotated by rotating the drive shaft 5. Both front and rear end faces of the cylinder 1 are closed by joining a front side plate 6 and a rear side plate 7, and a working chamber 8 for compressing refrigerant gas is formed inside the cylinder 1. Further, a space behind the vane 4 divided by the vane slot 3, the front side plate 6 and the rear side plate 7 constitutes a vane back pressure chamber 18.

  A discharge valve 11 is arranged in the suction port 9 and the discharge hole 10 in the working chamber. The lower part of the high pressure chamber 14 constitutes an oil storage part 13. The oil storage unit 13 is configured to store the lubricating oil that is contained in the gas refrigerant compressed in the working chamber 8 in the form of mist and separated by the collision-type oil separating means. A gas discharge port 15 for discharging a compressed fluid (refrigerant gas) from the high pressure case 12 to the system cycle of the air conditioner is formed in the upper portion of the high pressure case 12. A vane back pressure applying device 16 is provided in the high pressure case 12 of the rear side plate 7, and the vane back pressure applying device 16 has a lubricating oil supply port 17 so as to be substantially perpendicular to the lubricating oil surface when the compressor is stationary. Is provided.

  Further, in the middle of the first gas supply passage 27 communicating with the vane back pressure chamber 18, one end thereof communicates with the first gas supply passage 27 and the other end communicates with the second pressure introduction passage 35. 38 is provided. The lubricating oil discharge passage 38 is provided with a valve body that is configured to cut off the lubricating oil discharge passage 38 at a predetermined pressure by a fourth spherical seat 39, a fourth spherical body 40, and a fourth elastic body 41 in the middle thereof. ing.

  About the compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below. FIG. 3 is a detailed view of the vane back pressure applying device 16. FIG. 3 shows the vane back pressure applying device 16 during operation of the compressor. The first piston back pressure chamber 25 becomes the high pressure of the working chamber 8 through the first pressure introduction path 24, and the first piston moves downward by the resultant force of the first elastic body 26 and the high pressure of the first piston back pressure chamber 25. It moves and the first sphere 21 is released from the first ball seat 20.

  For this reason, the vane back pressure chamber 18 is supplied with lubricating oil from the oil storage section 13 in the high pressure chamber 14 via the oil supply passage 19 by the vane back pressure applying device 16. At this time, due to the pressure difference between the high pressure chamber 14 and the second lower piston chamber 33, the second sphere 30 is seated on the second ball seat 29, and the first gas supply passage 27 and the second gas supply passage 28 are blocked. Therefore, the refrigerant gas is not supplied from the high pressure chamber 14. Since the pressure in the first gas supply passage 27 becomes the pressure of the second pressure introduction passage 35 through the gap between the second piston 32 and the second piston chamber 31, the third sphere 37 has the first pressure due to the pressure of the oil supply passage 19. It is seated on the three ball seat 36 and the communication between the first gas supply passage 27 and the oil supply passage 19 is blocked. Further, since the pressures of the first gas supply passage 27 and the second pressure introduction passage 35 are the same in the fourth spherical body 40 in the lubricating oil discharge passage 38, the fourth spherical body 40 is separated from the fourth spherical seat 39 by the fourth elastic body 41. Yes.

  FIG. 4 shows immediately after the compressor is stopped. Immediately after the compressor is stopped, the first piston back pressure chamber 25 becomes the low pressure of the working chamber 8 via the first pressure introduction path 24, so that the first piston 23 has the high pressure chamber 14 and the first piston back pressure. Due to the pressure difference with the chamber 25, the first sphere 21 is seated on the first ball seat 20, so that the oil supply passage 19 is blocked, and lubrication from the oil reservoir 13 in the high pressure chamber 14 to the vane back pressure chamber 18 is performed. No oil is supplied, and the pressure of the lubricating oil in the vane back pressure chamber 18 is the same as the pressure in the working chamber 8.

  At this time, since the pressure in the first gas supply passage 27 and the lubricating oil discharge passage 38 is the pressure in the working chamber 8, the third sphere 37 is released from the third ball seat 36 by its own weight, so that the vane back pressure is increased. The chamber 18 and the oil supply passage 19 communicate with each other, and the lubricating oil in the vane back pressure chamber 18 passes through the lubricating oil discharge passage 38 and is discharged to the working chamber 8 through the second pressure introduction passage 35. A part of the lubricating oil is replaced with the refrigerant gas in the working chamber 8.

  Therefore, even when the compressor starts to operate with the passage of time and at least one of the vanes 4 is immersed in the vane slot 3 due to its own weight and no refrigerant gas or lubricating oil is supplied, Since the back pressure chamber 18 is not filled only with the lubricating oil, the volume of the vane back pressure chamber 18 can be increased when the centrifugal force acts on the vane 4, and the vane can jump out and be compressed. .

  FIG. 5 shows a case where the time after the stop of the compressor has elapsed, the pressure in the high-pressure chamber 14 has decreased, and the pressure difference from the working chamber 8 has become a predetermined pressure or less. When the pressure difference between the high pressure chamber 14 and the working chamber 8 becomes a predetermined pressure or less, the second spherical body 30 is released from the second spherical seat 29 due to the load of the third second elastic body, and the first gas supply passage 27 is The high pressure chamber 14 communicates with the second gas supply passage 28. Therefore, the refrigerant gas in the high pressure chamber 14 flows into the working chamber 8 through the first gas supply passage 27 through the gap between the lubricating oil discharge passage 38 and the vane 4, the rotor 2, the front side plate 6 and the rear side plate 7. Therefore, the pressures in the high pressure chamber 14 and the working chamber 8 are equal.

  FIG. 6 shows a state at the start of operation of the compressor from the state of FIG. When the compressor starts operation from the state of FIG. 5, the internal pressure difference between the high pressure chamber 14 and the second lower piston chamber 33 becomes a predetermined pressure, and the second piston 32 moves downward due to the pressure difference, The refrigerant gas in the high pressure chamber 14 flows into the first gas supply passage 27 until the two-sphere body 30 is seated on the second ball seat 29.

  At this time, the pressure on the side communicating with the second pressure introduction path 35 of the lubricating oil discharge passage 38 becomes the pressure in the working chamber 8, and the pressure on the first gas supply passage 27 side becomes the pressure of the high pressure chamber 14. Here, the fourth sphere 40 is seated on the fourth ball seat 39 with a pressure difference smaller than the pressure difference between the high pressure chamber 14 where the second sphere 30 is seated on the second ball seat 29 and the second lower piston chamber 33. By setting the load of the fourth elastic body 41, the communication between the second pressure introduction path 35 and the first gas supply path 27 is blocked.

  Therefore, it is possible to prevent the refrigerant gas flowing in from the high pressure chamber 14 from flowing into the working chamber 8 through the second oil pressure introducing passage 35 via the lubricating oil discharge passage 38, and the refrigerant gas can be prevented from flowing into the vane back pressure chamber 18. Therefore, the pressure drop in the vane back pressure chamber 18 immediately after startup can be prevented, smooth startup is possible, and vane jumping can be suppressed. Also, compression failure due to vane popping failure is prevented.

  In addition, when the second sphere 30 is seated on the second sphere seat 29 and the first gas supply passage 27 and the second gas supply passage 28 are blocked, the lubricating oil is discharged regardless of whether the compressor is operating or stopped. Even if the passage 38 communicates, the same effect can be obtained.

  As described above, the rotary compressor according to the present invention discharges the lubricating oil in the vane back pressure chamber at the time of stoppage through the lubricating oil discharge passage provided with the opening / closing means communicating with the gas supply passage. Since it becomes possible to prevent the compression failure due to the vane popping failure due to the filling of the residual lubricating oil in the pressure chamber and to suppress the noise due to the vane jump, it can also be applied to applications such as compressors other than those for air conditioning.

A longitudinal sectional view of a rotary compressor in an embodiment of the present invention Sectional view taken along line XX in FIG. Sectional drawing of the vane back pressure provision apparatus at the time of the driving | operation in embodiment of this invention Sectional drawing of the vane back pressure provision apparatus immediately after the stop in embodiment of this invention Sectional drawing of the vane back pressure application apparatus when there is no pressure difference of a high pressure chamber and a working chamber in embodiment of this invention Sectional view of the vane back pressure applying device at the start of operation from FIG. Longitudinal sectional view of a conventional rotary compressor Sectional view along line YY in FIG. Sectional view of a conventional vane back pressure application device

Explanation of symbols

1 cylinder 2 rotor 3 vane slot 4 vane 5 drive shaft 6 front side plate 7 rear side plate 8 working chamber 9 suction port 10 discharge port 11 discharge valve 12 high pressure case 13 oil storage unit 14 high pressure chamber 15 gas discharge port 16 vane back pressure applying device 17 Lubricating oil supply port 18 Vane back pressure chamber 19 Oil supply passage 20 First ball seat 21 First sphere 22 First piston chamber 23 First piston 24 First pressure introduction passage 25 First piston back pressure chamber 26 First elastic body 27 First gas supply passage 28 Second gas supply passage 29 Second ball seat 30 Second sphere 31 Second piston chamber 32 Second piston 33 Second lower piston chamber 34 Second elastic body 35 Second pressure introduction path 36 Third sphere Seat 37 Third sphere 38 Lubricating oil discharge passage 39 Fourth sphere seat 40 Fourth sphere 41 Fourth elastic body

Claims (2)

A cylinder having a cylindrical hollow portion therein, a substantially cylindrical rotor in which at least a part of the outer peripheral portion is rotatably disposed close to the inner wall surface of the cylinder, and a plurality of the rotor in a substantially radial manner The vane slot is slidably inserted into the vane slot, the tip abuts against the inner wall surface of the cylinder, and the compression space formed between the cylinder and the rotor is at least a suction space and a discharge space. A vane for partitioning, a front side plate and a rear side plate that close both ends of the cylinder to form a working chamber therein; a vane back pressure chamber formed by the vane slot, the vane, the front side plate, and the rear side plate; In the rotary type compressor having a gas supply passage and an oil supply passage for cutting off the communication between the vane back pressure chamber and a vane back pressure applying device for controlling the vane back pressure, the back pressure applying device includes: Serial to the working chamber and the gas supply passage provided a passage for blocking communication, when the compressor stops the passage communicates, at the start of the compressor rotary compressor is characterized in that so as to cut off. 2. The rotary compressor according to claim 1, wherein the communication blocking means for the passage connecting the gas supply passage and the working chamber is constituted by a valve body and an elastic body.

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