JP2013217276A - Vane-type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vane-type compressor capable of reducing the backflow of a coolant gas or the like and the reverse rotation of a drive shaft while achieving downsizing, and also capable of achieving reduction in manufacturing cost.SOLUTION: In a vane-type compressor, a supply chamber 62 is formed at a back end of a drive shaft 9. A slide bearing 8 is provided between a rear side plate 5 and the drive shaft 9. An upstream passage 5m extending upward from a lower end of a discharge chamber 16 to the supply chamber 62 is formed at the rear side plate 5. A first downstream passage 8a is formed through the slide bearing 8 in a radial direction. A second downstream passage 5s and a third downstream passage 30 are formed at the rear side plate 5. An axial hole 9a and a radial hole 9b are formed at the drive shaft 9. The axial hole 9a and the radial hole 9b extend from the supply chamber 62 to an inner surface of the slide bearing 8. A separator 5e and the second and third downstream passages 5s and 30 are formed at the rear side plate 5.

Description

  The present invention relates to a vane type compressor.

  In a general vane type compressor, a suction chamber, a discharge chamber, and a compression chamber are formed in a housing, and a drive shaft is rotatably supported. Also, in the housing, the rotation of the drive shaft causes the compression chamber to draw a low-pressure refrigerant gas from the suction chamber, the compression stroke to compress the refrigerant gas in the compression chamber, and the high-pressure refrigerant gas in the compression chamber. A compression mechanism is provided for performing a discharge stroke for discharging into the discharge chamber.

  The compression mechanism has a cylinder chamber formed in the housing, and a rotor that is rotatably provided in the cylinder chamber by a drive shaft. A plurality of vane grooves are formed in the rotor in the radial direction. The compression mechanism has vanes that are provided in the vane grooves so as to be able to appear and retract, and that form a compression chamber positioned forward together with the inner surface of the cylinder chamber and the outer surface of the rotor.

  The housing includes a cylinder block in which a cylinder chamber is formed, a front side plate that closes the front of the cylinder chamber and forms a suction chamber, a rear side plate that closes the rear of the cylinder chamber and forms a discharge chamber, and a cylinder block And a shell for housing the front side plate and the rear side plate. The shell may have a front housing that forms a suction chamber with the front side plate, and a rear housing that is coupled to the front housing and forms a discharge chamber with the rear side plate.

  Further, a centrifugal separator that separates the lubricating oil from the refrigerant gas discharged from the compression chamber and stores the lubricating oil in the discharge chamber may be provided in the rear housing. A back pressure chamber is formed between the bottom surface of each vane and each vane groove, and each back pressure chamber communicates with the discharge chamber by a back pressure supply mechanism in a compression stroke.

  When this vane type compressor is used in an air conditioner such as a vehicle, the drive shaft is rotationally driven, for example, via an electromagnetic clutch. As a result, the compression mechanism operates. That is, the rotor rotates and the compression chamber performs a suction stroke, a compression stroke, and a discharge stroke. For this reason, the refrigerant gas is sucked into the compression chamber from the suction chamber, compressed in the compression chamber, and discharged into the discharge chamber. The high-pressure refrigerant gas discharged into the discharge chamber is supplied to the refrigeration circuit of the air conditioner. In the meantime, in this vane type compressor, during the compression stroke, high pressure lubricating oil is supplied to each back pressure chamber by the back pressure supply mechanism, and each vane is pressed against the inner surface of the cylinder chamber. Therefore, each vane is lubricated in the vane groove, chattering is prevented, and leakage of the refrigerant gas from the compression chamber is prevented, thereby improving efficiency.

  However, in this vane type compressor, when the drive shaft is not rotated by the electromagnetic clutch, the refrigerant gas in the discharge chamber and the lubricating oil contained therein flow back to the compression chamber through the back pressure supply mechanism and the back pressure chamber, and the drive shaft There is a problem that reversal can occur. In this case, since the evaporator is heated by backflow of the high-temperature refrigerant gas to the suction side of the refrigeration circuit, the temperature of the air blown out to the passenger compartment rises when the drive shaft is rotated again and the refrigeration efficiency decreases. Produce. In addition, liquid compression occurs during re-driving, resulting in a decrease in durability. Abnormal noise is also generated during reverse rotation. For this reason, Patent Documents 1 to 6 propose vane type compressors that can solve this problem.

  In the vane type compressors of Patent Documents 1 to 4, an open / close valve is provided in the back pressure supply mechanism. The on-off valves of Patent Documents 1 and 4 are configured to communicate the discharge chamber and the back pressure chamber by a pressure difference between the upstream side and the downstream side of the discharge valve. Further, the on-off valve of Patent Document 2 disconnects the discharge chamber from the back pressure chamber while the drive shaft is not rotated, and if the drive shaft continues to rotate, the pressure oil pumped by the spiral groove causes the discharge chamber and the back pressure chamber to communicate with each other. The pressure chamber is configured to communicate with the pressure chamber. The on-off valve of Patent Document 3 is provided so as to be swingable between a first position and a second position with respect to the rotor due to a pressure difference, and when in the first position, the discharge chamber and the back pressure chamber are not connected. The communication chamber is configured to communicate with the discharge chamber and the back pressure chamber when in the second position. These on-off valves make the discharge chamber and the back pressure chamber out of communication unless the drive shaft is rotated.

  Moreover, in the vane type compressor of patent document 5, the check valve is provided in the discharge chamber. In the vane type compressor of Patent Document 6, a check valve is provided in the suction chamber. These check valves prevent the backflow of the refrigerant gas.

JP-A-55-134787 JP-A-56-154191 JP 58-174193 A JP-A-60-162092 JP-A-7-155103 JP-A-7-259779

  However, if the conventional on-off valve is provided in the back pressure supply mechanism of the vane type compressor, or if a check valve is provided in the discharge chamber or the suction chamber, the space occupied by the on-off valve or the check valve is increased in the vane type compressor. Therefore, the vane type compressor is easily increased in size.

  In addition, vane compressors are also required to reduce manufacturing costs by reducing the number of parts.

  The present invention has been made in view of the above-described conventional situation, and can reduce the backflow of refrigerant gas and the like and the reverse of the drive shaft while realizing a reduction in size, and can also reduce the manufacturing cost. Providing a vane-type compressor that is possible is an issue to be solved.

The vane type compressor of the present invention has a suction chamber, a discharge chamber, and a compression chamber formed in a housing, and a drive shaft is rotatably supported in the housing, and the compression is performed in the housing by the rotation of the drive shaft. A suction stroke in which the chamber sucks low-pressure refrigerant gas from the suction chamber, a compression stroke in which the refrigerant gas is compressed in the compression chamber, and a discharge stroke in which the high-pressure refrigerant gas in the compression chamber is discharged into the discharge chamber. A compression mechanism is provided,
The compression mechanism includes a cylinder chamber formed in the housing, a rotor that is rotatably provided in the cylinder chamber by the drive shaft, and a plurality of vane grooves formed in a radial direction. And a vane that forms the compression chamber together with the inner surface of the cylinder chamber and the outer surface of the rotor,
A separator is provided for separating the lubricating oil from the refrigerant gas discharged from the compression chamber and storing the lubricating oil in the discharge chamber;
A back pressure chamber is formed between the bottom surface of each vane and each vane groove,
Each of the back pressure chambers is a vane type compressor communicated with the discharge chamber by a back pressure supply mechanism in the compression stroke,
The back pressure supply mechanism is located on the downstream side of the rotation path formed in the drive shaft or a rotating body that rotates synchronously with the drive shaft, and communicates the rotation path and the back pressure chamber. An intermittent mechanism having a lower flow path,
The intermittent mechanism is configured such that the rotation path is in communication with or out of communication with the discharge chamber and each of the back pressure chambers according to the phase in the rotation direction of the drive shaft.
The housing includes a cylinder block in which the cylinder chamber is formed, a front side plate that closes the front of the cylinder chamber and forms the suction chamber, and closes the rear of the cylinder chamber and forms the discharge chamber. A rear side plate, a cylinder block, the front side plate, and a shell for housing the rear side plate;
The rear side plate includes the separator and the lower flow path (Claim 1).

  In the vane compressor of the present invention, the back pressure supply mechanism includes a rotation path and an intermittent mechanism, and the intermittent mechanism is located on the downstream side of the rotation path and has a lower flow path that communicates the rotation path and the back pressure chamber. Then, the intermittent mechanism causes the rotation path to communicate with the discharge chamber and each back pressure chamber according to the phase in the rotation direction of the drive shaft, or to make it non-communication. In other words, if the drive shaft is in the first phase in the rotation direction, the rotation path communicates the discharge chamber and each back pressure chamber, and if the drive shaft is in the second phase in the rotation direction, the rotation path is The discharge chamber and each back pressure chamber are not in communication.

  For this reason, high-pressure lubricating oil is intermittently supplied to each back pressure chamber during the compression stroke. For this reason, each vane is intermittently pressed against the inner surface of the cylinder chamber. Therefore, each vane is lubricated in the vane groove, chattering is prevented, and leakage of the refrigerant gas from the compression chamber is prevented, thereby improving efficiency.

  If the rotation of the drive shaft is stopped and the discharge chamber and each back pressure chamber are not communicated with each other in this state, the reverse flow of the refrigerant gas or the like and the reverse rotation of the drive shaft do not occur. Even if the rotation of the drive shaft is stopped in a state where the discharge chamber and each back pressure chamber communicate with each other, if the reverse flow of the refrigerant gas or the like and the reverse rotation of the drive shaft occur, the phase of the drive shaft is thereby shifted. Therefore, the discharge chamber and each back pressure chamber are immediately disconnected, and no further reverse flow of the refrigerant gas or the like and reverse rotation of the drive shaft occur. For this reason, this vane type compressor can prevent the reverse flow of the refrigerant gas and the like and the reverse rotation of the drive shaft reliably and early.

  Here, in this vane type compressor, the rotation path is formed in the drive shaft or the rotating body. For this reason, it is not necessary to secure a space in the vane compressor for providing a conventional on-off valve or check valve, and the vane compressor does not increase in size. In addition, since the rotation path can be easily formed on the drive shaft and the rotating body, it is possible to save time and labor when developing many different models for vehicles and the like.

  Moreover, in this vane type compressor, since the rear side plate includes the separator and the lower flow path, the number of parts is reduced.

  Therefore, according to this vane type compressor, while realizing miniaturization, it is possible to reduce the backflow of the refrigerant gas and the like and the reverse rotation of the drive shaft, and to reduce the manufacturing cost.

  The rotating body may be integral with the drive shaft, and is separate from the drive shaft, but may be fixed to the drive shaft so as to rotate synchronously with the drive shaft. As the separator, in addition to a centrifugal separator, a separator other than a centrifugal separator such as a collision type can be employed.

  The separator has a cylindrical guide surface and a cylindrical separation cylinder that is provided on the inner side of the guide surface and is substantially coaxial with the guide surface. The separator discharges refrigerant gas discharged from the compression chamber to the outer periphery of the guide surface and the separation cylinder. The lubricating oil can be separated by circulating around the surface, and the refrigerant gas can be guided to the inside of the separation cylinder and discharged to the outside of the compressor. This guide surface is preferably formed on the rear side plate (claim 2). In this case, the separator is a centrifugal separator. Thereby, reduction of a number of parts and size reduction can be implement | achieved easily.

  The rear side plate can include a supply chamber that houses the rear end of the drive shaft or the rotating body, and an upper flow path that connects the supply chamber and the discharge chamber. In this case, the intermittent mechanism communicates with the supply path, the upper flow path communicating with the discharge chamber and the supply chamber, the back pressure chambers of the compression stroke, and the communication with or without communication with the rotation path. It consists of a lower flow path.

  In this case, high-pressure lubricating oil existing in the discharge chamber reaches the upper flow path, the supply chamber, and the rotation path. If the rotation path communicates with the lower flow path by the phase of the drive shaft, high-pressure lubricating oil in the rotation path is supplied to each back pressure chamber via the lower flow path. Further, if the rotation path is not in communication with the lower flow path due to the phase of the drive shaft, the high-pressure lubricating oil in the rotation path is not supplied to each back pressure chamber via the lower flow path.

  As the intermittent mechanism, the following more specific configuration can be adopted. That is, a sliding bearing can be provided between the rear side plate and the drive shaft or the rotating body. The upper flow path is formed in the rear side plate, extends upward from the discharge chamber, and can communicate with the supply chamber. The lower flow path includes a first lower flow path formed in a radial direction on the slide bearing or the rear side plate, a second lower flow path formed in the rear side plate and communicating with the first lower flow path, and each back pressure chamber from the second lower flow path. And a third lower flow path extending up to. The rotation path may have an intermittent port that extends from the supply chamber to the inner surface of the slide bearing or the rear side plate and communicates with or does not communicate with the first lower flow path.

  In this case, high-pressure lubricating oil that may exist in the discharge chamber reaches the upper flow path, the supply chamber, and the rotation path. If the rotation path communicates with the first lower flow path by the phase of the drive shaft, the high-pressure lubricating oil in the rotation path passes through the first lower flow path, the second lower flow path, and the third lower flow paths to each back pressure chamber. Supplied. In addition, if the rotation path is not in communication with the first lower flow path due to the phase of the drive shaft, the high-pressure lubricating oil in the rotation path passes through the first lower flow path, the second lower flow path, and the third lower flow paths to each back pressure. Not supplied to the room.

  A sliding bearing is provided between the rear side plate and the drive shaft or the rotating body. The plain bearing is less likely to cause relative rotation with the rear side plate and is likely to cause relative rotation with the drive shaft or the rotating body. For this reason, the rotation path can extend from the supply chamber to the sliding bearing or the intermittent opening on the inner surface of the rear side plate. The slide bearing need not be provided in the entire axial length facing the drive shaft or the rotating body. For this reason, the first lower flow path can be formed in the radial direction on the slide bearing or the rear side plate. The first lower flow path may be single or plural.

  The second lower flow path is formed in the rear side plate and communicates with the first lower flow path. The second lower flow path may be an annular shape that is coaxial with the drive shaft or the rotating body, or may be an arc shape that is coaxial with these. A part of the second lower flow path may be formed along the outer surface of the sliding bearing.

  The third lower flow path extends from the second lower flow path to each back pressure chamber. The number of third lower flow paths may be the same as the number of back pressure chambers. In this case, since each third lower flow path can communicate with a single second lower flow path and each back pressure chamber, the high-pressure lubricating oil that can exist in the discharge chamber is easily supplied to each back pressure chamber equally. .

  If sliding bearings are used in this way, and the communication and non-communication between the rotary path and each back pressure chamber are performed by sliding bearings and rear side plates, the number of parts increases when conventional on-off valves and check valves are used, The increase in assembly man-hours and equipment, the increase in parts and the increase in man-hours for assembly can be achieved, and the manufacturing cost can be reduced.

  As the intermittent mechanism, the following more specific configuration can also be adopted. That is, the rear side plate and the drive shaft or the rotating body can come into contact with each other by a cylindrical sliding surface. The upper flow path is formed in the rear side plate, extends upward from the discharge chamber, and can communicate with the supply chamber. The lower flow path can include a first lower flow path formed on the sliding surface of the rear side plate and a second lower flow path extending from the first lower flow path to each back pressure chamber. The rotation path may have an intermittent port that extends from the supply chamber to the drive shaft or the sliding surface of the rotating body and communicates with or does not communicate with the first lower flow path.

  In this case, high-pressure lubricating oil that may exist in the discharge chamber reaches the upper flow path, the supply chamber, and the rotation path. If the rotation path communicates with the first lower flow path by the phase of the drive shaft, high-pressure lubricating oil in the rotation path is supplied to each back pressure chamber via the first lower flow path and each second lower flow path. Further, if the rotation path is not in communication with the first lower flow path due to the phase of the drive shaft, the high-pressure lubricating oil in the rotation path is not supplied to the back pressure chambers via the first lower flow path and the second lower flow paths.

  Since no sliding bearing is provided between the rear side plate and the drive shaft or the rotating body, the rotation path can extend from the supply chamber to the intermittent opening on the sliding surface of the drive shaft or the rotating body. The first lower flow path may be formed on the sliding surface of the rear side plate. The first lower flow path may be single or plural.

  The second lower flow path extends from the first lower flow path to each back pressure chamber. The number of second lower flow paths may be the same as the number of back pressure chambers. In this case, since each second lower flow path can communicate with the single first lower flow path and each back pressure chamber, the high-pressure lubricating oil that can exist in the discharge chamber is easily supplied to each back pressure chamber equally. .

  If the rear side plate and the drive shaft or the rotating body are brought into contact with each other by the cylindrical sliding surface in this way, the number of parts can be further reduced, the number of assembling steps and equipment, the number of parts and the number of assembling steps can be reduced. Further, the manufacturing cost can be further reduced.

  The rotation path may include an axial hole extending in the axial direction and a radial hole communicating with the axial hole and extending in the radial direction to the intermittent opening. Further, the rotation path may be formed of an axial groove that is recessed in the axial direction and has a front end serving as an intermittent opening.

  According to the vane type compressor of the present invention, while realizing downsizing, it is possible to reduce the backflow of refrigerant gas and the like and the reverse rotation of the drive shaft, and to reduce the manufacturing cost.

1 is a cross-sectional view of a vane type compressor of Example 1. FIG. It is a vane type compressor of Example 1, and is a II-II arrow sectional view of Drawing 1. 1 is an enlarged cross-sectional view of a main part of a vane type compressor according to Embodiment 1. FIG. FIG. 4 is a rear view of the vane compressor according to the first embodiment, in which a rear housing is sectioned. FIG. 4 is an enlarged cross-sectional view of a main part of a rear side plate during processing according to the vane type compressor of the first embodiment. It is a vane type compressor of Example 1, and is a principal part rear view of a partial section. It is a vane type compressor of Example 1, and is a principal part rear view of a partial section. 3 is an enlarged cross-sectional view of a main part of a vane type compressor of Example 2. FIG. It is a vane type compressor of Example 2, and is a principal part rear view of a partial cross section. FIG. 6 is an enlarged cross-sectional view of a main part of a vane type compressor according to a third embodiment. It is a vane type compressor of Example 3, and is a principal part rear view of a partial cross section. 6 is an enlarged cross-sectional view of a main part of a vane type compressor of Example 4. FIG. It is a vane type compressor of Example 4, and is a principal part rear view of a partial cross section. FIG. 6 is an enlarged cross-sectional view of a main part of a vane compressor according to a fifth embodiment. It is a vane type compressor of Example 5, and is a principal part rear view of a partial cross section.

  Hereinafter, Embodiments 1 to 5 embodying the present invention will be described with reference to the drawings.

Example 1
As shown in FIGS. 1 and 2, the vane compressor according to the first embodiment is fixed in a state in which a cylinder block 3 is accommodated in a front housing 1 and a rear housing 2 that are coupled to each other. The cylinder block 3 is formed with an elliptical cylinder chamber 3a in a direction perpendicular to the axis. The front housing 1, the rear housing 2, and the cylinder block 3 correspond to the housing. Further, the front housing 1 and the rear housing 2 correspond to the shell 60.

  A front side plate 4 and a rear side plate 5 are housed and fixed in the front housing 1 and the rear housing 2, and the front and rear of the cylinder chamber 3a are closed by the front side plate 4 and the rear side plate 5, respectively. .

  A drive shaft 9 is rotatably held in shaft holes 4 a and 5 a of the front side plate 4 and the rear side plate 5 via a shaft seal device 6 and sliding bearings 7 and 8. The shaft hole 5 a is recessed from the front with respect to the rear side plate 5, and the sliding bearing 8 is press-fitted into the shaft hole 5 a of the rear side plate 5 from the front. The tip of the drive shaft 9 protrudes through the shaft hole 1a of the front housing 1, and an electromagnetic clutch or pulley (not shown) is fixed to the tip. A driving force is transmitted to the electromagnetic clutch or pulley by the engine or motor of the vehicle.

  A rotor 10 having a circular cross section is fixed to the drive shaft 9 so as to be disposed in the cylinder chamber 3a. As shown in FIG. 2, five vane grooves 10 a are formed in the radial direction on the outer peripheral surface of the rotor 10, and the vanes 11 are accommodated in the respective vane grooves 10 a so as to be able to appear and retract. A back pressure chamber 40 is formed between the bottom surface of each vane 11 and each vane groove 10a. Five compression chambers 12 are formed by two adjacent vanes 11 and 11, the outer peripheral surface of the rotor 10, the inner peripheral surface of the cylinder block 3, the inner surface of the front side plate 4, and the inner surface of the rear side plate 5.

  As shown in FIG. 1, a suction chamber 13 is formed between the front housing 1 and the front side plate 4. In the front housing 1, an inflow port 1b for connecting the suction chamber 13 to the outside is opened upward. The front side plate 4 is provided with two suction holes 4 b communicating with the suction chamber 13, and each suction hole 4 b communicates with each suction space 3 b of the cylinder block 3. As shown in FIG. 2, each suction space 3b communicates with the compression chamber 12 in the suction stroke by a suction port 3c.

  In addition, two discharge spaces 3 d are formed between the cylinder block 3 and the rear housing 2. The compression chamber 12 in the discharge stroke communicates with each discharge space 3d through a discharge port 3e. In each discharge space 3d, a discharge valve 14 for closing the discharge port 3e and a retainer 15 for regulating the lift amount of the discharge valve 14 are provided. The drive shaft 9, the cylinder block 3, the rotor 10, each vane 11, the discharge valve 14, the retainer 15 and the like constitute a compression mechanism 1C.

  As shown in FIGS. 3 and 4, a bulging portion 5 p that bulges to the rear side with a certain thickness is formed at the center of the outer surface of the rear side plate 5. The bulging portion 5p includes a step portion 5f that extends to the left and right while covering the drive shaft 9 and the rear end of the sliding bearing 8, a hanging portion 5g that extends downward with the same thickness as the step portion 5f, and a step portion 5f and a hanging portion 5g. It consists of a separator portion 5e that protrudes rearward and extends vertically.

  As shown in FIG. 3, a supply chamber 62 that houses the drive shaft 9 and the rear end of the slide bearing 8 is formed in the step portion 5 f. Further, as shown in FIG. 4, the step portion 5f is provided with two discharge holes 5j and 5k that are communicated with the discharge spaces 3d at both ends and extend to the separator portion 5e.

  As shown in FIG. 1, a discharge chamber 16 is formed between the rear side plate 5 and the rear housing 2. The separator unit 5 e is located in the discharge chamber 16. As shown in FIG. 3, a cylindrical guide surface 17b for circulating the refrigerant gas discharged from the compression chamber 12 is formed in the separator portion 5e. The guide surface 17b communicates with an oil separation chamber 17a that extends vertically in a cylindrical shape. Inside the guide surface 17b, there is press-fitted a cylindrical separation cylinder 18 that circulates the refrigerant gas on its outer peripheral surface and guides the refrigerant gas from which the lubricating oil has been separated to the inside thereof. The guide surface 17b and the separation cylinder 18 are coaxial. The discharge holes 5j and 5k shown in FIG. 4 communicate with the outer peripheral surface of the separation cylinder 18 and the guide surface 17b. A nozzle 61 projects horizontally at the lower end of the separator portion 5e. In the nozzle 61, a communication port 61a is formed which communicates the lower part of the oil separation chamber 17a with the discharge chamber 16.

  On the inner surface (front surface) of the rear side plate 5, as shown in FIGS. 2 and 6 to 7, a pair of oil drain grooves 5 c having a fan shape is recessed. Each oil drain groove 5 c communicates with the back pressure chamber 40 in the suction stroke or the like by the rotation of the rotor 10. As shown in FIGS. 1 and 3, the rear side plate 5 is provided with a valve chamber 5d communicating with the discharge chamber 16 and each oil drain groove 5c. The valve chamber 5d has a ball-like shape. The valve body 20 is accommodated. The valve body 20 is urged in a direction to open the valve chamber 5d by a spring 19 housed in the valve chamber 5d. The valve body 20 is prevented from being detached by a circlip 63. The oil drain groove 5c, the valve chamber 5d, the valve body 20, the spring 19, and the circlip 63 constitute a chattering prevention valve 64 that prevents chattering.

  As shown in FIG. 3, an upper flow path 5 m extending upward from the lower end is provided through the hanging part 5 g of the rear side plate 5. The lower end of the upper flow path 5m communicates with the discharge chamber 16, and the upper end of the upper flow path 5m communicates with the supply chamber 62. The rear side plate 5 is also formed with a thickness 5n for the purpose of weight reduction.

  As shown in FIGS. 3 and 6-7, the drive shaft 9 has one shaft hole 9a extending in the axial direction from the rear end, and two shafts communicating with the shaft hole 9a and extending in the radial direction to the intermittent opening 9x. The diameter hole 9b is formed. Both diameter holes 9 b are opened at the diameter position of the drive shaft 9. The shaft hole 9 a and the diameter hole 9 b are rotation paths extending from the supply chamber 62 to the inner surface of the sliding bearing 8.

  In addition, two first lower flow paths 8a are provided in the sliding bearing 8 in the radial direction. Here, the position where both the first lower flow paths 8 a are provided is the position from the rear end of the drive shaft 9 communicating with the supply chamber 62 to the radial hole 9 b. Both first lower flow paths 8 a are open to the inner surface of the sliding bearing 8 at a position passing through the axis of the drive shaft 9. The shaft hole 5a of the rear side plate 5 is formed with a second lower flow path 5s formed along the outer surface of the slide bearing 8 so as to communicate with the first lower flow path 8a. The second lower flow path 5 s has an annular shape that is coaxial with the drive shaft 9. In addition, two third lower flow paths 30 extending from the second lower flow path 5 s to the end surface of the rotor 10 are formed in the rear side plate 5. Both the third lower flow paths 30 communicate with the back pressure chamber 40 in the compression stroke by the rotation of the rotor 10. The first lower flow path 8a, the second lower flow path 5s, and the third lower flow path 30 are the lower flow paths. The supply chamber 62, the upper flow path, and the lower flow path are intermittent mechanisms.

  As shown in FIG. 1, the rear housing 2 is formed with an outlet 2a for connecting the upper end of the discharge chamber 16 to the outside. The outlet 2 a is located above the separation cylinder 18.

  The rear side plate 5 is manufactured as follows. First, the workpiece 5w shown in FIG. 5 is manufactured by casting. As a material, an aluminum alloy or the like can be adopted. In the work 5w, a bulging portion 5p including a step portion 5f, a hanging portion 5g, and a separator portion 5e is formed, and a nozzle 61 without a communication port 61a is formed. The workpiece 5w is formed with a hollow 5n, a supply chamber 62 is formed in the stepped portion 5f, and an oil separation chamber 17a is formed in the separator portion 5e. These thinning 5n, supply chamber 62 and oil separation chamber 17a are formed by a slide mold.

  For this work 5w, the shaft hole 5a, the second lower flow path 5s, the third lower flow path 30, the oil drain groove 5c, the valve chamber 5d, the discharge holes 5j, 5k, the O-ring groove 5x, the upper flow path 5m, the communication port 61a, The press-fit portion 18a is formed by cutting. Then, as shown in FIG. 3, the sliding bearing 8 is press-fitted into the shaft hole 5a, and the separation cylinder 18 is press-fitted into the press-fit portion 18a. Further, the spring 19 and the valve body 20 are inserted into the valve chamber 5d, and these are prevented from coming off by the circlip 63.

  The drive shaft 9, the sliding bearings 7 and 8, the front side plate 4, the cylinder block 3, each vane 11, the discharge valve 14, the retainer 15, the rear side plate 5, and the chattering prevention valve 64 are assembled as a sub assembly SA.

  An O-ring is attached to the sub-assembly SA, and this is inserted into the rear housing 2. Next, an O-ring is mounted on the rear housing 2 and the front housing 1 is put on the O-ring. Then, a plurality of bolts 71 shown in FIG. 2 are fastened. Thus, the vane type compressor of Example 1 is assembled.

  Although not shown, the outlet 2a is connected to the condenser by piping, the condenser is connected to the expansion valve by piping, the expansion valve is connected to the evaporator by piping, and the evaporator is connected to the inlet 1b by piping. ing. The piping, the condenser, the expansion valve, and the evaporator constitute an external refrigeration circuit. The refrigeration circuit including the compressor constitutes a vehicle air conditioner.

  In the vane type compressor configured as described above, when the drive shaft 9 is driven by an engine or the like, the rotor 10 rotates synchronously with the drive shaft 9 and the compression chamber 12 changes in volume. For this reason, the refrigerant gas having passed through the evaporator is sucked into the suction chamber 13 from the inlet 1b. The refrigerant gas in the suction chamber 13 is sucked into the compression chamber 12 through the suction hole 4b, the suction space 3b, and the suction port 3c. Further, the refrigerant gas compressed in the compression chamber 12 passes through the discharge port 3e and the discharge space 3d and is discharged into the discharge holes 5j and 5k as shown in FIGS. For this reason, the refrigerant gas is discharged toward the guide surface 17b in the separator portion 5e. For this reason, the refrigerant gas circulates between the guide surface 17b and the outer peripheral surface of the separation cylinder 18, and the lubricating oil is centrifuged from the refrigerant gas.

  The separated lubricating oil is stored in the discharge chamber 16 from the oil separation chamber 17a through the communication port 61a. The lubricating oil in the discharge chamber 16 is supplied to the supply chamber 62 through the upper flow path 5m as shown in FIG. 3 because the discharge chamber 16 has a high pressure. At this time, since the upper flow path 5m is formed in a straight line, there is no pressure loss and processing is also easy. Since the slide bearing 8 is press-fitted into the shaft hole 5a of the rear side plate 5, the slide bearing 8 and the drive shaft 9 cause relative rotation. The lubricating oil supplied to the supply chamber 62 is supplied between the sliding bearing 8 and the drive shaft 9 and lubricates between them.

  Then, as shown in FIG. 6, if both the diameter holes 9b communicate with both the first lower flow paths 8a by the phase in the rotational direction of the drive shaft 9, the high-pressure lubricating oil in the shaft holes 9a and both diameter holes 9b The first lower flow path 8a, the second lower flow path 5s, and the third lower flow paths 30 are supplied to the back pressure chambers 40 shown in FIGS. In particular, in this vane type compressor, each third lower flow path 30 communicates the single second lower flow path 5s with each back pressure chamber 40, so that the high-pressure lubricating oil present in the discharge chamber 16 is even. It is easy to be supplied to each back pressure chamber 40.

  In addition, as shown in FIG. 7, if the both-diameter holes 9b are not in communication with both first lower flow paths 8a due to the phase of the drive shaft 9, the high-pressure lubricating oil in the shaft holes 9a and both-diameter holes 9b 1 is not supplied to each back pressure chamber 40 via the lower flow path 8a, the second lower flow path 5s, and the third lower flow paths 30.

  For this reason, high-pressure lubricating oil is intermittently supplied to each back pressure chamber 40 during the compression stroke. For this reason, each vane 11 is intermittently pressed against the inner surface of the cylinder chamber 3a. Therefore, each vane 11 is lubricated in the vane groove 10a, chattering is prevented, and leakage of the refrigerant gas from the compression chamber 12 is prevented, thereby improving efficiency.

  Moreover, by supplying lubricating oil to the back pressure chamber 40 intermittently, the back pressure of each vane 11 can be adjusted by adjusting the supply amount of the back pressure. For this reason, it is also possible to reduce the pressing force of each vane 11 and to reduce the power during operation.

  If the rotation of the drive shaft 9 is stopped and both the diameter holes 9b are not in communication with the first lower flow paths 8a in this state, the reverse flow of the refrigerant gas or the like and the reverse rotation of the drive shaft 9 do not occur. As shown in FIG. 6, even if the rotation of the drive shaft 9 is stopped in a state where both the diameter holes 9b communicate with both the first lower flow paths 8a, the reverse flow of the refrigerant gas or the like and the reverse rotation of the drive shaft 9 are slightly caused. If this occurs, as shown in FIG. 7, the phase of the drive shaft 9 is thereby shifted, so that both the diameter holes 9 b are immediately disconnected from both the first lower flow paths 8 a, and the reverse flow of the refrigerant gas or the like is driven. There is no reversal of the shaft 9. For this reason, this vane type compressor can prevent the reverse flow of the refrigerant gas and the like and the reverse rotation of the drive shaft 9 reliably and early.

  Here, in this vane type compressor, a shaft hole 9 a and both diameter holes 9 b are formed in the drive shaft 9. For this reason, it is not necessary to secure a space in the vane compressor for providing a conventional on-off valve or check valve, and the vane compressor does not increase in size. Further, since the shaft hole 9a and the both-diameter holes 9b can be easily formed in the drive shaft 9, it is possible to save time and labor when developing many different models for vehicles and the like.

  Moreover, in this vane type compressor, since the guide surface 17b is formed in the separator part 5e of the rear side plate 5, reduction of a number of parts and size reduction can be implement | achieved easily. In particular, in this vane type compressor, since the rear side plate 5 includes the separator portion 5e and the lower flow path 5s of the intermittent mechanism, it is possible to easily reduce the number of parts and reduce the size.

  Furthermore, in this vane type compressor, it is not necessary to change the position where the on-off valve and the check valve are provided for each of many different models depending on the vehicle or the like, and the development effort can be reduced.

  Further, in this vane type compressor, the sliding bearing 8 is adopted, and the shaft hole 9a and the diameter hole 9b are communicated with and disconnected from the back pressure chambers 40 by the sliding bearing 8. When the check valve is adopted, the number of parts, the number of assembling steps and facilities, the number of parts and the number of assembling steps are not increased, and the manufacturing cost can be reduced.

  Therefore, according to this vane type compressor, it is possible to reduce the backflow of the refrigerant gas and the like and the reverse rotation of the drive shaft 9 while reducing the size, and to reduce the manufacturing cost.

(Example 2)
In the vane type compressor of the second embodiment, as shown in FIG. 8, the center hole formed in the drive shaft 9 is the shaft hole 9e of the rotation path. As shown in FIG. 9, the shaft hole 9e communicates with one radial hole 9f extending in the radial direction from the front end of the shaft hole 9e to the intermittent port 9x. The shaft hole 9e and the diameter hole 9f are rotation paths.

  The rear side plate 5 has three first lower flow paths 5u that communicate with the second lower flow path 5s. As shown in FIG. 8, each first lower flow path 5u extends rearward in the axial direction and is open to the shaft hole 5a. The first lower flow path 5u, the second lower flow path 5s, and the second lower flow path 30 are lower flow paths. The length from the front end face of the rear side plate 5 to the intermittent opening 9x is longer than the length from the rear end face of the drive shaft 9 to the intermittent opening 9x. Other configurations are the same as those of the first embodiment.

  In this vane type compressor, since the length from the front end surface of the rear side plate 5 to the intermittent port 9x is longer than the length from the rear end surface of the drive shaft 9 to the intermittent port 9x, the seal length formed on the inner surface of the slide bearing 8 is increased. Therefore, the high-pressure lubricant is easily supplied from the supply chamber 62 at a necessary timing by the intermittent mechanism. For this reason, the vane 11 more reliably intermittently presses the inner surface of the cylinder chamber 3a, and the efficiency is improved. Other functions and effects are the same as those of the first embodiment.

(Example 3)
As shown in FIGS. 10 and 11, the vane compressor according to the third embodiment employs a shaft groove 9 c that is recessed in the axial direction as a rotation path and an intermittent port. The front end of the shaft groove 9c becomes the intermittent opening 9x. Other configurations are the same as those of the first embodiment. In this vane type compressor, the same effects as those of the first embodiment can be obtained.

Example 4
As shown in FIGS. 12 and 13, the vane compressor of the fourth embodiment does not employ the sliding bearing 8 as in the first to third embodiments, and the rear side plate 5 and the drive shaft 9 are cylindrical. The sliding surfaces 5v and 9d are in contact with each other. Two first lower flow paths 5t are formed on the sliding surface 5V of the rear side plate 5. Here, the position where both the first lower flow paths 5t are formed is a position where the distance from the rear end of the drive shaft 9 is equal to the diameter hole 9b. Both first lower flow paths 5t open to the sliding surface 5v at a position passing through the axis of the drive shaft 9.

  Further, two second lower flow paths 30 extending from each first lower flow path 5t to the end surface of the rotor 10 are formed in the rear side plate 5. The first lower flow path 5t and the second lower flow path 30 are the lower flow paths. Other configurations are the same as those of the first embodiment.

  In this vane type compressor, if the diameter hole 9b communicates with the first lower flow path 5t by the phase of the drive shaft 9, high-pressure lubricating oil in the shaft hole 9a and the diameter hole 9b is transferred to the first lower flow path 5t and each second flow path. It is supplied to each back pressure chamber 40 via the lower flow path 30. Further, if the diameter hole 9b is not in communication with the first lower flow path 5t due to the phase of the drive shaft 9, the high-pressure lubricating oil in the shaft hole 9a and the diameter hole 9b is in the first lower flow path 5t and each second lower flow path 30. Not supplied to each back pressure chamber.

  If the rear side plate 5 and the drive shaft 9 are brought into contact with each other by the cylindrical sliding surfaces 5v and 9d in this way, the number of parts can be further reduced, the number of assembling steps and equipment, the number of parts and the number of assembling steps can be reduced. Due to the reduction, the manufacturing cost can be further reduced.

(Example 5)
As shown in FIGS. 14 and 15, the vane compressor of the fifth embodiment employs a shaft groove 9 c that is recessed in the axial direction as a rotation path and an intermittent port. The front end of the shaft groove 9c becomes the intermittent opening 9x. Other configurations are the same as those of the fourth embodiment. In this vane type compressor, the same effects as those of the fourth embodiment can be obtained.

  In the above, the present invention has been described with reference to the first to fifth embodiments. However, the present invention is not limited to the first to fifth embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

  For example, the rotation path may be formed not on the drive shaft 9 but on a rotating body that rotates synchronously with the drive shaft.

Further, according to the present invention, not only a single cylinder type vane type compressor having a single cylinder chamber 3a and a rotor 10 but also a plurality of cylinder chambers and a rotor are connected in tandem as in the first to fifth embodiments. It is also applicable to tandem vane type compressors.

  The present invention is applicable to a vehicle air conditioner.

1. Front housing (housing)
2 ... Rear housing (housing)
3 ... Cylinder block (housing)
3a ... Cylinder chamber 4 ... Front side plate 5 ... Rear side plate 5m ... Upper flow path 5v, 9d ... Sliding surface 5s ... Second lower flow path (lower flow path)
5t ... 1st lower flow path (lower flow path)
5u ... 1st lower flow path (lower flow path)
8 ... Slide bearing 8a ... First lower flow path (lower flow path)
DESCRIPTION OF SYMBOLS 9 ... Drive shaft 9a, 9b, 9c, 17f, 5m, 8a, 5s, 30, 5t ... Back pressure supply mechanism 9a ... Shaft hole (rotation path)
9b ... Diameter hole (rotating path)
9c ... Shaft groove (rotating path)
9x ... intermittent port 10 ... rotor 10a ... vane groove 11 ... vane 12 ... compression chamber 13 ... suction chamber 14 ... discharge valve 16 ... discharge chamber
1C: compression mechanism 17f, 5m, 8a, 5s, 30, 5t ... intermittent mechanism 62 ... supply chamber 30 ... second and third lower flow paths (lower flow paths)
40 ... back pressure chamber 17b ... guide surface 18 ... separation cylinder

Claims (7)

A suction chamber, a discharge chamber, and a compression chamber are formed in the housing, and a drive shaft is rotatably supported in the housing. The rotation of the drive shaft causes the compression chamber to move from the suction chamber to a low-pressure refrigerant. A compression mechanism is provided for performing a suction stroke for sucking gas, a compression stroke for compressing the refrigerant gas in the compression chamber, and a discharge stroke for discharging the high-pressure refrigerant gas in the compression chamber to the discharge chamber;
The compression mechanism includes a cylinder chamber formed in the housing, a rotor that is rotatably provided in the cylinder chamber by the drive shaft, and a plurality of vane grooves formed in a radial direction. And a vane that forms the compression chamber together with the inner surface of the cylinder chamber and the outer surface of the rotor,
A separator is provided for separating the lubricating oil from the refrigerant gas discharged from the compression chamber and storing the lubricating oil in the discharge chamber;
A back pressure chamber is formed between the bottom surface of each vane and each vane groove,
Each of the back pressure chambers is a vane type compressor communicated with the discharge chamber by a back pressure supply mechanism in the compression stroke,
The back pressure supply mechanism is located on the downstream side of the rotation path formed in the drive shaft or a rotating body that rotates synchronously with the drive shaft, and communicates the rotation path and the back pressure chamber. An intermittent mechanism having a lower flow path,
The intermittent mechanism is configured such that the rotation path is in communication with or out of communication with the discharge chamber and each of the back pressure chambers according to the phase in the rotation direction of the drive shaft.
The housing includes a cylinder block in which the cylinder chamber is formed, a front side plate that closes the front of the cylinder chamber and forms the suction chamber, and closes the rear of the cylinder chamber and forms the discharge chamber. A rear side plate, a cylinder block, the front side plate, and a shell for housing the rear side plate;
The vane type compressor, wherein the rear side plate includes the separator and the lower flow path. The separator has a cylindrical guide surface and a cylindrical separation cylinder provided on the inner side of the guide surface and substantially coaxial with the guide surface, and guides the refrigerant gas discharged from the compression chamber. Circulating between the surface and the outer peripheral surface of the separation cylinder to separate the lubricating oil, guiding the refrigerant gas to the inside of the separation cylinder and discharging it to the outside of the compressor,
The vane type compressor according to claim 1, wherein the guide surface is formed on the rear side plate.   3. The vane type compression according to claim 1, wherein the rear side plate includes a supply chamber that houses a rear end of the drive shaft or the rotating body, and an upper flow path that communicates the supply chamber with the discharge chamber. Machine. A sliding bearing is provided between the rear side plate and the drive shaft or the rotating body,
The upper flow path is formed in the rear side plate, extends upward from the discharge chamber, communicates with the supply chamber,
The lower flow path includes a first lower flow path formed in the sliding bearing or the rear side plate in a radial direction, a second lower flow path formed in the rear side plate and communicating with the first lower flow path, and the second downstream flow path. A third lower flow path extending from the road to each of the back pressure chambers,
4. The vane compressor according to claim 3, wherein the rotation path has an intermittent port that extends from the supply chamber to an inner surface of the sliding bearing or the rear side plate and communicates with or does not communicate with the first lower flow path. The rear side plate and the drive shaft or the rotating body are in contact with each other by a cylindrical sliding surface,
The upper flow path is formed in the rear side plate, extends upward from the discharge chamber, communicates with the supply chamber,
The lower flow path includes a first lower flow path formed on the sliding surface of the rear side plate and a second lower flow path extending from the first lower flow path to each of the back pressure chambers,
4. The vane compressor according to claim 3, wherein the rotation path has an intermittent port that extends from the supply chamber to the drive shaft or the sliding surface of the rotating body and communicates with or does not communicate with the first lower flow path.   6. The vane compressor according to claim 4, wherein the rotation path includes an axial hole extending in an axial direction and a radial hole communicating with the axial hole and extending in a radial direction to the intermittent opening.   The vane type compressor according to claim 4 or 5, wherein the rotary path is formed by an axial groove that is recessed in the axial direction and has a front end serving as the intermittent port.

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