JP2014001698A - Vane type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vane compressor capable of showing excellent quietness and mountability, without deteriorating quality after mounting, while decreasing a manufacturing cost.SOLUTION: A housing 1 of a vane type compressor is composed of a front housing 3 forming a suction chamber 15 and one end surface 13a of a cylinder chamber 13, and journaling one end of a drive shaft 9; a rear side plate 5 forming the other end surface 13c of the cylinder chamber 13, and journaling the other end of the drive shaft 9; and a shell 7 forming a discharge chamber 17 inside with the rear side plate 5, and formed with an attaching leg 7a. The front housing 3 or the rear side plate 5 has a cylinder forming portion 11 for forming an inner peripheral surface 13b of the cylinder chamber 13. The shell 7 stores the cylinder forming portion 11.

Description

  The present invention relates to a vane type compressor.

  Patent Document 1 discloses a conventional vane type compressor. In this 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. A compression mechanism is provided in the housing.

  The compression mechanism has a cylinder chamber, a rotor, and a plurality of vanes. The rotor is rotatably provided in the cylinder chamber by a drive shaft, and a plurality of vane grooves are formed. Each vane is provided so as to be able to appear and retract in the vane groove, and forms a compression chamber together with the inner peripheral surface of the cylinder chamber and the outer surface of the rotor.

  The housing forms a first end surface of the cylinder chamber and includes a first housing that supports one end of the drive shaft and a second housing that forms the other end surface of the cylinder chamber and supports the other end of the drive shaft. Become. The second housing has a cylinder forming portion that forms the inner peripheral surface of the cylinder chamber, and the first housing accommodates the second housing. The first housing and the second housing are formed with mounting feet for mounting on a vehicle or the like.

  When this vane type compressor is used for an air conditioner or the like of a vehicle, for example, the drive shaft is rotated by an electromagnetic clutch. Thus, the compression mechanism has a suction stroke in which the compression chamber sucks the 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 in which the high-pressure refrigerant gas in the compression chamber is discharged into the discharge chamber. Do the process.

  In addition, this vane type compressor has fewer parts than a vane type compressor formed by a side plate that forms a pair of one end surface and the other end surface of the cylinder chamber. Cost reduction can be realized.

JP 2011-153618 A

  However, in the conventional vane type compressor, since the mounting foot is formed on the second housing in which the inner peripheral surface of the cylinder chamber is formed by the cylinder forming portion, the cylinder chamber is deformed when mounted on a vehicle or the like. There is a fear. For this reason, during operation, the vanes of the compression mechanism may be abnormally inclined to cause seizure, or refrigerant gas may leak from the compression chamber. In this case, quality deterioration after mounting occurs.

  In this vane type compressor, a discharge space is formed in the cylinder forming portion of the second housing. In addition, a space between the cylinder forming portion and the first housing is an outer peripheral discharge space that communicates with the discharge space and circulates around the cylinder forming portion. The discharge space and the outer peripheral discharge space communicate with a discharge chamber in which a separator is provided. For this reason, since the first housing determines the volumes of the discharge space and the outer periphery discharge space, the discharge space and the outer periphery discharge space cannot be increased unless the first housing is increased. For this reason, discharge pulsation is large, and quietness is easily impaired. If a large discharge space and an outer peripheral discharge space are to be secured, the first housing must be enlarged, the trunk diameter becomes large, and the mountability to a vehicle or the like is impaired due to an increase in size and weight.

  The present invention has been made in view of the above-described conventional situation, and realizes a reduction in manufacturing cost, does not cause deterioration in quality after mounting, and can exhibit excellent quietness and mountability. Providing a mold compressor is a problem 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, a rotor provided in the cylinder chamber so as to be rotatable by the drive shaft, and provided with a plurality of vane grooves, and provided in the vane grooves so as to be protruded and retracted. A vane that forms the compression chamber together with an inner peripheral surface and an outer surface of the rotor;
The housing forms the suction chamber and one end surface of the cylinder chamber, forms a first housing that supports one end of the drive shaft, forms the other end surface of the cylinder chamber, and other than the drive shaft. A second housing that pivotally supports the end, and a shell in which the discharge chamber is formed in the interior together with the second housing, and a mounting foot is formed;
The first housing or the second housing has a cylinder forming portion that forms an inner peripheral surface of the cylinder chamber,
The shell accommodates the cylinder forming portion (claim 1).

  In the vane type compressor of the present invention, the number of parts is smaller than that of the vane type compressor formed by the side plate that forms a pair of one end surface and the other end surface of the cylinder chamber. Is possible.

  Further, in this vane type compressor, mounting legs are formed on the shell. When the first housing has a cylinder forming portion, the shell accommodates the cylinder forming portion of the first housing and the second housing. When the second housing has a cylinder forming portion, the shell accommodates the second housing having the cylinder forming portion. That is, no mounting foot is formed on the first housing or the second housing forming the inner peripheral surface of the cylinder chamber. For this reason, there is no possibility that the cylinder chamber is deformed when mounted on a vehicle or the like. For this reason, during operation, there is no possibility that the vanes of the compression mechanism are abnormally inclined to cause seizure or the refrigerant gas leaks from the compression chamber.

  Furthermore, in this vane type compressor, a discharge chamber is formed between the second housing and the shell. For this reason, even if it does not enlarge the 2nd housing, if the space between the 2nd housing and the shell is enlarged in the axial direction, the discharge chamber can be enlarged. For this reason, discharge pulsation is reduced and high silence is easily exhibited. Further, the trunk diameter can be maintained or reduced, and a reduction in size and weight can be realized.

  Therefore, according to the vane type compressor of the present invention, the manufacturing cost can be reduced, the quality after the mounting is not deteriorated, and the excellent quietness and mounting property can be exhibited.

  The first housing may be a front housing having a cylinder forming part. The second housing may be a rear side plate that forms the other end surface of the cylinder chamber. In this case, the other end of the drive shaft can be pivotally supported by a rear side plate that does not have a cylinder forming portion, so that positioning is easy and reduction in assembly man-hours can be realized.

  The first housing may be a front housing that forms one end surface of the cylinder chamber. The second housing may be a rear side plate having a cylinder forming portion and forming the other end surface of the cylinder chamber. In this case, since the shape of the front housing can be simplified, the manufacturing cost can be reduced at this point.

  The second housing is preferably press-fitted into the shell. In this case, during operation, the second housing does not vibrate in the direction perpendicular to the axis due to the pressure change in the compression chamber, and excellent quietness can be reliably exhibited.

  The second housing preferably includes a separator that separates the lubricating oil from the refrigerant gas discharged from the compression chamber and stores the lubricating oil in the discharge chamber. In this case, the number of parts dedicated to the separator can be reduced, and the manufacturing cost can be further reduced. 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 in the second housing (claim 4). 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 outlet opening that opens the discharge chamber to the outside is preferably displaced with respect to the opening at the upper end of the separation cylinder. When the outlet is not displaced from the opening at the upper end of the separation cylinder, the discharge pulsation transmitted to the inside of the separation cylinder is transmitted to the outside through the outlet and causes noise or the like in the air conditioner or the like. On the other hand, if the outlet is displaced with respect to the opening at the upper end of the separation cylinder, the discharge pulsation transmitted to the inside of the separation cylinder is hardly transmitted to the outside, and the quietness of the air conditioner or the like can be improved. For this reason, the quietness due to the expansion of the discharge chamber is made more effective.

  A back pressure chamber can be formed between the bottom surface of each vane and each vane groove. Each back pressure chamber can be communicated with the discharge chamber by a back pressure supply path in the compression stroke of the compression mechanism. And it is preferable that a shell has a recessed part between 2nd housings, and the recessed part comprises a part of back pressure supply path (Claim 6). In this case, if a concave portion is formed in the shell in advance, a part of the back pressure supply path can be easily secured by the concave portion by accommodating the second housing in the shell. Further, the channel cross-sectional area of the back pressure supply channel can be adjusted by the recess. Further, since the discharge hole and the like including the remaining back pressure supply path can be formed in the second housing in advance and the second housing can be accommodated in the shell, the number of manufacturing steps can be reduced.

  In the vane type compressor of the present invention, the cylinder chamber may extend in the axial direction of the drive shaft, and the cylinder perpendicular to the axis of the drive shaft may be formed in an elliptical column shape. It is preferable that the cylinder chamber has a cylindrical shape eccentric with respect to the axis of the drive shaft. If it is a vane type compressor having a cylindrical cylinder chamber, the cylinder chamber can be formed relatively easily, so that the manufacturing cost can be further reduced.

  The vane type compressor of the present invention realizes low manufacturing cost, does not cause quality deterioration after mounting, and can exhibit excellent quietness and mountability.

1 is a cross-sectional view of a vane type compressor of Example 1. FIG. FIG. 2 is a cross-sectional view perpendicular to the axis of FIG. 1 according to the vane compressor of Example 1. 1 is an enlarged cross-sectional view of a main part of a vane type compressor according to Embodiment 1. FIG. 4 is a cross-sectional view of a vane type compressor of Example 2. FIG. 4 is a cross-sectional view of a vane type compressor of Example 3. FIG. It is a principal part expanded sectional view of the vane type compressor of a modification.

  Embodiments 1 to 3 and modifications embodying the present invention will be described below with reference to the drawings.

Example 1
As shown in FIGS. 1 and 2, the vane type compressor of the first embodiment employs a front housing 3, a rear side plate 5, and a shell 7 as the housing 1. The front housing 3 is a first housing, and the rear side plate 5 is a second housing.

  The front housing 3 is provided with a shaft hole 3a through which the drive shaft 9 is inserted. Further, the front housing 3 has a cylinder forming portion 11, and a cylinder chamber 13 is recessed in the cylinder forming portion 11 from the rear. The cylinder chamber 13 has a cylindrical shape that is eccentric with respect to the axis O of the drive shaft 9. For this reason, the front housing 3 forms one end face 13 a and an inner peripheral face 13 b of the cylinder chamber 13.

  A suction chamber 15 is formed in the front housing 3. The suction chamber 15 opens to the outside by an inflow port 15a formed at the upper side, and communicates with the cylinder chamber 13 by a suction port 15b.

  The rear side plate 5 is common to the conventional vane type compressor. The rear side plate 5 is in contact with the cylinder forming portion 11 of the front housing 3, and the other end of the cylinder chamber 13 is closed by the rear side plate 5. For this reason, the rear side plate 5 forms the other end surface 13 c of the cylinder chamber 13. Further, the rear side plate 5 is provided with a shaft hole 5a in which the other end of the drive shaft 9 is accommodated.

  The shell 7 accommodates the cylinder forming portion 11 and the rear side plate 5 of the front housing 3. An O-ring 10 a is attached to the inner peripheral surface of the shell 7 on the front housing 3 side, and the O-ring 10 a seals between the shell 7 and the cylinder forming portion 11 of the front housing 3.

  The rear side plate 5 is press-fitted into the shell 7 as shown in FIG. A discharge chamber 17 is formed between the rear side plate 5 and the shell 7. As shown in FIG. 1, the discharge chamber 17 is opened to the outside by an outlet 17a. The shell 7 is formed with an appropriate number of mounting legs 7a. The front housing 3, the rear side plate 5 and the shell 7 are fastened by a plurality of bolts 45. The mounting foot 7a is attached to an engine or the like (not shown) of the vehicle.

  A shaft seal device 19 and a slide bearing 21 are provided in the shaft hole 3 a of the front housing 3. The shaft seal device 19 and the slide bearing 21 communicate with the suction chamber 15 through the communication passage 3b. A slide bearing 23 is provided in the shaft hole 5 a of the rear side plate 5. The drive shaft 9 is rotatably held in the shaft seal device 19 and the slide bearings 21 and 23.

  The tip of the drive shaft 9 protrudes through the shaft hole 3a of the front housing 3, 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.

  Further, a rotor 25 having a circular cross section is press-fitted into the drive shaft 9 so as to be disposed in the cylinder chamber 13. As shown in FIG. 2, two vane grooves 25 a are formed in the outer peripheral surface of the rotor 25. The vane grooves 25a are spaced equiangularly around the axis O of the drive shaft 9. A vane 27 is accommodated in each vane groove 25a so as to be able to appear and retract. A back pressure chamber 29 is formed between the bottom surface of each vane 27 and each vane groove 25a. Two compression chambers 31 are formed by the two vanes 27 and 27, the outer peripheral surface of the rotor 25, the one end surface 13a of the cylinder chamber 13, the inner peripheral surface 13b of the cylinder chamber 13, and the other end surface 13c of the cylinder chamber 13. . The suction port 15b communicates with the compression chamber 31 in the suction stroke. A compression mechanism C is constituted by the cylinder chamber 13, the rotor 25, and both the vanes 27.

  Further, the outer peripheral surface of the cylinder forming portion 11 is recessed toward the axis O, and a discharge space 33 is formed between the cylinder forming portion 11 and the shell 7. Further, a space between the cylinder forming portion 11 and the shell 7 is an outer peripheral discharge space 35 that communicates with the discharge space 33 and circulates around the cylinder forming portion 11. The compression chamber 31 and the discharge space 33 in the discharge stroke communicate with each other through a discharge port 33a. A discharge valve 37 that closes the discharge port 33 a and a retainer 39 that regulates the lift amount of the discharge valve 37 are provided in the discharge space 33.

  As shown in FIG. 1, a separator 41 is formed at the center of the other end surface of the rear side plate 5 so as to bulge to the rear side with a certain thickness. The separator 41 is located in the discharge chamber 17. A cylindrical guide surface 41 a for circulating the refrigerant gas discharged from the compression chamber 31 is formed in the separator 41. The guide surface 41a communicates with an oil separation chamber 41b that extends vertically in a cylindrical shape. The oil separation chamber 41b communicates with the discharge chamber 17 through the communication hole 41c. A cylindrical separation cylinder 43 that presses the refrigerant gas separated from the lubricating oil into the inside of the guide surface 41a and presses the refrigerant gas around the outer periphery of the guide surface 41a is press-fitted. The guide surface 41a and the separation cylinder 43 are coaxial. A discharge hole 33b is formed in the discharge space 33, and the discharge hole 33b communicates between the outer peripheral surface of the separation cylinder 43 and the guide surface 41a.

  The shell 7 is formed with a recess 7 b that communicates the bottom surface of the discharge chamber 17 and the lower edge of the rear side plate 5. The rear side plate 5 communicates with the recess 7b and extends upward, and includes a first back pressure hole 5b that communicates with the shaft hole 5a, and two first back pressure holes 5b that extend in the axial direction from the first back pressure hole 5b. Two back pressure holes 5c are formed. The rear side plate 5 has an annular groove 5d formed in an annular shape along the shaft hole 5a and partitioned by a slide bearing 23, and two third back pressure holes that communicate with the annular groove 5d and extend in the axial direction. 5e are formed. The third back pressure hole 5e communicates with the back pressure chamber 29 in the compression stroke and the discharge stroke. The recess 7b, the first back pressure hole 5b, the second back pressure hole 5c, the annular groove 5d, and the third back pressure hole 5e are back pressure supply paths. The rear side plate 5 is provided with a chattering prevention valve (not shown), and chattering is prevented by this chattering prevention valve.

  The outlet 17 a that opens the discharge chamber 17 to the outside is displaced with respect to the opening 43 a at the upper end of the separation cylinder 43. Although not shown, the outlet 17a 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 15a 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 this vane type compressor, when the drive shaft 9 is driven by an engine or the like, the rotor 25 rotates synchronously with the drive shaft 9 and the volume of the compression chamber 31 changes. For this reason, the refrigerant gas having passed through the evaporator is sucked into the suction chamber 15 from the inlet 15a. The refrigerant gas in the suction chamber 15 is sucked into the compression chamber 31 through the suction port 15b. The refrigerant gas compressed in the compression chamber 31 is discharged to the discharge space 33 and the outer discharge space 35 through the discharge port 33a, and between the outer peripheral surface of the separation cylinder 43 of the separator 41 and the guide surface 41a through the discharge hole 33b. Discharged. For this reason, lubricating oil is centrifuged from refrigerant gas. The refrigerant gas from which the lubricating oil has been separated is discharged to the condenser.

  During this time, the lubricating oil is supplied to the respective back pressure chambers 29 by the back pressure supply passage, urges the vanes 27 toward the inner peripheral surface 13b of the cylinder chamber 13, and serves to lubricate the vane grooves 25a and the like. Further, the lubricating oil leaked from the vane groove 25a and the like lubricates the sliding bearing 21 and the shaft sealing device 19 because the space between the shaft sealing device 19 and the sliding bearing 21 communicates with the suction chamber 15 through the communication passage 3b. From the communication path 3b to the suction chamber 15. On the other hand, the O-ring 10a seals the outer peripheral discharge space 35 to the outside.

  And this vane type compressor has fewer parts than the vane type compressor formed by the side plate that makes a pair of one end surface and the other end surface of the cylinder chamber, so it is possible to reduce manufacturing man-hours and assembly man-hours, etc. It is. In particular, in this vane type compressor, the other end of the drive shaft 9 can be pivotally supported by the rear side plate 5 that does not have the cylinder forming portion 11, so that the positioning is easy and the number of assembly steps can be reduced. Moreover, in this vane type compressor, since the rear side plate 5 has the separator 41, the parts dedicated to the separator can be reduced, and the manufacturing cost can be further reduced. Further, in this vane type compressor, since the cylinder chamber is cylindrical, the cylinder chamber 13 can be formed relatively easily, and the manufacturing cost can be further reduced.

  Further, in this vane type compressor, the mounting foot 7 a is formed on the shell 7, and the mounting foot is not formed on the front housing 3 forming the inner peripheral surface 13 b of the cylinder chamber 13. For this reason, there is no possibility that the cylinder chamber 13 is deformed when mounted on the vehicle. For this reason, during operation, there is no possibility that the vane 27 may be abnormally inclined to cause seizure or the refrigerant gas may leak from the compression chamber 31.

  Further, in this vane type compressor, a discharge chamber 17 is formed between the rear side plate 5 and the shell 7. For this reason, the discharge chamber 17 can be enlarged by enlarging the space between the rear side plate 5 and the shell 7 in the axial direction. For this reason, discharge pulsation is reduced and high silence is easily exhibited.

  Further, in this vane type compressor, since the rear side plate 5 is press-fitted into the shell 7, the rear side plate 5 does not vibrate in the direction perpendicular to the axis due to the pressure change in the compression chamber 31 during operation, and is excellent. The quietness can be reliably exhibited.

  Furthermore, in this vane type compressor, the body diameter can be maintained or reduced, and the size and weight can be reduced.

  Further, in this vane type compressor, since the outlet 17a is displaced with respect to the opening 43a at the upper end of the separation cylinder 43, the discharge pulsation transmitted to the inside of the separation cylinder 43 is difficult to be transmitted to the outside, and the air conditioner is quiet. Can be increased. For this reason, quietness due to the enlargement of the discharge chamber 17 is made more effective.

  Further, in this vane type compressor, the shell 7 has a recess 7b between the shell 7 and the rear side plate 5, and the recess 7b constitutes a part of the back pressure supply path. For this reason, by forming the concave portion 7b in the shell 7 in advance and housing the rear side plate 5 in the shell 7, a part of the back pressure supply path can be easily secured by the concave portion 7b. Further, the cross-sectional area of the back pressure supply path can be adjusted by the recess 7b. Further, since the discharge hole 33b and the like including the remaining back pressure supply path are formed in the rear side plate 5 in advance and the rear side plate 5 can be accommodated in the shell 7, it is possible to reduce the number of manufacturing steps.

  Therefore, according to this vane type compressor, the manufacturing cost can be reduced, the quality after mounting is not deteriorated, and excellent silence and mountability can be exhibited.

  Although an O-ring may be provided between the end surface of the shell 7 and the end surface of the front housing 3, in this case, it is preferable to locate the bolt 45 on the outer peripheral side of the vane compressor.

(Example 2)
As shown in FIG. 4, the vane compressor according to the second embodiment employs a front housing 4, a rear side plate 6, and a shell 8 as the housing 2. The front housing 4 is a first housing, and the rear side plate 6 is a second housing.

  The front housing 4 does not have the cylinder forming portion 11, and the rear side plate 6 has the cylinder forming portion 11. A cylinder chamber 13 is recessed in the cylinder forming portion 11 from one side. For this reason, the rear side plate 6 forms the inner peripheral surface 13 b and the other end surface 13 c of the cylinder chamber 13.

  The front housing 4 is in contact with the cylinder forming portion 11 of the rear side plate 6, and one end of the cylinder chamber 13 is closed by the front housing 4. For this reason, the front housing 4 forms one end face 13 a of the cylinder chamber 13. The shell 8 accommodates the rear side plate 6 having the cylinder forming portion 11. An O-ring 10 b is provided between the end surface of the shell 8 and the end surface of the front housing 4. The shell 8 and the front housing 4 are fastened by bolts (not shown) on the outer peripheral side of the O-ring 10b. Other configurations are the same as those of the first embodiment.

  In this vane type compressor, since the shape of the front housing 4 can be simplified, the manufacturing cost can be reduced in this respect. Other functions and effects are the same as those of the first embodiment.

(Example 3)
As shown in FIG. 5, the vane compressor according to the third embodiment employs a front side plate 12 and a shell 14 as the housing 6. The front side plate 12 is a first housing.

  The front side plate 12 is accommodated in the shell 14. A suction chamber 16 is formed around the shaft hole 3 a in the front side plate 12, and the suction chamber 16 communicates with an inflow port 15 a formed in the shell 14. In addition, O-rings 10 c and 10 d that partition the suction chamber 16 from the outside and the outer peripheral discharge space 35 are mounted between the front side plate 12 and the shell 14. Other configurations are the same as those of the first embodiment.

  In this vane compressor, since the suction chamber 16 is large, not only the discharge pulsation but also the suction pulsation can be reduced, and noise and vibration can be further reduced. Moreover, in this vane type compressor, the surplus thickness of the front side plate 12 is reduced, and weight reduction is also realized. Other functions and effects are the same as those of the first embodiment.

  In the first to third embodiments, as illustrated in FIG. 6, when the rear side plate 47 in which the O ring groove 47 a is formed is used, the O ring 49 is attached to the O ring groove 47 a, and the rear side plate 47 It is possible to press-fit and fit the rear or front portion of the O-ring groove 47a into the shells 7, 8, and 14. As a result, leakage of refrigerant gas and lubricating oil from the discharge chamber 17 can be reliably prevented.

  In the above, the present invention has been described according to the first to third embodiments and the modified examples. However, the present invention is not limited to the first to third embodiments and the modified examples, and may be appropriately selected without departing from the spirit of the present invention. Needless to say, it can be changed and applied.

  For example, the number and size of the vane grooves 25a and vanes 27 can be set as appropriate.

  The present invention is applicable to a vehicle air conditioner.

DESCRIPTION OF SYMBOLS 1 ... Housing 15 ... Suction chamber 17 ... Discharge chamber 31 ... Compression chamber 9 ... Drive shaft C ... Compression mechanism 13 ... Cylinder chamber 25a ... Vane groove 25 ... Rotor 27 ... Vane 13a ... One end surface 3, 4, 12 ... 1st housing 13c ... Other end surface 5, 6, 47 ... Second housing 7a ... Mounting feet 7,8 ... Shell 13b ... Inner peripheral surface 11 ... Cylinder forming part 41 ... Separator 41a ... Guide surface 43 ... Separating cylinder 17a ... Outlet 43a ... Opening 29 ... Back pressure chamber 7b ... Recess 7b, 5b, 5c, 5d, 5e ... Back pressure supply path

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, a rotor provided in the cylinder chamber so as to be rotatable by the drive shaft, and provided with a plurality of vane grooves, and provided in the vane grooves so as to be protruded and retracted. A vane that forms the compression chamber together with an inner peripheral surface and an outer surface of the rotor;
The housing forms the suction chamber and one end surface of the cylinder chamber, forms a first housing that supports one end of the drive shaft, forms the other end surface of the cylinder chamber, and other than the drive shaft. A second housing that pivotally supports the end, and a shell in which the discharge chamber is formed in the interior together with the second housing, and a mounting foot is formed;
The first housing or the second housing has a cylinder forming portion that forms an inner peripheral surface of the cylinder chamber,
The vane compressor, wherein the shell accommodates the cylinder forming portion.   The vane type compressor according to claim 1, wherein the second housing is press-fitted into the shell.   The vane compressor according to claim 1 or 2, wherein the second housing has a separator that separates lubricating oil from the refrigerant gas discharged from the compression chamber and stores the lubricating oil in the discharge chamber. . 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 3, wherein the guide surface is formed on the second housing.   The vane type compressor according to claim 4, wherein the outlet opening that opens the discharge chamber to the outside is displaced with respect to the opening at the upper end of the separation cylinder. A back pressure chamber is formed between the bottom surface of each vane and each vane groove,
Each back pressure chamber communicates with the discharge chamber by a back pressure supply path in the compression stroke of the compression mechanism,
The vane compressor according to any one of claims 1 to 5, wherein the shell has a concave portion between the shell and the second housing, and the concave portion constitutes a part of the back pressure supply path.   The vane type compressor according to any one of claims 1 to 6, wherein the cylinder chamber has a cylindrical shape that is eccentric with respect to an axis of the drive shaft.

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