JP2015004288A - Vane type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vane type compressor capable of keeping the distribution of clearance at the axial front and rear parts of a rotor in a proper state by balancing the force acting on the front and rear parts of the rotor and a driving shaft integrated with the rotor by generating the pressure difference between the axial front and rear parts of the rotor.SOLUTION: A pair of side blocks 13, 21 closing both axial ends of a cylinder 12 are provided with at least one of a suction pressure introduction groove formed on a face opposed to a rotor 3 of one side block 13 to introduce a fluid equivalent to a suction pressure, a groove-contracted portion 41a formed by contracting a part of an area where a vane groove of an oil introduction groove 41 formed on a face opposed to the rotor 3 of one of the side blocks can be opened, to the radial inner side of the rotor, and a groove-expanded portion 42a formed by expanding a part of an area where a vane groove of an oil introduction groove 42 formed on the other side block can be opened, to the radial outer side of the rotor.

Description

  The present invention relates to a vane type compressor, and more particularly to a vane type compressor having a structure useful for maintaining a proper distribution of clearances before and after a rotor.

  There are various types of vane compressors used in the refrigeration cycle of a vehicle air conditioner (see the following patent publication). For example, as represented by the configurations of FIGS. And a pair of side blocks (a first side block 13 and a second side block 21) that close both ends of the cylinder 12 in the axial direction. A drive shaft 2 rotatably supported by the pair of side blocks, a rotor 3 fixedly mounted on the drive shaft 2 and rotatably accommodated in a cylinder, and from the outer peripheral surface of the rotor 3 toward the inside The formed vane groove 8 and the vane 4 accommodated in the vane groove 8 so as to be retractable and retracted. The centrifugal force generated by the rotation of the rotor 3 and the back pressure chamber 8a provided at the bottom of the vane groove 8 are provided. Back pressure from Therefore, the compression chamber 31 is defined by the rotor 3 and the vane 4 in a space closed by the cylinder 12 and the pair of side blocks 13 and 21 in contact with and supported by the inner peripheral surface (cam surface 11) of the cylinder 12. The fluid sucked into the compression chamber 31 is compressed as the rotor 3 rotates.

  In such a vane compressor, in order to ensure smooth rotation of the rotor 3 and to prevent a reduction in compression efficiency, the front and rear end faces in the axial direction of the rotor 3 and the respective side blocks 13.21 The dimensions of the rotor are controlled so that an appropriate clearance is formed between them, and the oil introduction grooves (where oil is introduced) are formed on the surfaces of the side blocks 13 and 21 where the end faces of the rotor 3 face each other. A first oil introduction groove 41 is formed in the first side block 13, and a second oil introduction groove 42) is formed in the second side block 21, and the bearing portion of the drive shaft 2 and the rotor 3 and the side blocks 13, 21 Lubricating oil is supplied to the sliding contact surface. The oil introduction grooves 41 and 42 formed in each side block communicate with each other through the back pressure chamber 8a of the rotor 3, and as shown in FIG. 13 and the second side block 21 are formed in a symmetrical shape.

JP 2013-050038 A JP 2007-064163 A

However, one end (front end) of the drive shaft 2 on which the rotor 3 is fixed is required to be directly connected to the drive source, or a power transmission member (pulley, electromagnetic clutch, etc.) for transmitting the power of the drive source is fixed. Therefore, one side block (second side block 21) is made to penetrate.
For this reason, when one end of the drive shaft 2 passes through one side block (second side block 21) and protrudes outside the housing, atmospheric pressure acts on one end side of the drive shaft 2, On the other hand, since a relatively high pressure inside the compressor acts on the other end side (side supported by the first side block 13) of the drive shaft 2, the drive shaft 2 is disposed on both front and rear sides in the axial direction. Due to the acting pressure difference, the rotor 3 is biased to one end (front side) protruding from the side block, and the axial position of the rotor 3 is the side block side (second side) through which the drive shaft 2 passes. The clearance between the front end of the rotor 3 and the front second side block 21 becomes relatively small, and the rear end of the rotor 3 and the first side block 13 on the rear side become closer to the block 21 side). The clearance between is relative It increases in the. For this reason, on the rear side (the first side block 13 side) where the clearance becomes larger, fluid leaks through the clearance between adjacent compression chambers (oil seal becomes worse), resulting in a disadvantage that the compression efficiency is lowered. .

  As indicated by the one-dot chain line in FIG. 5, when the electromagnetic clutch 33 is provided on the drive shaft 2 as a power transmission member, a leaf spring constituting the clutch is attracted to the electromagnetic clutch 33 that transmits power to the rotor 3. Since the spring force acts to urge the rotor 3 rearward (on the first side block 13 side) via the drive shaft 2, the axial position of the rotor 3 is the front and rear in the axial direction of the drive shaft 2. Although it is determined by the pressure difference acting on both sides and the spring force of the electromagnetic clutch 33, in general, many vane type compressors are small, and the spring force of the electromagnetic clutch is also the pressure difference between the front and rear ends of the drive shaft 2. Therefore, even if the electromagnetic clutch 33 is provided, the clearance on the rear side of the rotor 3 (the clearance between the rotor 3 and the first side block 13) is not increased on the front side of the rotor. Lance can not be overcome larger state than (clearance between the rotor 3 and the second side block 21), a disadvantage that the compression efficiency is lowered still occur.

  Therefore, conventionally, in order to keep the clearance on the rear side of the rotor within an allowable range, the total clearance before and after the rotor in the axial direction (the sum of clearances before and after the rotor) is managed so as not to become too large. However, there are disadvantages such as complicating the management process and reducing productivity.

  The present invention has been made in view of such circumstances, and balances the forces acting on the front and rear of the rotor and the drive shaft integral with the rotor by causing a difference in the pressure acting on the front and rear of the rotor in the axial direction. Thus, the main object is to provide a vane type compressor capable of maintaining the distribution of the clearance in the axial direction of the rotor in an appropriate state.

  In order to achieve the above object, a vane compressor according to the present invention includes a housing, a cam surface formed therein, a cylinder provided in the housing, and both ends of the cylinder in the axial direction closed. A pair of side blocks provided on the drive shaft, a drive shaft rotatably supported by the pair of side blocks, a rotor fixedly mounted on the drive shaft and rotatably accommodated in the cylinder, and the rotor A plurality of formed vane grooves; a plurality of vanes that are slidably inserted into the vane grooves; and tips that protrude and retract from the vane grooves and slide on the cam surface; the cylinder and the pair of side blocks; A compression chamber formed by the rotor and the vane in a space closed by the air, a suction port provided for sucking fluid into the compression chamber, and a compression by the compression chamber. A discharge port provided for discharging the fluid, a discharge chamber for discharging the fluid, an oil chamber for storing oil pressurized by the discharged fluid, and the rotor of the pair of side blocks In the vane type compressor, comprising: an oil introduction groove that is provided on a surface opposed to the oil supply groove and that opens the vane groove; and at least one oil communication path that communicates the oil chamber and the oil introduction groove. One side block of one of the side blocks is provided on a surface facing the rotor, the suction pressure introduction groove into which the fluid corresponding to the suction pressure is introduced, and a surface of the one side block facing the rotor. A portion of the oil introduction groove where the vane groove can be opened is reduced to a radially inner side of the rotor, and the pair of side blocks. A groove enlargement part provided on a surface of the other side block facing the rotor, and a part of the oil introduction groove where the vane groove can be opened is enlarged outward in the radial direction of the rotor; It has at least any one of these.

Therefore, by providing a suction pressure introduction groove into which a fluid corresponding to the suction pressure is introduced on the surface facing the rotor of one side block, the suction pressure introduction groove is formed with respect to the end surface of the rotor facing one side block. Since only the pressure corresponding to the suction pressure acts on the opposed portions, it is possible to reduce the force for urging the rotor toward the other side block.
In addition, by providing a groove reduction portion on the surface of the one side block facing the rotor, the area where oil introduced into the oil introduction groove formed in one side block acts on the rotor can be reduced. It is possible to reduce the force for urging the rotor toward the other side block.
Furthermore, by providing a groove expanding portion on the surface facing the rotor of the other side block, the area where the oil introduced into the oil introduction groove formed in the other side block acts on the rotor can be increased. It becomes possible to increase the force that urges the rotor toward one side block.
For this reason, by providing at least one of the suction pressure introducing groove, the groove reducing portion, and the groove expanding portion, it is possible to reduce the force for urging the rotor to the other side block. It is possible to adjust the distribution of the clearances on both sides of the rotor in the axial direction by balancing the forces acting on the front and rear of the drive shaft integrated with the rotor.

  In addition, the structure of the side block described above is a relatively low pressure space in the electric compressor in which the drive shaft passes through the other side block and is directly connected to the shaft of the electric motor. Or in the case where the drive shaft passes through the other side block and protrudes to the outside of the housing, the low-pressure space of the drive shaft or the side protruding outside and the side disposed in the housing of the compressor This is an effective configuration for adjusting the bias in the distribution of clearance due to the pressure difference between the two.

Here, it is preferable that the suction pressure introduction groove is provided in the one side block between the drive shaft and the cam surface and over an angular range corresponding to the suction port.
By providing the suction pressure introduction groove in an angular range corresponding to the suction port, it is possible to make the suction pressure introduction groove large in a range that does not inhibit the compression of the fluid in the compression stroke, and the other side block that acts on the rotor It is possible to reduce the urging force to the side as much as possible.

In addition, the groove reducing portion may be configured such that the pressure of the compression chamber in the driving state of the vane compressor is in a range between the drive shaft and a position where the outer peripheral edge of the rotor faces the one side block. Is preferably provided within an angle range corresponding to a region that is equal to or lower than the pressure of the oil introduction groove.
An oil introduction groove is provided on one side block by providing a groove reduction portion within a range in which the pressure in the compression chamber is lower than the pressure in the oil introduction groove (the suction stroke region and the initial compression stroke region). The area facing the rotor can be reduced, and the pressure gradient from the compression chamber to the oil introduction groove at the location where the groove reduction portion is provided can be made gentle, and the other side block acting on the rotor can be moved to the side. It becomes possible to reduce the urging force.

Further, the groove enlarged portion may be configured such that the pressure of the compression chamber is in a driving state of the vane compressor in a range between the drive shaft and a position where the outer peripheral edge of the rotor faces the other side block. Is preferably provided within an angle range corresponding to a region that is equal to or lower than the pressure of the oil introduction groove.
The oil introduction groove is provided on the other side block by providing a groove expansion portion within a region where the pressure of the compression chamber is lower than the pressure of the oil introduction groove (region of suction stroke and initial region of compression stroke). Increases the area facing the rotor, and the pressure gradient from the compression chamber to the oil introduction groove at the location where the groove expansion portion is provided can be made steep, so that one side block acting on the rotor It is possible to increase the urging force.

  The housing includes a first housing member integrally formed with the cylinder having an inner peripheral surface formed into a perfect circle, and a first side block that closes one end of the cylinder in the axial direction; A second housing member formed with a second side block that closes the other end side of the cylinder in the axial direction is combined to form the pair of side blocks, the first side block and the second side block. You may comprise by this side block.

  As described above, according to the present invention, the suction pressure introduction groove for reducing the force for urging the rotor toward the other side block is provided on the surface of the one side block facing the rotor. A configuration in which a groove reducing portion for reducing a force for urging the rotor toward the other side block is provided on a surface facing the rotor of one side block, and a rotor on a surface facing the rotor of the other side block. By adopting at least one of the configuration in which a groove expanding portion for increasing the force that urges the rotor toward one side block is provided, a difference is caused in the pressure acting in the axial direction of the rotor. By balancing the forces acting on the front and back of the rotor and the drive shaft integral with the rotor, it is possible to maintain the distribution of the clearance in the front and rear of the rotor in the proper state. That. For this reason, the compression efficiency is not reduced while ensuring smooth rotation of the rotor.

FIG. 1 is a sectional view showing a vane type compressor according to the present invention. Fig.2 (a) is the figure which looked at the rear side from the AA line of the vane type compressor shown in FIG. 1, and shows the state which removed the rotor. Moreover, FIG.2 (b) is the figure which looked at the front side from the BB line of the vane type compressor shown in FIG. 3 (a) and 3 (b) are views in which hatching is applied to a portion different from the conventional side block (FIG. 6) in the portion shown in FIG. 2 where the rotor of the side block faces. FIG. 4A is a diagram for explaining a change in pressure from the cylinder inner diameter to the rotor inner diameter in a portion where the oil introduction groove is formed, and FIG. 4B is a diagram illustrating the pressure in the compression chamber and the oil It is a diagram which shows the pressure of an introduction groove | channel according to the rotation angle of a rotor. FIG. 5 is a cross-sectional view showing a conventional vane compressor. Fig.6 (a) is the figure which looked at the rear side from the AA line of the vane type compressor shown in FIG. 5, and shows the state which removed the rotor. FIG. 6B is a view of the vane compressor shown in FIG. 5 as viewed from the BB line.

  Hereinafter, the vane type compressor of the present invention will be described with reference to the drawings.

  FIG. 1 shows a vane compressor suitable for a refrigeration cycle using a refrigerant as a working fluid. The vane compressor 1 includes a drive shaft 2, a rotor 3 that is fixed to the drive shaft 2 and rotates as the drive shaft 2 rotates, a vane 4 attached to the rotor 3, and the drive shaft 2. A housing 5 that supports the rotor 3 and the vanes 4 while supporting the rotor 3 and the vanes 4 is provided. When FIG. 1 is viewed sideways, the left side is the front side and the right side is the rear side.

The housing 5 is configured by combining two members of the first housing member 10 and the second housing member 20.
The first housing member 10 accommodates the rotor 3 and is integrally formed so as to close the cylinder 12 having the cam surface 11 formed on the inner peripheral surface and one end side (rear side) of the cylinder 12 in the axial direction. The first side block 13 is formed. The inner peripheral surface (cam surface 11) of the cylinder 12 is formed in a perfect circle in cross section, and the axial length is substantially equal to the axial length of the rotor 3 described later.

  The second housing member 20 is in contact with an end face on the other end side (front side) in the axial direction of the cylinder 12 and closes the other end side. The shell 22 is formed integrally and extends in the axial direction of the drive shaft 2, and is formed so as to surround the outer peripheral surfaces of the cylinder 12 and the first side block 13.

  The first housing member 10 and the second housing member 20 are fastened in the axial direction via a connector 6 such as a bolt, and the first side block 13 and the second side block 13 of the first housing member 10 are connected. A sealing member 7 such as an O-ring is interposed between the housing member 20 and the shell 22 so as to be airtightly sealed.

  In addition, the second housing member 20 is integrally formed with a boss portion 23 extending from the second side block 21 to the front side. A pulley 32 (shown by a one-dot chain line) that transmits rotational power to the drive shaft 2 is rotatably mounted on the boss portion 23, and rotational power is transmitted from the pulley 32 to the drive shaft 2 via an electromagnetic clutch 33. It is like that.

  The drive shaft 2 is rotatably supported by the first side block 13 and the second side block 21 via bearings 14 and 24, and the tip portion is the second of the second housing member 20. The side block 21 passes through and protrudes into the boss portion 23, and the boss portion 23 is hermetically sealed by a seal member 25 provided between the boss portion 23 and the boss portion 23.

The electromagnetic clutch 33 is configured such that the clutch plate 35 is opposed to the friction surface 32a of the pulley 32 via a leaf spring 34 attached in an axial direction to a portion protruding from the housing (second side block) of the drive shaft 2. The clutch plate 35 is attracted to the pulley 32 by energizing the excitation coil 36 contained in the pulley 32, and the rotational power from the traveling engine applied to the pulley 32 is passed through the clutch plate 35 and the plate spring 34. The transmission to the drive shaft 2 is known per se.
By the adsorption of the clutch plate 35 to the pulley 32, the urging force toward the first side block 13 (rear side) is urged to the drive shaft 2 by the spring force of the plate spring 34.

  The rotor 3 has a circular cross section, and the drive shaft 2 is inserted through an insertion hole 3a provided at the center of the rotor 3, and the rotor 3 is fixed to the drive shaft 2 in a state where the centers of the shafts coincide with each other. Yes. Further, the axial center of the cylinder 12 and the axial center of the rotor 3 (drive shaft 2) are such that the outer peripheral surface of the rotor 3 and the inner peripheral surface (cam surface 11) of the cylinder 12 abut at one place in the circumferential direction. They are shifted (they are shifted by a half of the difference between the inner diameter of the cylinder 12 and the outer diameter of the rotor 3). In the space closed by the cylinder 12, the first side block 13 and the second side block 21, a compression space 30 is defined between the inner peripheral surface of the cylinder 12 and the outer peripheral surface of the rotor 3. ing.

  A plurality of vane grooves 8 are formed on the outer peripheral surface of the rotor 3, and the vanes 4 are slidably inserted into the respective vane grooves 8. The vane groove 8 is opened not only on the outer peripheral surface of the rotor 3 but also on the end surfaces facing the first side block 13 and the second side block 21, and a back pressure chamber 8 a is formed at the bottom. A plurality of the vane grooves 8 are formed at equal intervals in the circumferential direction, and in this example, the vane grooves 8 are formed so as to be parallel to each other at two places different in phase by 180 degrees, and a plane including the vane 4; It is formed in a state (offset state) that is parallel to the vane 4 and separated from the plane including the axis of the drive shaft 2 by a predetermined distance.

  The vane 4 is formed such that the width along the axial direction of the drive shaft 2 is equal to the axial length of the rotor 3, and the length in the insertion direction (sliding direction) into the vane groove 8 is the length of the vane groove 8. It is formed approximately equal to the length in the same direction. The vane 4 is protruded from the vane groove 8 by oil, which will be described later, supplied to the back pressure chamber 8 a of the vane groove 8, and a tip portion thereof can come into contact with the inner peripheral surface (cam surface 11) of the cylinder 12. Yes.

  Therefore, the compression space 30 is partitioned into a plurality of compression chambers 31 by the vanes 4 slidably inserted into the vane grooves 8, and the volume of each compression chamber 31 changes as the rotor 3 rotates. ing.

  The second housing member 20 has a suction port 26 for sucking working fluid (refrigerant gas) from the outside and a discharge port 27 for discharging the working fluid (refrigerant gas) to the outside. The second side block 21 has a suction port 26 and a suction port 26. A communicating suction chamber 28 is formed. In addition, the cylinder 12 of the first housing member 10 is located near the front side in the rotational direction of the rotor 3 with respect to a portion (radial seal portion 40) where the outer peripheral surface of the rotor 3 contacts the inner peripheral surface of the cylinder 12. A suction port 15 is formed in communication with the suction chamber 28 to suck fluid into the compression chamber 31.

  Furthermore, the first housing member 10 is provided with a discharge port 16 for discharging the fluid compressed in the compression chamber in the vicinity of the radial seal portion 40 on the rear side in the rotational direction of the rotor 3. In addition, a discharge chamber 17 that guides the fluid discharged through the discharge port 16 to the discharge port 27 is formed.

  An oil separator (not shown) is disposed between the discharge chamber 17 and the discharge port 27, and a lower portion of the first side block 13 of the first housing member 10 and a lower portion of the shell 22 of the second housing member 20. An oil chamber 18 for storing high-pressure oil separated from the fluid by the oil separator is provided between the two.

  Further, the first side block 13 has a surface facing the end surface of the rotor 3, and the drive shaft 2 is extended in the circumferential direction with the opening peripheral edge of the bearing hole 13 a inserted through the bearing 14 being recessed. 1 oil introduction groove 41 is formed. The first oil introduction groove 41 is formed over a predetermined angular range (an angular range of about 270 degrees) from the angular position where the radial seal portion 40 is provided to the front side from the angular position where the discharge port 16 is provided, When the oil chamber 18 is connected to the oil chamber 18 via an oil communication passage 19 having a throttle portion, and the angle range from the position where the tip of the vane 4 reaches the suction port 15 to the position immediately before the discharge port 16 is reached. It communicates with the bottom (back pressure chamber 8a) of the vane groove 8.

  Therefore, when the discharge pressure increases, the high-pressure oil stored in the oil chamber 18 is supplied to the first oil introduction groove 41 formed in the first side block 13 via the oil communication path 19, and this first 1 is introduced into the space 45 formed between the sliding portion of the bearing 14 and the like and the end portion of the drive shaft 2 and the first side block 13, and into the back pressure chamber 8 a of the rotor 3. It is supposed to be sent. The vane 4 is pressed against the inner peripheral surface (cam surface 11) of the cylinder 12 by the oil fed into the back pressure chamber 8a, so that stable compression is ensured.

  Further, the surface of the second side block 21 that faces the end surface of the rotor 3 is provided with a second extending in the circumferential direction with the opening periphery of the bearing hole 21a into which the drive shaft 2 is inserted via the bearing 24 being recessed. Two oil introduction grooves 42 are formed. The second oil introduction groove 42 is formed over a predetermined angle range (an angle range of about 270 degrees) from the angular position where the radial seal portion 40 is provided to the front side from the angular position where the discharge port 16 is provided, The vane 4 communicates with the bottom portion (back pressure chamber 8a) of the vane groove 8 when the tip end portion of the vane 4 is in an angular range from a position at which the tip of the vane 4 reaches the suction port 15 to immediately before it reaches the discharge port 16.

Accordingly, the oil fed into the back pressure chamber 8a is supplied to the second oil introduction groove 42 in a process in which the back pressure chamber 8a communicates with the second oil introduction groove 42, and the second oil introduction groove 42 is supplied. It is sent to sliding parts, such as a bearing, via.
In FIG. 2, reference numeral 37 denotes a screw hole into which the connector 6 is screwed.

  In such a configuration, the suction pressure introduction groove into which a fluid corresponding to the suction pressure is introduced, as shown in FIG. 2A, on the surface of the first side block 13 that faces the end surface of the rotor 3. 43 is formed, and the first oil introduction groove 41 is formed with a groove reducing portion 41a in which a part of the portion where the vane groove 8 can be opened is reduced inward in the radial direction of the rotor.

  The suction pressure introduction groove 43 is located between the drive shaft 2 and the cam surface 11, more specifically, between the outer edge of the first oil introduction groove 41 and the cam surface 11, and the inner peripheral surface of the cylinder 12. Along the (cam surface), an angle range corresponding to the suction port 15 is provided.

  In this example, since the suction port 15 is formed over a range of approximately 90 degrees along the cam surface from the vicinity of the radial seal portion 40, the suction pressure introducing groove 43 also has an outer peripheral edge portion on the end surface of the rotor 3. It is formed over a range of approximately 90 degrees along the cam surface 11 from the vicinity of the opposed radial seal portion 40. Moreover, the suction pressure introduction groove 43 is formed so as to gradually widen from the vicinity of the radial seal portion 40, and as shown by the hatched portion of the suction pressure introduction groove in FIG. It is formed so as to be opposed to the outer peripheral edge portion with a substantially equal width.

  Accordingly, the portion of the suction pressure introduction groove 43 indicated by the hatch does not exceed the pressure corresponding to the suction pressure. Therefore, the second portion that acts on the rotor 3 by the amount indicated by the hatch is equivalent to the area indicated by the hatch. The biasing force toward the side block 21 will be reduced.

  Next, the groove reducing portion 41a is formed in a range between the drive shaft 2 and the position where the outer peripheral edge of the rotor 3 faces on the surface facing the end surface of the rotor 3 of the first side block 13, In the driving state of the vane compressor, as shown in FIG. 4B, the pressure in the compression chamber 31 is provided in an angle range corresponding to a region where the pressure is equal to or lower than the pressure in the oil introduction groove 41.

  In this example, the groove reducing portion 41a is formed over the entire range of about 180 degrees in the rotor rotation angle from the vicinity of the radial seal portion 40 in a region where the pressure of the compression chamber 31 is equal to or lower than the pressure of the oil introduction groove. Further, it is formed so as to gradually become wider from the vicinity of the radial seal portion 40, and the area facing the rotor 3 is smaller than the conventional oil introduction groove shown in FIG.

  As described above, the groove reducing portion 41a is provided by providing the groove reducing portion 41a in the region where the pressure of the compression chamber 31 is equal to or lower than the pressure of the oil introduction groove (the region of the suction stroke and the initial region of the compression stroke). Assuming that the influence of the suction pressure introduction groove 43 does not consider the change in the radial pressure in the portion, as shown in FIG. 4 (a), the groove width is narrowed compared to the conventional oil introduction groove. Accordingly, the pressure gradient from the outer diameter of the rotor 3 to the first oil introduction groove 41 becomes gentle, and the force acting on the rotor end surface (the urging force acting on the second side block 21 acting on the rotor 3) is reduced. Will be.

  Further, on the surface of the second side block 13 that faces the end surface of the rotor 3, as shown in FIG. 2B, the second oil introduction groove 42 has a bottom portion of the vane groove (back pressure chamber 8a). A groove enlarging portion 42 a is formed by enlarging a part of the portion that can be opened outward in the radial direction of the rotor 3.

  The groove enlarged portion 42a is formed between the drive shaft 2 and the position where the outer peripheral edge of the rotor 3 faces on the surface of the second side block 13 that faces the end surface of the rotor 3. In the driving state, as shown in FIG. 4B, the compression chamber is provided within an angle range corresponding to a region where the pressure in the compression chamber is equal to or lower than the pressure in the oil introduction groove.

  In this example, the groove expanding portion 42a extends from the vicinity of the radial seal portion 40 over the entire range of about 180 degrees in terms of the rotor rotation angle in which the pressure in the compression chamber 31 is a region equal to or lower than the pressure in the second oil introduction groove 42. In addition, the width is gradually narrowed from the vicinity of the radial seal portion 40.

  As described above, the groove expansion portion 42a is provided by providing the groove expansion portion 42a in the region where the pressure in the compression chamber 31 is equal to or lower than the pressure of the oil introduction groove 42 (the suction stroke region and the initial region of the compression stroke). As shown in FIG. 4 (a), the radial pressure transition at the part where the oil acts on the end surface of the rotor 3 is increased by the width of the groove compared to the conventional oil introduction groove. Increases, the pressure gradient from the outer diameter of the rotor 3 to the second oil introduction groove 42 becomes steep, and the force acting on the rotor end surface (the biasing force of the rotor 3 toward the first side block 13) increases. Will do.

  Therefore, in the case where the electromagnetic clutch 33 is provided, the position of the rotor 3 in the axial direction is different from the pressure difference acting on both the front and rear sides of the drive shaft 2 when the electromagnetic clutch 33 to which power is transmitted to the drive shaft 2 is attracted. The spring force of the plate spring 34 of the electromagnetic clutch 33, the effect of reducing the urging force to the second side block acting on the rotor by the suction pressure introduction groove 43, and the second acting on the rotor by the groove reducing portion 41a. The position where the effect of reducing the urging force toward the side block and the effect of increasing the urging force toward the first side block acting on the rotor by the groove expanding portion 42a are balanced.

  The force acting on the rotor by the suction pressure introducing groove 43, the force acting on the rotor by the groove reducing portion 41a, and the force acting on the rotor 3 by the groove expanding portion 42a are all the second side block that acts on the rotor 3. The force acting in the direction of weakening the urging force toward the 21 side is caused, and by these forces, a pressure difference is produced between the front and rear of the rotor 3 in the axial direction, and thereby the force acting on the front and rear of the rotor and the drive shaft integrated therewith is generated. It is possible to balance (reduce the urging force toward the second side block 21) and keep the distribution of the clearance in the axial direction of the rotor in an appropriate state.

  In the above-described example, the configuration in which the suction pressure introducing groove 43, the groove reducing portion 41a, and the groove expanding portion 42a are formed at the same time is shown, but even if any one of them is used, Even if any two of them are used in combination, it is possible to contribute to adjustment of clearance distribution in the axial direction of the rotor by reducing the urging force toward the second side block 21 acting on the rotor 3. It becomes.

  In the above example, the example in which the groove reducing portion 41a is provided over the entire range of the rotor rotation angle range of approximately 180 degrees, in which the pressure of the compression chamber 31 is equal to or lower than the pressure of the oil introduction groove 41, is shown. If the pressure in the compression chamber 31 is within the range of the region where the pressure is less than or equal to the pressure of the oil introduction groove 41, the second side block side acting on the rotor 3 is adjusted by adjusting the formation position and formation range of the groove reduction portion 41a. It becomes possible to reduce the urging force to.

  Similarly, in the above-described example, the example in which the groove expansion portion 42a is provided over the entire range of the rotor rotation angle range of approximately 180 degrees where the pressure in the compression chamber 31 is equal to or less than the pressure of the oil introduction groove 42 is shown. If the pressure in the compression chamber 31 is within the range of the region where the pressure in the oil introduction groove 42 is lower, the first side block acting on the rotor 3 is adjusted by adjusting the formation position and formation range of the groove expansion portion 42a. It is possible to increase the urging force toward the 13 side.

  Further, in the above configuration, the compressor in the case where there are two vanes 4 has been described. However, a similar configuration can be adopted in three or more vane compressors, and two Also in the configuration of the vane, the example in which the vane groove 8 (vane 4) is provided offset is shown in the above example. However, the plane including the vane 4 and the axis of the drive shaft 2 are parallel to the vane 4. The same distribution is adopted to adjust the clearance distribution before and after the rotor 3 in the axial direction even in the case of matching with the plane including the offset (set the offset to 0) or offset to the opposite side. Also good.

Reference Signs List 1 vane compressor 2 drive shaft 3 rotor 4 vane 5 housing 8 vane groove 8a back pressure chamber 10 first housing member 11 cam surface 12 cylinder 13 first side block 15 suction port 16 discharge port 17 discharge chamber 18 oil chamber DESCRIPTION OF SYMBOLS 19 Oil communication path 20 2nd housing member 21 2nd side block 31 Compression chamber 41 1st oil introduction groove 41a Groove reduction part 42 2nd oil introduction groove 42a Groove expansion part 43 Suction pressure introduction groove

Claims (6)

A housing, a cam surface is formed, the cylinder provided in the housing, the both ends of the cylinder in the axial direction are closed, the pair of side blocks provided in the housing, and the pair of side blocks are rotatable. A drive shaft supported by the rotor, a rotor fixed to the drive shaft and rotatably accommodated in the cylinder, a plurality of vane grooves formed in the rotor, and a slidably inserted into the vane groove And a compression chamber formed by the rotor and the vane in a space closed by the plurality of vanes whose tips protrude from the vane grooves and slide on the cam surface, the cylinder, and the pair of side blocks. A suction port provided for sucking fluid into the compression chamber, a discharge port provided for discharging fluid compressed in the compression chamber, and the fluid An oil discharge groove, an oil chamber storing oil pressurized by the discharged fluid, and an oil introduction groove provided on a surface of the pair of side blocks facing the rotor and opening the vane groove And a vane type compressor comprising: at least one oil communication path communicating the oil chamber and the oil introduction groove;
A suction pressure introduction groove that is provided on a surface of the one side block of the pair of side blocks facing the rotor and into which the fluid corresponding to the suction pressure is introduced;
A groove reducing portion provided on a surface of the one side block facing the rotor, wherein a part of the oil introduction groove that allows the vane groove to be opened is reduced inward in the radial direction of the rotor;
A part of the other side block of the pair of side blocks that is provided on the surface facing the rotor and that allows the opening of the vane groove of the oil introduction groove is expanded radially outward of the rotor. An enlarged groove part,
A vane type compressor having at least one of the following.   2. The vane compressor according to claim 1, wherein the drive shaft passes through the other side block and protrudes to the outside of the housing.   The suction pressure introducing groove is provided in the one side block between the drive shaft and the cam surface, and is provided over an angular range corresponding to the suction port. The vane type compressor according to 1 or 2.   The groove reducing portion is configured such that, in the driving state of the vane compressor, the pressure in the compression chamber is in a range between the drive shaft and a position where the outer peripheral edge of the rotor faces the one side block. The vane type compressor according to claim 1 or 2, wherein the vane type compressor is provided within an angle range corresponding to a region that is equal to or lower than a pressure of the oil introduction groove.   The groove enlarging portion is configured such that the pressure in the compression chamber is in the drive state of the vane compressor in a range between the drive shaft and a position where the outer peripheral edge of the rotor faces the other side block. The vane type compressor according to claim 1 or 2, wherein the vane type compressor is provided within an angle range corresponding to a region that is equal to or lower than a pressure of the oil introduction groove. The housing includes a first housing member formed integrally with the cylinder having an inner peripheral surface formed into a perfect circle, and a first side block that closes one end of the cylinder in the axial direction, and the cylinder. A second housing member formed with a second side block for closing the other end side in the axial direction.
6. The vane compressor according to claim 1, wherein the pair of side blocks are the first side block and the second side block.

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