JP2014181598A - Vane type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vane type compressor capable of eliminating the need of positioning a guide mechanism for regulating movement of a vane to an insertion direction into a vane groove in installment, capable of accurately forming the guide mechanism, accurately and easily forming a clearance between the vane and the guide mechanism, so as to reduce chattering noise caused by the vane.SOLUTION: In a vane type compressor 1, a housing 9 is constituted by combining a first housing member 10 having a cylinder forming part 12 whose inner peripheral surface is formed into a true circle and a first side block forming part 13 for closing one end side thereof, and a second housing member 20 having a second side block forming part 21 for closing the other end side of the cylinder forming part 12. A guide mechanism 35 for regulating movement of a vane 4 to an insertion direction into a vane groove 5 is provided in the first side block forming part 13 in a concentric manner with the inner peripheral surface of the cylinder forming part 12. The vane groove 5 may be formed from an outer peripheral surface of a rotor 3 to a center of a driving shaft 2.

Description

  The present invention relates to a vane type compressor, and more particularly to a vane type compressor having a structure useful for reducing noise (chattering noise) associated with vane vibration that occurs during startup.

  When the vane compressor is started, sufficient back pressure is not applied to the vane, and the pressure of the fluid compressed in the compression chamber on the front side in the rotation direction of the vane acts on the protruding end of the vane. Coupled with the vane's sudden output is not sufficient. For this reason, the vane vibrates in the sliding direction in the vane groove of the rotor, and this vibration causes the inconvenience that the vane collides with the inner peripheral surface of the cylinder and generates abnormal noise (chattering noise).

  Therefore, conventionally, in order to reduce such chattering noise, as shown in Patent Document 1 (Japanese Patent Laid-Open No. 2005-320916), a convex portion that protrudes into the recessed portion of the rotor on the rotor contact surface of the rear side block. And the vane side end of the vane is vaned on the outer peripheral surface of the convex portion so that the locus drawn by the protruding end of the vane along the rotation of the rotor follows the contour shape of the inner peripheral surface of the cylinder. Instead of pressing the vane against the inner peripheral surface of the cylinder only by hydraulic back pressure, the vane is formed in the direction of the inner peripheral surface of the cylinder by the convex portion formed on the side block. There has been proposed a configuration in which the vane is forced to protrude by being pressed.

  Further, as shown in Patent Document 2 (Japanese Utility Model Publication No. 57-152482), the rotor is eccentrically accommodated in a cylindrical cylinder, and is fitted slidably in the radial direction of the rotor so that the rotor rotates. In addition, in a vane type pump having a vane that rotates while sliding in contact with the inner peripheral surface of the cylinder, a ring-shaped protrusion concentric with the cylinder is provided on a bracket attached to the opening end of the cylinder so that the rotor rotates at a low speed and acts on the vane. A configuration in which the vane is forcibly pushed up in the radial direction of the rotor when the force is small and is brought into sliding contact with the inner periphery of the cylinder is also known.

JP-A-2005-320916 Japanese Utility Model Publication No. 57-152482

  By the way, when providing the guide mechanism which controls the motion of a vane, it is necessary to form the clearance between a vane and a guide mechanism appropriately. If the clearance is too small, the movement of the vane is deteriorated, and if it is too large, chattering noise cannot be sufficiently reduced.

  However, in the above-described configuration, the guide mechanism that restricts the movement of the vane (the convex portion of Patent Document 1 and the ring-shaped protrusion of Patent Document 2) is a separate member (the side block of Patent Document 1 and Patent Document 1). 2), the clearance between the vane and the guide mechanism cannot be reduced sufficiently unless the assembly accuracy between the cylinder and the separate member provided with the guide mechanism is strictly controlled. Generation of chattering noise cannot be sufficiently reduced.

  Further, the guide mechanism needs to have a shape close to the cross-sectional shape of the inner peripheral surface of the cylinder on which the vane slides so that the clearance between the vane and the guide mechanism does not change greatly due to the rotation angle of the rotor. In the former configuration, since the outer peripheral surface of the convex portion constituting the guide mechanism is formed in an elliptical shape in accordance with the contour shape of the inner peripheral surface of the cylinder, it is very difficult to form the guide mechanism with high accuracy. Met.

  The present invention has been made in view of such circumstances, and it is not necessary to align the guide mechanism at the time of assembly, and the clearance between the vane and the guide mechanism can be increased so that the guide mechanism can be formed with high accuracy. The main object is to provide a vane type compressor that can be easily formed with high accuracy and can reduce chattering noise due to vanes.

  In order to achieve the above object, a vane compressor according to the present invention includes a cylinder forming portion having an inner peripheral surface formed in a perfect circle, and a first end that closes one end side in the axial direction of the cylinder forming portion. A first housing member in which a side block forming portion is integrally formed and a second housing member in which a second side block forming portion for closing the other end side in the axial direction of the cylinder forming portion is combined. And a drive shaft that is rotatably supported by the first side block forming portion and the second side block forming portion, and is fixed to the drive shaft and is rotatable in the cylinder forming portion. A rotor housed in the rotor, a plurality of vane grooves provided in the rotor, and a vane that is slidably inserted into the vane groove, the cylinder forming portion and the first side block forming portion, In the vane type compressor in which a plurality of compression chambers are formed by the rotor and the vane in a space closed by the second side block forming part, the first side block forming part includes the vane A guide mechanism for restricting movement in the insertion direction into the vane groove is integrally provided, and this guide mechanism is formed concentrically with the inner peripheral surface of the cylinder forming portion and the outer peripheral surface is formed into a perfect circle. It is said.

  Therefore, since the guide mechanism for restricting the movement of the vane is formed integrally with the first side block forming portion that is integrated with the cylinder forming portion, it is not necessary to align the guide mechanism when the compressor is assembled. Since the guide mechanism is formed concentrically with the cylinder forming portion whose inner peripheral surface is formed in a perfect circle, the guide mechanism can be formed with high accuracy. For this reason, the clearance between the assembled vane and the guide mechanism is easily formed with high accuracy, and chattering noise due to the vane can be reduced.

  Here, the guide mechanism may be configured by an annular convex portion protruding from the first side block forming portion into the cylinder forming portion.

The vane groove is preferably formed from an outer peripheral surface of the rotor toward an axis center of the drive shaft.
If the plane that includes the vane and the plane that is parallel to the vane and that includes the axis of the drive shaft do not match (when the vane groove is offset), the guide mechanism is concentric with the inner peripheral surface of the cylinder forming portion. In this case, since the distance (clearance) between the vane and the guide mechanism varies greatly depending on the rotation angle of the rotor, the function of guiding the vane of the guide mechanism becomes insufficient. And the plane parallel to the vane and including the axis of the drive shaft (by making the offset zero), it becomes possible to geometrically reduce the distance (clearance) between the vane and the guide mechanism. Chattering noise can be reduced.

Further, the tip end portion of the vane that is in sliding contact with the inner peripheral surface of the cylinder forming portion described above is located at the front side portion in the moving direction of the vane due to the rotation of the rotor from the center position in the thickness direction of the vane. It is preferable that the vane protrudes most in the sliding direction of the vane groove.
Since chattering is likely to occur at a position where the pressure applied to the tip of the vane is increased, the chattering is most prominent at the front end of the vane in the rotational direction of the vane from the center position in the thickness direction of the vane. By doing so, it is possible to reduce the inconvenience that the vane is pushed back by reducing the area receiving the compression chamber pressure on the front side where the pressure increases first, and to reduce chattering noise.

Further, the end of the vane on the guide mechanism side slides on the vane groove at the rear side portion in the moving direction of the vane due to the rotation of the rotor from the center position in the thickness direction of the vane. It is good also as a structure which protrudes most in the direction to do.
An area where chattering is likely to occur (by the vicinity of the discharge port) by causing the end of the vane on the guide mechanism side to protrude most from the center position in the thickness direction of the vane at the rear side in the rotor rotation direction. ), The clearance between the vane and the guide mechanism can be further reduced geometrically, and chattering noise can be reduced.

The above guide mechanism is characterized in that it is provided in the first side block forming portion formed integrally with the cylinder forming portion. On the premise of such a configuration, the same guide mechanism is used as the second side block. It may be provided also in the forming part.
According to such a configuration, the vane can be supported at both ends by the guide mechanism formed in the first side block forming portion and the guide mechanism formed in the second side block forming portion. It becomes possible to prevent catching or the like due to the tilting of the vane.

The guide mechanism may be provided with a chipped portion that allows the vane to move in the insertion direction into the vane groove in the vicinity where the amount of protrusion of the vane from the vane groove is the largest.
If the movement of the vane is restricted by the provision of the guide mechanism, the vane and rotor are overloaded during liquid compression, so the vane that does not require strict clearance between the vane and the guide mechanism is the most from the vane groove of the rotor. It is desirable to avoid overload due to liquid compression by canceling the guide function by the guide mechanism in the vicinity of the protrusion. For this reason, with such a configuration, it is possible to prevent an excessive load from being applied to the vane or the rotor even when the liquid medium flows into the compression chamber.

  As described above, according to the present invention, the cylinder forming portion whose peripheral surface is formed in a perfect circle and the first side block forming portion that closes one end side in the axial direction are integrally formed. The guide member that restricts the movement of the vane in the insertion direction into the vane groove concentrically with the inner peripheral surface of the cylinder forming portion is integrally provided in the housing member of the cylinder so that the movement of the vane is restricted when the compressor is assembled. Positioning of the guide mechanism is unnecessary, and the guide mechanism is formed concentrically with the inner peripheral surface of the cylinder forming portion, so that the guide mechanism can be formed with high accuracy. For this reason, the clearance between the vane and the guide mechanism is easily formed with high accuracy, and chattering noise due to the vane can be reduced.

  And on the premise of the above configuration, in order to further reduce the clearance between the vane and the guide mechanism, any one of the following configurations or a combination thereof may be used.

  First, a vane groove is formed from the outer peripheral surface of the rotor toward the axis center of the drive shaft, and a plane including the vane is aligned with a plane parallel to the vane and including the axis of the drive shaft (set to offset 0). By adopting such a configuration, even when the guide mechanism is formed concentrically with the inner peripheral surface of the cylinder forming portion, the distance (clearance) between the vane and the guide mechanism varies greatly depending on the rotation angle of the rotor. This can be avoided and chattering noise can be further reduced.

  Further, the vane slides on the vane groove at the front portion of the vane in the moving direction by the rotation of the rotor from the center position in the thickness direction of the vane with respect to the tip end portion of the vane that is in sliding contact with the inner peripheral surface of the cylinder forming portion. The most protruding in the direction. By adopting such a configuration, it is possible to reduce the area receiving the compression chamber pressure on the front side where the pressure first increases, and to suppress the inconvenience that the vane is pushed back, thereby suppressing chattering and reducing chattering noise. It becomes possible to reduce.

  Further, at the end of the vane on the guide mechanism side, the vane protrudes most in the direction in which the vane slides in the vane groove at the rear side portion in the moving direction of the vane due to the rotation of the rotor from the center position in the thickness direction of the vane. . With such a configuration, the clearance between the vane and the guide mechanism in a region where chattering is likely to occur (near the discharge port) can be reduced, and chattering noise can be reduced.

  The above configuration shows an example in which the guide mechanism is integrally provided in the first housing member in which the cylinder forming portion and the first side block forming portion are integrally formed. The guide mechanism may be provided also in the second side block forming portion, and by adopting such a configuration, the guide mechanism formed in the first side block forming portion and the second side block forming. It is possible to support from both sides by the guide mechanism formed in the section, and it is possible to prevent catching or the like due to the tilting of the vane.

  Further, by providing the guide mechanism with a chipped portion that allows movement of the vane in the insertion direction into the vane groove in the vicinity where the amount of protrusion of the vane from the vane groove becomes the largest, the liquid medium is contained in the contracted chamber. Even when it flows in, it is possible to prevent an excessive load from being applied to the vane or the rotor.

FIG. 1A is a cross-sectional view showing the overall configuration of a vane compressor according to the present invention, and FIG. 1B is a rotor attached to a drive shaft used in the vane compressor of FIG. FIG. 1C is a perspective view showing a first housing member of the vane type compressor according to the present invention. FIG. 2 is a view showing the relationship between the vane and the guide mechanism accompanying the rotation of the rotor of the vane type compressor shown in FIG. FIG. 3 is a diagram showing the relationship between the vane provided in the rotor and the guide mechanism when the vane offset is zero, and (a) shows the state in which the vane enters the vane groove most and the most from the vane groove. The figure which shows the state which protruded, (b) is a figure which shows the motion of the vane accompanying rotation of a rotor. FIG. 4A is a diagram for explaining an example of the shape of the tip of the vane when the vane offset is zero, and FIG. 4B is a vane when the vane of FIG. 4A is used. It is a figure explaining the relationship between a guide mechanism. FIG. 5A is a diagram for explaining an example of the shape of the base end portion of the vane when the vane offset is zero, and FIG. 5B is a diagram when the vane of FIG. 5A is used. It is a figure explaining the relationship between a vane and a guide mechanism. FIG. 6A is a cross-sectional view showing another configuration example of the vane type compressor according to the present invention, and FIG. 6B is a cylinder forming portion as seen from the line AA in FIG. FIG. 6C is a view showing the guide mechanism formed in the second side block forming portion, and FIG. 6C is a view showing the cylinder forming portion and the first side block forming portion as seen from the line BB in FIG. It is a figure which shows the guide mechanism formed in this. FIG. 7 is an explanatory diagram illustrating an example in which a notch is provided in a part of the guide mechanism.

  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 9 that supports the rotor 3 and the vanes 4 while supporting them freely is configured. In FIG. 1A, the left side is the front side and the right side is the rear side.

  The housing 9 is configured by combining two members of a first housing member 10 and a second housing member 20, and the first housing member 10 has a cylinder hole 11 for housing the rotor 3. And a first side block forming portion 13 integrally formed so as to close one end side (rear side) in the axial direction of the cylinder forming portion 12. The cylinder hole 11 formed in the cylinder forming part 12 is formed in a perfect circle in cross section (the cylinder forming part 12 is formed in a perfect circle in the inner peripheral surface), and the axial length of the rotor 4 is described later. It is formed equal to the length in the direction.

  The second housing member 20 includes a second side block forming portion 21 that is in contact with an end face on the other end side (front side) in the axial direction of the cylinder forming portion 12 and closes the other end side. A shell forming portion formed integrally with the side block forming portion 21 and extending in the axial direction of the drive shaft 2 so as to surround the outer peripheral surfaces of the cylinder forming portion 12 and the first side block forming portion 13. 22.

  The first housing member 10 and the second housing member 20 are fastened in the axial direction via a connector 8 such as a bolt, and the first side block forming portion 13 of the first housing member 10 A seal member such as an O-ring (not shown) is interposed between the second housing member 20 and the shell forming portion 22 so as to be airtightly sealed.

  Further, the second housing member 20 is integrally formed with a boss portion 23 extending from the second side block forming portion 21 to the front side. A pulley (not shown) that transmits rotational power to the drive shaft 2 is rotatably mounted on the boss portion 23 so that the rotational power is transmitted from the pulley to the drive shaft 2 via an electromagnetic clutch (not shown). It has become.

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

  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. As shown in FIG. 2, the axial center O ′ of the cylinder forming portion 12 and the axial center O of the rotor 3 (drive shaft 2) are the outer peripheral surface of the rotor 3 and the inner peripheral surface 12 a of the cylinder forming portion 12. Are provided so as to be brought into contact with each other at one place in the circumferential direction (offset by a half of the difference between the inner diameter of the cylinder forming portion 12 and the outer diameter of the rotor 3). In the space closed by the cylinder forming portion 12, the first side block forming portion 13 and the second side block forming portion 21, the inner peripheral surface 12 a of the cylinder forming portion 12 and the outer peripheral surface of the rotor 3 are A compression space 30 is defined between them.

  Although not shown, the second housing member 20 is formed with a suction port for sucking working fluid (refrigerant gas) from the outside and a discharge port for discharging the working fluid (refrigerant gas) to form the cylinder of the first housing member 10. In the portion 12, a suction port 15 communicating with the suction port is formed near the front side in the rotation direction of the rotor 3 with respect to a portion where the outer peripheral surface of the rotor 3 contacts the inner peripheral surface 12 a of the cylinder forming portion 12. Further, a discharge port 16 communicating with the discharge port is formed in the vicinity of the rear side in the rotational direction of the rotor 3.

  A plurality of vane grooves 5 are formed on the outer peripheral surface of the rotor 3, and the vanes 4 are slidably inserted into the respective vane grooves 5. The vane groove 5 is opened not only on the outer peripheral surface of the rotor but also on the end surface facing the first side block forming portion 13 and the second side block forming portion 21, and a back pressure chamber 5 a is formed at the bottom. ing. A plurality of the vane grooves 5 are formed at equal intervals in the circumferential direction. In this example, the vane grooves 5 are formed at two places different in phase by 180 degrees, and are parallel to the plane including the vane 4 and the vane 4. The drive shaft 2 is formed in a state (offset α state) separated from the plane including the axis O by a predetermined distance α.

  Further, on the rear and front end surfaces of the rotor 3, a recess 3 b having a circular cross section formed concentrically around an insertion hole 3 a through which the drive shaft 2 is inserted is formed.

  The vane 4 is formed such that the width along the axial direction of the drive shaft 2 is equal to the axial width of the rotor 3, and the length in the insertion direction (sliding direction) into the vane groove 5 is the same direction as the vane groove 5. It is formed approximately equal to the length of. The vane 4 is protruded from the vane groove 5 due to the back pressure supplied to the back pressure chamber 5 a of the vane groove 5, and the tip portion thereof can come into contact with the inner peripheral surface 12 a of the cylinder forming portion 12.

  Therefore, the compression space 30 is partitioned into a plurality of compression chambers 31 by the vanes 4 slidably inserted into the vane grooves 5, and the volume of each compression chamber 31 changes as the rotor 3 rotates. ing. Moreover, since the length along the axial direction of the drive shaft 2 of each vane 4 is formed equal to the axial direction width of the rotor 3, the front side of the base end portion (embedded side end portion) of the vane 4 A side edge portion with the rear side is exposed in a recessed portion 3 b formed on the end surface of the rotor 3.

  The movement of the vane 4 in the insertion direction into the vane groove 5 is restricted on the surface of the first side block forming portion 13 facing the end surface of the rotor 3 concentrically with the inner peripheral surface of the cylinder forming portion 12. A guide mechanism 35 is integrally formed. The guide mechanism 35 protrudes from the first side block forming portion 13 into the cylinder forming portion 12 and has an annular outer peripheral surface (perfect outer peripheral surface) concentric with the inner peripheral surface of the cylinder forming portion 12. It is comprised by the convex part, is accommodated in the recessed part 3b formed in the end surface of the said rotor 3, and the part of the base end part (embedding side edge part) exposed to the recessed part 3b of the vane 4 is an outer peripheral surface. It comes to contact.

  An oil separator (not shown) is disposed between the discharge port 16 and the discharge port, and the oil separated from the working fluid by the oil separator is the first housing member 10 and the second housing member. 20 is temporarily stored in an oil reservoir chamber 17 formed between the two. During steady operation when the discharge pressure becomes high, high-pressure refrigerant gas or high-pressure oil is sent from the oil reservoir chamber 17 to the back pressure chamber 5a through the high-pressure introduction passage 18, whereby the vane 4 is connected to the cylinder forming portion 12. Is stably pressed against the inner peripheral surface 12a, and stable compression is ensured.

  Therefore, in the above configuration, at the initial stage of startup when sufficient back pressure cannot be obtained, the pressure of the fluid compressed in the compression chamber on the front side in the rotation direction of the vane acts on the tip of the vane on the protruding side. However, the vane is pressed in the direction of the inner peripheral surface 12a of the cylinder forming portion 12 by the guide mechanism 35 formed in the first side block forming portion 13. Since the vane is forced to protrude, it can be brought into sliding contact with the inner peripheral surface 12a of the cylinder forming portion 12, or even if it is separated from the inner peripheral surface 12a, it is only slightly separated, and chattering noise is reduced. It becomes possible to reduce.

  In particular, in the above-described configuration, the guide mechanism 35 that regulates the movement of the vane 4 is integrally formed with the first side block forming portion 13 that is integrated with the cylinder forming portion 12, so that when the compressor is assembled, Positioning of the guide mechanism 35 becomes unnecessary, and the guide mechanism 35 is formed concentrically with the inner peripheral surface of the cylinder forming portion 12 and the outer peripheral surface is formed in a perfect circle. Since the clearance between the vane and the guide mechanism can be easily formed with high accuracy, chattering noise due to the vane can be reduced. Moreover, since the guide mechanism 35 is formed integrally with the side block forming portion 13 and concentrically with the inner peripheral surface of the cylinder forming portion, the guide mechanism 35 is formed simultaneously with the processing of the cylinder forming portion 12 or of the cylinder forming portion 12. Processing can be performed continuously with processing, and formation can be easily performed.

  FIG. 3 shows another configuration example described above. In the configuration described above, the inner peripheral surface of the cylinder forming portion 12 is formed into a perfect circle, and the guide mechanism 35 is integrally formed with the first side block forming portion 13 concentrically with the inner peripheral surface of the cylinder forming portion 12. Thus, the chattering noise is reduced, but the axis center O ′ of the guide mechanism 35 (cylinder forming portion 12) and the axis center O of the rotor 3 (drive shaft 2) are shifted. The clear lath between the base end portion (buried side end portion) of the vane 4 and the guide mechanism 35 is not constant, and changes occur while the vane 4 rotates once.

Since the change in the clearance becomes large when the vane 4 (vane groove 5) is provided offset, in this example, the plane including the vane 4 is parallel to the vane 4 and the drive shaft 2 The plane including the axis O is made coincident (offset to 0). That is, the vane grooves 5 are formed radially from the outer peripheral surface of the rotor 3 toward the axis center O of the drive shaft 2, and in particular, when there are two vane grooves 5, the two vane grooves 5 have both vane grooves. The surface to be included is formed on the opposite side of the axis (180 degrees out of phase) so as to include the axis O of the drive shaft 2.
In addition, since another structure is the same as that of the said structural example, it attaches | subjects the same code | symbol to the same location, and abbreviate | omits description.

  According to such a configuration, since the offset of the vane 4 (vane groove 5) is zero, the clearance between the base end (buried side end) of the vane 4 and the guide mechanism is geometrically reduced. And chattering noise can be further reduced.

In the above configuration, in order to reduce the clearance between the base end (buried side end) of the vane 4 and the guide mechanism, an optimum layout of the vane is proposed for the guide mechanism. Alternatively, on the premise of the configuration of FIG. 3, the clearance between the base end (embedded side end) of the vane 4 and the guide mechanism may be further reduced by improving the shape of the vane itself.
For example, as shown in FIG. 4, the vane 4 slides in the vane groove 5 at the front position: γ in the moving direction of the vane 4 by the rotation of the rotor 3 from the center position: β in the thickness direction of the vane 4. It is good also as a shape which protrudes on the outermost side in the direction to do.

  With such a configuration, in the vicinity of the discharge port 16 where chattering is likely to occur, the contact portion between the tip end portion of the vane 4 and the inner peripheral surface 12a of the cylinder forming portion 12 is the center in the thickness direction of the vane 4. Since the position is β from the front side in the rotational direction of the rotor 3, the clearance between the vane 4 and the guide mechanism 35 can be reduced, and the compression chamber 31 on the front side where the pressure increases first. Since the area of the tip of the vane 4 that receives pressure can be reduced, the force with which the vane 4 is pushed back can be reduced, and chattering noise can be reduced.

  Further, as shown in FIG. 5, the end of the vane 4 on the guide mechanism 35 side is located at the rear side in the moving direction of the vane 4 due to the rotation of the rotor from the center position β in the thickness direction of the vane 4: In δ, the vane 4 may have a shape protruding inward in the direction in which the vane 4 slides in the vane groove 5. Such a shape on the guide mechanism side of the vane 4 may be formed at least at both ends where the vane 4 contacts the guide mechanism 35, but may be formed over the entire width of the vane 4.

  With this configuration, the clearance between the vane 4 and the guide mechanism 35 can be further reduced in the vicinity of the discharge port 16 where chattering is likely to occur, and chattering noise can be further reduced. It becomes possible.

  In the above configuration, the configuration example in which the guide mechanism 35 is integrally formed with the first side block forming portion 13 configuring the first housing member 10 has been described. Since the housing member of FIG. 6 is assembled with high accuracy by matching the axial center, the guide mechanism 36 having the same shape as the above-described guide mechanism 35 is replaced by the second housing member 20 as shown in FIG. The side block forming portion 21 may be integrally formed.

  By adopting such a configuration, the vane 4 is formed by the guide mechanism 35 formed in the first side block forming portion 13 and the guide mechanism 36 formed in the second side block forming portion 21. Since movement in the insertion direction into the groove 5 can be restricted on both sides of the vane 4, it is possible to prevent catching or the like due to the inclination of the vane 4.

  Moreover, although the above guide mechanisms 35 and 36 showed the example comprised by the annular convex part which has the outer peripheral surface formed concentrically with the inner peripheral surface of the cylinder formation part 12, as FIG. 7 shows, The vane 4 is located on the cylinder forming portion 12 near a place where a strict clearance between the vane 4 and the guide mechanism 35 is not required, that is, a place where the amount of protrusion of the vane 4 from the vane groove 5 is maximized by the guide mechanisms 35 and 36. You may make it provide the chip | tip part 35a which leaves | separates from the internal peripheral surface 12a, and accept | permits the movement to the insertion direction to the vane groove | channel 5.

By providing such a chipped portion 35a, the guide function by the guide mechanism 35 is canceled in the vicinity where the vane 4 protrudes most, so that the liquid refrigerant escapes from the gap between the vane 4 and the inner peripheral surface 12a during liquid compression. It becomes possible to prevent the vane 4 and the rotor 3 from being overloaded and damaged.
Further, the chipped portion 35 a may have an arc shape centered on the axis center of the drive shaft 2. In this case, since the chipped portion 35a has an arc shape concentric with the hole in which the bearing 14 is provided, the chipped portion 35a can be easily formed with high accuracy.

  In the above description, the configuration example in which two vanes 4 are attached to the rotor 3 has been described. However, the same configuration is also applied to a vane type compressor in which three or more vanes 4 (vane grooves 5) are provided. You may do it.

DESCRIPTION OF SYMBOLS 1 Vane type compressor 2 Drive shaft 3 Rotor 4 Vane 5 Vane groove 9 Housing 10 1st housing member 12 Cylinder formation part 13 1st side block formation part 20 2nd housing member 21 2nd side block formation part 35 36 Guide mechanism

Claims (6)

A first housing member integrally formed with a cylinder forming portion having an inner peripheral surface formed in a perfect circle, and a first side block forming portion that closes one end side in the axial direction of the cylinder forming portion; A housing is configured by combining with a second housing member formed with a second side block forming portion that closes the other end side in the axial direction of the cylinder forming portion,
A drive shaft rotatably supported by the first side block forming portion and the second side block forming portion; a rotor fixed to the drive shaft and rotatably accommodated in the cylinder forming portion; A plurality of vane grooves provided in the rotor, and a vane slidably inserted into the vane groove,
In a vane type compressor in which a plurality of compression chambers are formed by the rotor and the vanes in a space closed by the cylinder forming portion, the first side block forming portion, and the second side block forming portion.
The first side block forming portion is integrally provided with a guide mechanism for restricting movement of the vane in the insertion direction into the vane groove, and the guide mechanism is concentric with the inner peripheral surface of the cylinder forming portion. A vane type compressor having an outer peripheral surface formed into a perfect circle.   2. The vane compressor according to claim 1, wherein the vane groove is formed from an outer peripheral surface of the rotor toward an axis center of the drive shaft.   The tip of the vane that is in sliding contact with the inner peripheral surface of the cylinder forming portion is located at a front side portion in the moving direction of the vane by the rotation of the rotor from the center position in the thickness direction of the vane. The vane type compressor according to claim 1 or 2, wherein the vane type compressor protrudes most in a direction in which the groove slides.   An end of the vane on the guide mechanism side is a direction in which the vane slides in the vane groove at a position on the rear side in the moving direction of the vane due to the rotation of the rotor from the center position in the thickness direction of the vane. The vane type compressor according to any one of claims 1 to 3, wherein the vane type compressor is most protruded.   The vane compressor according to any one of claims 1 to 4, wherein the guide mechanism is also provided in the second side block forming portion.   2. The guide mechanism according to claim 1, further comprising a chipped portion that allows movement of the vane in the insertion direction into the vane groove in the vicinity of the largest protrusion amount of the vane from the vane groove. The vane type compressor according to any one of 5.

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