JP2009191796A - Vane compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vane compressor capable of obtaining stable rotary motion and reducing noise and vibration, in regard to a vane compressor in which a discharge valve is unnecessary. <P>SOLUTION: A rotor 3 is formed with a ventilation hole 11 in each of regions partitioned by vanes 5. A flow-in opening 9 as a flow-in opening for gas to the ventilation hole 11 and a discharge opening 10 through which the gas from the ventilation hole 11 is discharged are formed in the peripheral surface of the rotor 3. The flow-in opening 9 and the discharge opening 10 of the ventilation hole 11 are arranged in positions displaced from each other in the rotary shaft direction of the rotor 3. A discharge port 8 of a cylinder 2 is arranged in a position corresponding to a movement locus of the discharge port 10 to be moved by rotation of the rotor 3. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a vane compressor mainly used for car air conditioners, room air conditioners, refrigerators and the like.

  The compressor is roughly classified into a rotary type and a reciprocating type. The rotary type has the advantage of less noise and vibration during operation than the reciprocating type. For this reason, it is used for an air conditioner in an automobile (hereinafter referred to as “air conditioner”), an outdoor unit of an indoor air conditioner, and the like. Vane type, rotary type, scroll type, etc. are generally known as rotary compressors. Vane type is mainly used for air conditioning equipment in automobiles, and scroll type and rotary type are mainly used for outdoor units of air conditioners. ing.

  A conventional vane compressor will be described. A vane compressor mainly includes a cylinder and a cylindrical rotor that rotates in a space in the cylinder. In the rotor, a plurality of grooves cut in the radial direction are formed at equal intervals in the circumferential direction, and plate-like vanes are respectively fitted in the grooves. Each vane is slidable in the normal direction. The cylinder is a substantially cylindrical member whose internal space is larger than the diameter of the rotor. When the rotor rotates, the vane slides toward the outside in the radial direction of the rotor, and the tip is in sliding contact with the inner wall of the cylinder. As a result, a sealed space (hereinafter referred to as “compression chamber”) is formed between the adjacent vanes provided in the rotor in the cylinder. Further, the cylinder is provided with a suction port for sucking gas into the compression chamber and a discharge port for discharging compressed gas. Valve ”).

  On the other hand, the scroll compressor mainly includes a movable scroll in which a spiral jetty is formed and a fixed scroll in which a similar spiral jetty is formed. The fixed scroll is provided with a discharge port at the center of a spiral to discharge compressed gas. The fixed scroll and the movable scroll engage with each other in a spiral jetty, and the movable scroll performs an arc motion while maintaining the posture. Thereby, the gas is collected from the outside of the spiral toward the center while being compressed, and is discharged from the discharge port. As with the vane compressor, the discharge port is provided with a valve to prevent the backflow of the compressed gas.

  As described above, conventional vane compressors and scroll compressors are equipped with a valve at the discharge port to prevent the backflow of gas, and the gas is released by pushing the valve using the pressure of the compressed gas. Is being discharged. After the compressed gas pushes and opens the valve, the valve closes the discharge port by an elastic effect or the like. At this time, the valve generates a striking sound (hereinafter referred to as “opening / closing sound”) as the discharge port is closed. The rotary compressor has less noise and vibration than the reciprocating compressor, but noise and vibration are still generated, and the main cause is the above-mentioned opening / closing noise. In order to reduce the above-mentioned opening / closing sound as much as possible, various ideas have been made for conventional compressors. Hereinafter, conventional improvement measures will be described.

  The invention described in Patent Document 1 relates to a vane type compressor. The rotor is cylindrical, and a plurality of vanes are provided at equal intervals in the circumferential direction. The space inside the cylinder has an elliptic cylinder shape, and the circular center of the rotor and the elliptical center of the cylinder are located concentrically. Grooves are formed in the rotor at positions adjacent to the vanes. Each of these grooves is formed at one end of the length direction of the cylinder (axial direction of the rotor). The discharge port is formed on an elliptical surface inside the cylinder, and is designed so that the groove and the discharge port overlap when the rotor rotates. That is, when the rotor rotates, the sucked gas is compressed and pushed into the groove, and when the groove of the rotor overlaps the discharge port provided in the cylinder, the gas pushed into the groove is It is discharged from the discharge port. When the discharge port and the groove do not overlap, the side surface of the rotor closes the discharge port of the cylinder, so there is no back flow. Therefore, since it is not necessary to provide a discharge valve, no opening / closing noise is generated.

  The invention described in Patent Document 2 relates to a rotary compressor. The main constituent members are a cylindrical cylinder and a cylindrical roller that rotates inside the cylinder. The cylinder is provided with one plate-shaped blade toward the central axis and is slidable in the normal direction. The outer diameter of the roller is slightly smaller than the inner diameter of the cylinder, and the roller rotates in the cylinder. The rotation shaft of the roller is eccentric, and the peripheral wall of the longest portion extending outward from the rotation shaft of the roller rotates along the inner wall of the cylinder. The compression chamber is divided by sliding the blade simultaneously with the rotation of the roller in the cylinder. A discharge port is provided on an end face inside the cylinder. A disc having the same diameter as that of the cylinder is attached to the end surface of the roller, and a discharge guide hole communicating with the discharge port at a predetermined rotation angle of the disc is provided. The roller rotates in the cylinder, the discharge guide hole overlaps the discharge port at a predetermined rotation angle, and compressed gas is discharged. When the discharge guide hole and the discharge port do not overlap due to the rotation angle of the roller, a disk attached to the roller closes the discharge port. Therefore, since the compressed gas does not flow back and there is no need to provide a discharge valve, no opening / closing noise is generated.

  The invention described in Patent Document 3 relates to a vane rotary air pump. The main components are a cylindrical cylinder and a columnar rotor designed to have an outer diameter that is slightly smaller than the inner diameter of the cylinder. The central axis of the internal space of the cylinder is shifted from the central axis of the rotor, and the rotor is installed at a position where its peripheral wall contacts the inner wall of the cylinder, and rotates around the central axis. The rotor includes a plurality of vanes slidable in the normal direction, and a pump space is formed between adjacent vanes in the cylinder. The cylinder is provided with a suction port and a discharge port, and is designed so that the suction port and the discharge port do not directly communicate with each other by calculating a predetermined rotation angle of each vane provided in the rotor. Yes. That is, a pressure at which gas is constantly discharged is generated at the discharge port, and a discharge valve is not necessary.

JP-A-10-131878 Japanese Patent Application Laid-Open No. 08-193384 JP 2006-46206 A

  As described above, there is already a conventional example that does not require a discharge valve in order to reduce noise or vibration. Among these conventional techniques, a technique that is relatively close to the present invention is the technique described in Patent Document 1. However, the invention described in Patent Document 1 has the following problems to be solved. A characteristic configuration in the invention described in Patent Document 1 is that a groove for pushing the sucked gas is provided at a position adjacent to each vane of the rotor. These grooves are formed at one end in the direction of the rotation axis continuously to the vane grooves that guide the sliding of the vanes. Accordingly, the formation of the groove reduces the guide area of the vane, makes the vane unstable, and there is a problem that when the compressed air is pushed into the groove, the vane is easily rattled by the pressure. Moreover, in order to form the groove | channel for pushing in gas continuously to a vane groove | channel, it is necessary to perform a troublesome cutting process.

  The present invention solves the above-described problem, that is, a vane compressor that does not require a discharge valve, and achieves stable rotational motion without causing rattling in the rotational axis direction of the rotor. An object of the present invention is to provide a vane compressor that can reduce noise and vibration and is easy to process.

  The present invention includes a cylinder having a suction port for sucking gas and a discharge port for discharging compressed gas, a rotor that rotates in the cylinder, a slide that is provided so as to be slidable from the inside of the rotor toward the outer periphery. A plurality of vanes slidably in contact with the inner peripheral wall surface of the cylinder, and the vanes that compress the gas sucked from the suction port and discharge from the discharge port as each vane advances and retreats with respect to the rotor as the rotor rotates. The rotor has a vent hole in each of the regions divided by the vanes, and a gas inlet to the vent hole and a gas outlet from the vent are provided on the outer periphery of the rotor. Formed in the surface, the inlet and outlet of the vent hole are in a position displaced from each other in the rotational axis direction of the rotor, and the discharge port of the cylinder is The most important feature that the position corresponding to the movement locus of the discharge port by rotation of the rotor.

  According to the present invention, the rotor is formed with an inlet and an outlet in a region partitioned by the vanes, and each communicates with each other to form a vent hole. The gas flows into the compression chambers separated by, and the gas can be discharged from the compression chamber to the discharge port through the discharge port. The discharge port communicates with the discharge port of each vent hole at a predetermined rotation angle of the rotor, and the peripheral wall of the rotor closes the discharge port at other rotation angles. Therefore, even if gas flows backward from the discharge port, the peripheral wall of the rotor prevents entry into the compression chamber. That is, no discharge valve is required, and noise and vibration associated with opening and closing of the discharge valve are eliminated.

  Further, the vent hole does not need to be continuously formed in each vane groove that guides the sliding of each vane, and drilling by a drill is sufficient from the outer peripheral surface side of the rotor. At the same time, each vane is held stably and no rattling occurs. Therefore, a stable rotational motion of the rotor can be obtained.

  Furthermore, the vent hole in the present invention can change the volume of the vent hole by changing the diameter of the hole, for example. In the manufacturing process of the rotor of the vane compressor according to the present invention, the compression rate of the compression chamber is changed by changing the volume of the vent hole, and the pressure of the gas pushed into the vent hole can be adjusted. When it is desired to reduce the compression, the volume of the vent hole is increased. Conversely, when the compression is increased, the volume of the vent hole is decreased.

  Embodiments of a vane compressor according to the present invention will be described below with reference to the drawings. FIG. 1 is a cross-sectional view showing an embodiment of a vane compressor according to the present invention. In FIG. 1, the vane compressor 1 includes a cylinder 2 and a rotor 3. The cylinder 2 has a substantially cylindrical inner space larger than the outer diameter of the rotor 3. The rotor 3 has a cylindrical shape and is rotatably supported in the internal space of the cylinder 2. In the embodiment of the vane compressor shown in FIG. 1, the rotation shaft 4 of the rotor 3 is eccentric with respect to the central axis of the internal space of the cylinder 2. The cylinder 2 is provided with a suction port 7 for sucking the gas to be compressed into the compression chamber 6 and a discharge port 8 for discharging the compressed gas, respectively, penetrating the cylinder 2 in the radial direction. The suction port 7 and the discharge port 8 are holes having a circular cross section, and are formed at a predetermined interval in the circumferential direction of the cylinder 2 and at a position shifted in the rotational axis direction of the rotor 3 as shown in FIG. ing.

  In the rotor 3, a plurality of grooves 31 (four in the illustrated example) are formed at equal intervals in the circumferential direction, which are cut along a direction in which the outer side is inclined in the rotation direction of the rotor 3 with respect to the radial direction. A plate-like vane 5 is fitted in each groove 31. Each vane 5 is slidable along each groove 31. When the rotor 3 rotates, the vane 5 slides toward the outside of the rotor 3, and the tip edge comes into sliding contact with the inner wall of the cylinder 2. Each vane 5 may be configured such that the tip edge is in sliding contact with the inner wall of the cylinder 2 by centrifugal force generated by rotating together with the rotor 3, or the tip edge is in sliding contact with the inner wall of the cylinder 2 by biasing force. It may be energized. As a result, in the internal space of the cylinder 2, the compression chamber 6 partitioned by the vane 5 and the inner wall surface of the cylinder 2 is provided between the vane 5 provided in the rotor 3 and the adjacent vane 5. It is formed.

  In the rotor 3, the air holes 11 are formed for each region divided by the vanes 5. The vent hole 11 is used to let the gas flowing into the compression chamber 6 from the suction port 7 into the vent hole 11 and to discharge the gas pushed into the vent hole 11 from the compression chamber 6 through the discharge port 8. It consists of a discharge port 10. The inlet 9 and the outlet 10 are formed from the outer peripheral surface side of the rotor 3 toward the inner side of the rotor 3 by, for example, drilling with a drill. Further, by forming at least one of the inlet 9 and the outlet 10 obliquely, the inlet 9 and the outlet 10 communicate with each other in a V-shaped cross section inside the rotor 3.

  Hereinafter, the operation of the above embodiment will be described in order according to the rotational motion of the rotor. The rotor 3 is rotationally driven in the cylinder 2 counterclockwise by a motor (not shown) or the like. 1 to 4 show continuously the rotational movement of the rotor and the accompanying gas suction, compression, and exhaust operations in the vane type compressor according to the above embodiment. Here, in FIG. 1, focusing on the compression chamber 6 communicating with the suction port 7, this compression chamber will be described as A. The compression chamber A communicating with the suction port 7 increases in volume as the rotor 3 rotates counterclockwise, and gas flows into the compression chamber A from the suction port 7.

  When the rotor 3 further rotates, the vane 5 on the rear side in the rotational direction that defines the compression chamber 6 passes through the position of the suction port 7, and the inflow of gas into the compression chamber 6 stops. As shown in FIG. 2, after the rotor 3 further rotates and the volume of the compression chamber 6 becomes the maximum, the volume of the compression chamber A starts to be reduced, and the gas in the compression chamber 6 starts to be compressed. As shown in FIG. 3, the compression chamber A is further compressed and pushed into the vent hole 11 of the rotor 3. When the rotor 3 further rotates, the vane 5 in front of the rotation direction defining the compression chamber A passes through the discharge port 8. However, since the rotor 3 is eccentric with respect to the cylinder 2, the outer peripheral surface of the rotor 3 faces the discharge port 8, and the discharge of the gas compressed in the compression chamber A is restricted. Therefore, the gas in the compression chamber A is further compressed, and the gas is further pushed into the vent hole 11.

  In FIG. 4, when the rotor 3 further rotates and the discharge port 10 of the vent hole 11 corresponding to the compression chamber A faces the discharge port 8, the gas pushed into the vent hole 11 is discharged at once by the pressure. This shows the state. When the vane 5 on the front side in the rotational direction that defines the compression chamber A passes through the position of the suction port 7, the suction into the compression chamber A is started, and the operation mode shown in FIG.

  In the illustrated embodiment, the rotor is provided with four vanes and four compression chambers are formed, and the four compression chambers continuously perform suction, compression, and exhaust operations. The number of compression chambers can be changed as appropriate. In the illustrated embodiment, the cross-sectional shape of the vent hole 11 formed in the rotor 3 is V-shaped, but it may not be V-shaped. The shape of the vent hole can be changed in any way as long as it is possible to communicate with each other in the region of one compression chamber divided by adjacent vanes and to allow the gas to flow therethrough.

  FIG. 5 is a side view of the rotor 3. The suction port 7 and the discharge port 8 on the cylinder 2 side are indicated by dotted lines. In FIG. 5, the inlet 9 and the outlet 10 of the vent hole 11 are formed at positions shifted in the rotational axis direction of the rotor 3. The discharge port 8 exists at a position corresponding to the movement locus of the discharge port 10 accompanying the rotation of the rotor 3. As a result, the compressed gas is discharged only when the position of the discharge port 10 and the position of the discharge port 8 match, and otherwise, the peripheral wall of the rotor 3 closes the discharge port 8, so that the discharge port 8 The backflow of gas to the compression chamber 6 can be prevented. The suction port 7 may be located at a position deviating from the movement locus of the discharge port 10, and need not be provided at a position corresponding to the movement locus of the inlet 9.

  In the illustrated embodiment, the inlet 9 and the outlet 10 of the air hole 11 of the rotor 3 are formed at positions shifted in the rotational direction of the rotor 3. However, it is not always necessary to shift the inlet 9 and the outlet 10 in the rotation direction of the rotor 3, and it may be desirable not to shift in the rotation direction depending on the design. The positional relationship between the vane 5 and the vent hole 11 of the rotor 3 may be appropriately changed so that the gas can be efficiently sucked in and compressed and discharged without waste.

  As described above, according to the present invention, by forming the inlet and the outlet in the rotor and providing the vent holes that communicate with each other, the discharge valve can be made unnecessary, and noise and vibration can be reduced. Can be reduced. Further, by providing the rotor with a vent hole, it is possible to prevent rattling due to pressure applied to one end portion in the rotation axis direction of the rotor, and a stable rotational motion can be obtained.

It is a cross-sectional view which shows the Example of the vane type compressor concerning this invention. It is a cross-sectional view which shows the different operation | movement aspect of the said Example. It is a cross-sectional view which shows the further different operation | movement aspect of the said Example. It is a cross-sectional view which shows the further different operation | movement aspect of the said Example. It is a front view which shows the rotor in the said Example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Vane type compressor 2 Cylinder 3 Rotor 4 Rotating shaft 5 Vane 6 Compression chamber 7 Suction port 8 Discharge port 9 Inlet port 10 Outlet port 11 Vent hole

Claims (5)

A cylinder having a suction port for sucking gas and a discharge port for discharging compressed gas, a rotor rotating in the cylinder, and a slidable portion from the inside of the rotor toward the outer peripheral direction, the tip of which is inside the cylinder A vane compressor that compresses the gas sucked from the suction port and discharges the gas from the discharge port as each vane advances and retreats with respect to the rotor as the rotor rotates. And
In the rotor, a vent is formed for each region divided by the vanes, and a gas inlet to the vent and a gas outlet from the vent are formed on the outer peripheral surface of the rotor. ,
The inflow port and the discharge port of the vent hole are at positions shifted from each other in the rotation axis direction of the rotor,
The vane type compressor, wherein the discharge port of the cylinder is at a position corresponding to a movement locus of the discharge port due to rotation of the rotor.   The inlet of the vent hole is located at the rear side in the rotation direction of the rotor in the region delimited by the vanes, and the discharge port of the vent hole is opened at the front side in the rotation direction of the rotor from the inlet port in the region delimited by the vanes. The vane type compressor according to claim 1.   The inner circumferential surface of the cylinder is a cylindrical surface, the outer circumferential surface of the rotor is a cylindrical surface having a smaller diameter than the inner circumferential surface of the cylinder, and the rotation center of the rotor is provided at a position offset from the center of the cylinder contact surface. The vane type compressor according to claim 1.   The positional relationship between the discharge port and the rotor discharge port is set so that the rotor discharge port corresponds to the discharge port of the cylinder when the gas in the region divided by the vane is compressed to the maximum extent. The vane compressor described.   2. The vane compressor according to claim 1, wherein the rotor air holes are formed in a V shape from two locations on the outer peripheral surface of the rotor toward the inside of the rotor and are connected inside the rotor.

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