JP2009257274A - Rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve compressor efficiency and reliability, by relieving abutting on a vane side surface by applying round-chamfering to a side surface distal end corner part of a suction side of a vane groove of a cylinder, since a shape and the surface roughness are not specified on the vane groove of a mating cylinder only by paying attention to the surface roughness of a suction side of a vane side surface, and since the surface roughness of a certain degree is secured by generally polishing a vane side surface, in a conventional constitution. <P>SOLUTION: A sliding loss of the vane can be reduced by being characterized by constituting the round-chamfering on the side surface distal end corner part Ra of the suction side of the vane groove 7 of the cylinder 1. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an improvement in performance and reliability of a rotary compressor incorporated in a room air conditioner, a refrigerator, and an air conditioner.

  A conventional vane of this type of rotary compressor is configured to be reciprocated by being inserted into a vane groove of a cylinder (see, for example, Patent Document 1).

FIG. 5 is a cross-sectional view seen from the upper bearing side of the conventional rotary compressor described in Patent Document 1. A vane 53 is inserted into a vane groove 52 provided in the cylinder 51. The tip of the vane is pressed against the outer periphery of the piston 54 by a pressure difference between the discharge pressure and the suction pressure, and reciprocates in accordance with the rotation of the piston. Further, the compression pressure Pc acts on the discharge side of the side surface of the vane 53 that has jumped out of the vane groove 52, and the suction pressure Ps acts on the suction side. Because of these forces, the tip of the vane tilts toward the suction side to perform reciprocating motion, so the suction side side tip corner of the vane groove 52, the suction side of the vane, the discharge side corner of the back of the vane 53, and the discharge side of the vane groove 52 Side sliding was severe and caused boundary friction, which increased input and greatly affected reliability.
Japanese Patent No. 2817395

  However, in the configuration of Patent Document 1, only the surface roughness of the suction side surface of the vane 53 is focused, and the shape and surface roughness of the counterpart cylinder vane groove 52 are not specified. Moreover, since the vane side surface is generally polished, a certain degree of surface roughness was ensured. Since the vicinity of the tip of the vane groove 52 on the suction side slides and becomes familiar with the suction side surface of the vane 53, the surface roughness becomes a value smaller than the initial value, so that it is considered that polishing or the like is not particularly required. Further, since the discharge side of the vane groove 52 slides on the discharge side surface of the vane 53 with a large area, the familiarity is small and the surface roughness of the initial processed surface remains.

  The present invention has been made in view of the above-described problems of the prior art, and the suction side side corner of the cylinder vane groove is rounded to reduce the contact with the side surface of the vane. It aims to improve and improve reliability.

  In order to achieve the above object, the invention according to claim 1 of the present invention is characterized in that an R chamfer is formed on the suction side side end corner of the vane groove of the cylinder.

  This makes it possible to reduce the vane sliding loss.

  By forming an R chamfer on the suction side side corner of the vane groove of the cylinder of the rotary compressor of the present invention, the sliding loss on the vane side surface can be reduced and the compressor efficiency can be improved. Further, since the sliding state is improved, the reliability can be improved.

  In the first aspect of the invention, a rounded chamfer is applied to the suction side side tip corner of the vane groove of the cylinder to reduce sliding loss with the suction side surface of the vane.

  According to a second aspect of the present invention, the surface roughness Ry value is processed to an appropriate value in the range of Ry = 0.1 μm to 0.9 μm by processing the discharge side surface of the vane groove of the cylinder, and the surface roughness Ry value is set to be more suitable than the suction side surface of the vane groove. By reducing the surface roughness Ry value, the sliding loss of the vane side surface can be reduced. That is, when the surface roughness Ry value is larger than 0.9, the metal-to-metal contact between the discharge side surface of the vane and the discharge side surface of the vane groove of the cylinder increases, and the input increases. If the ratio is smaller than 0.1, the oil holding capacity between the discharge side surface of the vane and the discharge side surface of the vane groove of the cylinder becomes small, and even if the Ry value is further reduced, the effect is not obtained so much. By setting the surface roughness Ry value to an appropriate roughness, the sliding state is improved and the reliability can be improved.

  In the third aspect of the invention, the discharge side corner portion on the back surface of the vane is rounded to reduce sliding loss with respect to the discharge side surface of the vane groove.

  According to a fourth aspect of the present invention, a bulging portion is provided in the moving direction of the discharge side surface of the vane, thereby reducing the collision noise and vibration between the discharge side surface of the vane and the discharge side surface of the vane groove of the cylinder. It has become.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, this invention is not limited by this embodiment.

(Embodiment 1)
FIG. 1 shows a longitudinal sectional view of a mechanical part of a rotary compressor according to a first embodiment of the present invention.

  As shown in FIG. 1, an upper bearing 2 is attached to the upper portion of the cylinder 1, and a lower bearing 3 is attached to the lower portion, and a piston 5 that rotates by a shaft 4 is provided in a space surrounded by the upper bearing 2. Since the compressed discharge pressure works behind the vane 6, it is inserted into the vane groove 7 of the cylinder while being pressed against the outer periphery of the piston 5, and reciprocates.

  FIG. 2 is a cross-sectional view of the mechanical part viewed from the upper bearing 2 of the rotary compressor according to the first embodiment of the present invention. A vane 6 is inserted into the vane groove 7 of the cylinder 1. The cylinder 1 is provided with a suction port 8 and a discharge notch 9. A cylinder chamber surrounded by the inner surface of the cylinder 1 and the outer periphery of the piston 5 is partitioned by a vane 6 to form a suction chamber 10 and a compression chamber 11.

  About the rotary compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  First, the refrigerant gas is sucked into the suction chamber 10 from the suction port 8 while the piston 5 makes one rotation with the rotation of the shaft 4. The refrigerant gas sucked into the suction chamber 10 enters the compression process during one rotation of the next shaft 4 to become the compression chamber 11, and the refrigerant gas is compressed with the rotation of the piston 5 and passes through the discharge notch 9 from the discharge port. Discharged. During the compression, the suction chamber 10 is at the suction pressure Ps, and the compression chamber 11 is at the compression pressure Pc. Further, since Pc> Ps, the tip of the vane 6 is pushed by the compression pressure Pc and tilts toward the suction side to reciprocate.

FIG. 3 is a sectional view showing details in the vicinity of the vane 6. A vane 6 is inserted into the vane groove 7 of the cylinder 1 and reciprocates in accordance with the rotation of the piston 5. As described above, since the compression pressure Pc acts on the discharge side surface 6b of the vane and the suction pressure Ps acts on the suction side surface 6a, the force F due to the differential pressure (Pc-Ps) acts and the tip of the vane 6 sucks. Reciprocating while tilting to the side. As can be seen from FIG. 3, the suction side surface tip corner portion Ra of the vane groove 7 and the suction side surface 6a of the vane 6, the discharge side surface 7b of the vane groove 7 and the discharge side corner portion Rb of the vane back surface cause severe boundary friction. Yes. In order to alleviate these boundary frictions, an R chamfer is formed on the suction side side edge corner Ra of the vane groove 7 and an R chamfer is formed on the discharge side corner Rb on the rear surface of the vane. The tip of the discharge side surface 7b of the vane groove 7 is a corner and is not chamfered. Also, the suction side corner on the back of the vane is not rounded. In general, the vane 6 is made of a hard material such as steel steel and is aggressive, and the cylinder 1 is made of a casting. Yes. The surface roughness value Ry of the suction side surface 7a of the vane groove 7 is processed to about Ry = 2.2 μm. Further, in order to reduce the sliding loss of the discharge side surface 7b of the vane groove 7, the discharge side surface 7b of the vane groove 7 is processed so as to have a surface roughness Ry value of about Ry = 0.5 μm. Therefore, the surface roughness value of the suction side surface 7a of the vane groove 7 is smaller.

  A bulging portion 6 c is provided on the discharge side surface 6 b of the vane 6 in the moving direction of the vane 6. As a result, the contact between the discharge side surface 6b of the vane 6 and the discharge side surface 7b of the vane groove 7 is alleviated, and the discharge side surface 6b of the vane 6 and the discharge of the vane groove 7 when the vane 6 is near the top dead center. Sound and vibration due to the collision of the side surface 7b can be reduced. In FIG. 3, the bulge portion 6c is drawn large, but the actual bulge is on the order of 5 μm.

  FIG. 4 shows the input reduction amount of the compressor when the vane groove surface roughness of the discharge side surface of the cylinder vane groove is improved, based on the input value of the surface roughness Ry = 2.2 μm. Surface roughness Ry = 2.2 μm, 1.1 μm, 0.5 μm, 0.1 μm input measurement is performed, and the horizontal axis represents the surface roughness value Ry value, and the vertical axis represents the surface roughness Ry = 2.2 μm input value. It is shown as a percentage. By processing the surface roughness Ry value of the vane groove on the discharge side surface to an appropriate value in the range of Ry = 0.1 μm to 0.9 μm, the input of the compressor could be reduced. That is, when the surface roughness Ry value is larger than 0.9, the metal-to-metal contact between the discharge side surface of the vane and the discharge side surface of the vane groove of the cylinder tends to increase and the input tends to increase. When the Ry value is smaller than 0.1, the oil holding capacity between the discharge side surface of the vane and the discharge side surface of the vane groove of the cylinder becomes small, and even if the Ry value is further reduced, the effect is not obtained so much. It has become a trend.

  As described above, in the present embodiment, the chamfering of the vane side surface of the vane groove of the cylinder of the rotary compressor is rounded so that the sliding loss on the side surface of the vane can be reduced. Therefore, sliding loss can be reduced and compression efficiency can be improved. In addition, reliability can be improved.

As described above, since the rotary compressor according to the present invention can improve the compression efficiency, it can also be applied to CO ₂ compressors for hot water heaters and air compression applications.

1 is a longitudinal sectional view of a mechanical part of a rotary compressor according to a first embodiment of the present invention. The cross-sectional view of the mechanical part seen from the upper bearing of the rotary compressor concerning Embodiment 1 of this invention Detail sectional drawing of the principal part of vane vicinity of the rotary compressor concerning Embodiment 1 of this invention The characteristic view which shows the vane groove surface roughness and input reduction effect of the cylinder of the rotary compressor concerning Embodiment 1 of this invention Cross section of mechanical part viewed from the upper bearing of a conventional rotary compressor

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Cylinder 2 Upper bearing 3 Lower bearing 4 Shaft 5 Piston 6 Vane 6a Suction side surface 6b Discharge side surface 6c Swelling part 7 Vane groove 7a Suction side surface 7b Discharge side surface 8 Suction port 9 Discharge notch 10 Suction chamber 11 Compression chamber Ra The corner on the suction side of the vane groove Rb The corner on the discharge side on the back of the vane

Claims (4)

On both end faces of the cylinder, an upper bearing and a lower bearing are arranged, and a piston that rotates in the cylinder, a shaft that drives the piston, and a vane that partitions the inside of the cylinder into a compression chamber that opens a suction chamber and a discharge port. The vane is inserted into the vane groove of the cylinder and the discharge pressure compressed on the back surface of the vane acts, and reciprocates while pressing the vane against the outer periphery of the piston in accordance with the rotation of the piston. A rotary compressor in which compressed refrigerant gas is sucked and compressed at the same time, and a rounded chamfer is formed on the suction side end of the vane groove of the cylinder. The surface roughness Ry value is processed in the range of Ry = 0.1 μm to 0.9 μm by processing the discharge side surface of the vane groove of the cylinder, and the surface roughness Ry value is made smaller than the suction side surface of the vane groove. The rotary compressor according to claim 1. The rotary compressor according to claim 1, wherein suction and compression of the compressed refrigerant gas are performed in association with the rotation of the piston, and an R chamfer is applied to a discharge side corner of the back surface of the vane. The rotary compressor according to claim 1, wherein a bulging portion is provided in a moving direction of a discharge side surface of the vane.