Patent Publication Number: US-10309399-B2

Title: Rotary compressor

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
     This application is based upon and claims the benefit of priorities from Japanese Patent Application No. 2016-080229 filed on Apr. 13, 2016, the entire contents of which are incorporated herein by reference. 
     FIELD 
     The present invention relates to a rotary compressor. 
     BACKGROUND 
     In a rotary compressor, an annular piston provided to be eccentric to a rotation shaft rotates in a cylinder, a tip end of a plate-like vane which reciprocates in the cylinder in accordance with rotation of the piston is thrust to an outer circumferential surface of the piston, and accordingly, the inside of the cylinder is divided into a compression chamber and an inlet chamber. In a two-cylinder type rotary compressor, the vane slides in a vane groove of the cylinder nipped by an end plate and an intermediate partition plate in a state of being biased by a spring. 
     In this type of rotary compressor, when a gas refrigerant is compressed by the piston in the cylinder, the rotation shaft is bent only by an extremely small amount with respect to the shaft direction. The piston is inclined with respect to the direction orthogonal to the rotation shaft in accordance with the bending of the rotation shaft, and the vane is inclined with respect to the sliding direction only by an amount of clearance between the vane and the vane groove in the upward-and-downward direction (the shaft direction of the rotation shaft) of the rotary compressor. Therefore, contact state between the tip end of the vane and the outer circumferential surface of the piston changes, and the tip end of the vane which slides in a state where the vane is bound in the vane groove is placed in a partially contact state with the outer circumferential surface of the piston. At this time, since a surface pressure of the tip end of the vane locally increases in the rotation shaft direction, there is a concern that wear or damage is generated in the vane or the piston. 
     As the rotary compressor of the related technology, in order to suppress the partially contact state of the vane with the piston, a configuration in which the vane is divided into two with respect to the rotation shaft direction, and the tip ends of the two vanes which are aligned in the rotation shaft direction respectively come into contact with the outer circumferential surface of the piston, is known. In this configuration, inclination is dispersed into the two vanes, and the partially contact state of the vane with the piston is suppressed. 
     WO 2014/025025 is an example of the related art. 
     However, in the rotary compressor of the above-described related art, by dividing the vane into two, sliding resistance is generated between each of the vanes. Therefore, there is an influence on sliding properties in the entire vane, and operation reliability of the entire vane deteriorates. In addition, since the springs are disposed in each vane divided into two, the structure becomes complicated, and manufacturing costs increase. 
     SUMMARY 
     Considering the above-described situation, an object of the invention is to provide a rotary compressor which can suppress a partially contact state of the vane with the piston, and improve operation reliability of the vane. 
     According to an aspect of the invention, there is provided a rotary compressor including: a sealed vertically-placed cylindrical compressor housing in which a discharging unit for a refrigerant is provided in an upper portion, and an inlet unit for the refrigerant is provided in a lower portion; a compressing unit which is disposed in the lower portion of the inside of the compressor housing, and which compresses the refrigerant suctioned from the inlet unit, and which discharges the refrigerant from the discharging unit; and a motor which is disposed in the upper portion of the inside of the compressor housing, and which drives the compressing unit, in which the compressing unit includes annular upper and lower cylinders, an upper end plate which closes an upper side of the upper cylinder, a lower end plate which closes a lower side of the lower cylinder, an intermediate partition plate which is disposed between the upper cylinder and the lower cylinder, and which closes the lower side of the upper cylinder and the upper side of the lower cylinder, a rotation shaft which is supported by a main bearing unit provided in the upper end plate and a sub-bearing unit provided in the lower end plate, and which is rotated by the motor, an upper eccentric portion and a lower eccentric portion which are provided in the rotation shaft by applying a phase difference of 180° therebetween, an upper piston which is fitted to the upper eccentric portion, and which revolves along an inner circumferential surface of the upper cylinder, and which forms an upper cylinder chamber on the inside of the upper cylinder, a lower piston which is fitted to the lower eccentric portion, and which revolves along an inner circumferential surface of the lower cylinder, and which forms a lower cylinder chamber on the inside of the lower cylinder, an upper vane which protrudes to the inside of the upper cylinder chamber from an upper vane groove provided in the upper cylinder, and which divides the upper cylinder chamber into an upper inlet chamber and an upper compression chamber by abutting against the upper piston, and a lower vane which protrudes to the inside of the lower cylinder chamber from a lower vane groove provided in the lower cylinder, and which divides the lower cylinder chamber into a lower inlet chamber and a lower compression chamber by abutting against the lower piston, in which a concave portion is provided at a position at which the upper vane and the lower vane slide in the outer circumferential portion of the intermediate partition plate, in which 80% or more of the entire length in the sliding direction of the lower vane and the upper vane are accommodated respectively on the inside of the upper cylinder and the inside of the lower cylinder at a lower dead center of the upper piston and the lower piston, in which, in the concave portion, a width W with respect to the circumferential direction of the intermediate partition plate is greater than a thickness T of the upper vane and the lower vane, and in which D≥0.1 ×L is satisfied when a depth of the concave portion is D and the entire length of the upper vane and the lower vane is L. 
     In the rotary compressor according to one aspect of the invention, it is possible to suppress a partially contact state of a vane with a piston, and to improve operation reliability of the vane. 
    
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         FIG. 1  is a longitudinal sectional view illustrating a rotary compressor according to an embodiment. 
         FIG. 2  is an exploded perspective view illustrating a compressing unit of the rotary compressor according to the embodiment. 
         FIG. 3  is a lateral sectional view when the compressing unit of the rotary compressor according to the embodiment is viewed from above. 
         FIG. 4  is a plan view illustrating an intermediate partition plate of the rotary compressor according to the embodiment. 
         FIG. 5  is a partially perspective view illustrating a concave portion of the intermediate partition plate of the rotary compressor according to the embodiment. 
         FIG. 6A  is a schematic view illustrating a state where an upper piston and a lower piston are inclined in accordance with bending of a rotation shaft in the rotary compressor according to the embodiment. 
         FIG. 6B  is a schematic view illustrating a state where an upper vane is inclined in an upper vane groove in the rotary compressor according to the embodiment. 
         FIG. 6C  is a schematic view illustrating a state where inclination of the upper vane is corrected by the concave portion of the intermediate partition plate in the rotary compressor according to the embodiment. 
     
    
    
     DESCRIPTION OF EMBODIMENTS 
     Hereinafter, an embodiment of a rotary compressor of the invention will be described in detail based on the drawings. In addition, the rotary compressor of the invention is not limited to the following embodiment. 
     Embodiment 
     Configuration of Rotary Compressor 
       FIG. 1  is a longitudinal sectional view illustrating a rotary compressor according to an embodiment.  FIG. 2  is an exploded perspective view illustrating a compressing unit of the rotary compressor according to the embodiment.  FIG. 3  is a lateral sectional view when the compressing unit of the rotary compressor according to the embodiment is viewed from above. 
     As illustrated in  FIG. 1 , a rotary compressor  1  includes: a compressing unit  12  which is disposed in a lower portion of the inside of a sealed vertically-placed cylindrical compressor housing  10 ; a motor  11  which is disposed on an upper portion of the inside of the compressor housing  10 , and drives the compressing unit  12  via a rotation shaft  15 ; and a vertically-placed cylindrical accumulator  25  which is fixed to an outer circumferential surface of the compressor housing  10 . 
     The accumulator  25  is connected to an upper cylinder chamber  130 T (refer to  FIG. 2 ) of an upper cylinder  121 T via an inlet unit configured of an upper inlet pipe  105  and an accumulator upper L-pipe  31 T, and is connected to a lower cylinder chamber  130 S (refer to  FIG. 2 ) of a lower cylinder  121 S via an inlet unit configured of a lower inlet pipe  104  and an accumulator lower L-pipe  31 S. 
     The motor  11  includes a stator  111  which is disposed on an outer side, and a rotor  112  which is disposed on an inner side. The stator  111  is fixed to an inner circumferential surface of the compressor housing  10  in a shrink fit state, and the rotor  112  is fixed to the rotation shaft  15  in a shrink fit state. 
     In the rotation shaft  15 , a sub-shaft unit  151  on a lower side of a lower eccentric portion  152 S is supported to be freely rotated by a sub-bearing unit  161 S provided in a lower end plate  160 S, and a main shaft unit  153  on an upper side of an upper eccentric portion  152 T is supported to be freely rotated by a main bearing unit  161 T provided in an upper end plate  160 T. The rotation shaft  15  is supported to be freely rotated with respect to the compressing unit  12  as each of an upper piston  125 T and a lower piston  125 S is supported by the upper eccentric portion  152 T and the lower eccentric portion  152 S which are provided by applying a phase difference of 180 degrees therebetween. In addition, by the rotation of the rotation shaft  15 , the upper piston  125 T and the lower piston  125 S are operated to revolve along the inner circumferential surfaces of each of the upper cylinder  121 T and the lower cylinder  121 S. 
     In order to ensure sliding properties of a sliding portion, such as the upper piston  125 T and the lower piston  125 S, which slide in the compressing unit  12 , and to seal an upper compression chamber  133 T (refer to  FIG. 2 ) and a lower compression chamber  133 S (refer to  FIG. 2 ), lubricant oil  18  having an amount by which the compressing unit  12  is substantially immersed is sealed on the inside of the compressor housing  10 . An attachment leg  310  (refer to  FIG. 1 ) which locks a plurality of elastic supporting members (not illustrated) that support the entire rotary compressor  1  is fixed to a lower side of the compressor housing  10 . 
     As illustrated in  FIG. 1 , the compressing unit  12  compresses a refrigerant suctioned from the upper inlet pipe  105  and the lower inlet pipe  104 , and discharges the refrigerant from a discharge pipe  107  which will be described later. As described in  FIG. 2 , the compressing unit  12  is configured by stacking an upper end plate cover  170 T including a bulging portion in which a hollow space is formed in an inner portion, the upper end plate  160 T, the annular upper cylinder  121 T, an intermediate partition plate  140 , the annular lower cylinder  121 S, the lower end plate  160 S, and a flat plate-like lower end plate cover  170 S, in order from above. The entire compressing unit  12  is fixed by a plurality of penetrating bolts  174  and  175  and an auxiliary bolt  176  which are disposed on a substantially concentric circle from above and below. 
     As illustrated in  FIG. 3 , in the upper cylinder  121 T, an upper cylinder inner wall  123 T is formed along the circle concentric to the rotation shaft  15  of the motor  11 . On the inside of the upper cylinder inner wall  123 T, the upper piston  125 T which has an outer diameter smaller than an inner diameter of the upper cylinder  121 T is disposed, and between the upper cylinder inner wall  123 T and the upper piston  125 T, the upper compression chamber  133 T which suctions, compresses, and discharges the refrigerant is formed. In the lower cylinder  121 S, along the circle concentric to the rotation shaft  15  of the motor  11 , a lower cylinder inner wall  123 S is formed. On the lower cylinder inner wall  123 S, the lower piston  125 S which has an outer diameter smaller than an inner diameter of the lower cylinder  121 S is disposed, and between the lower cylinder inner wall  123 S and the lower piston  125 S, the lower compression chamber  133 S which suctions, compresses, and discharges the refrigerant is formed. 
     As illustrated in  FIGS. 2 and 3 , the upper cylinder  121 T has an upper side protruding portion  122 T which overhung from a round outer circumference. In the upper side protruding portion  122 T, an upper vane groove  128 T which extends from the upper cylinder chamber  130 T to the outside in a radial shape, is provided. On the inside of the upper vane groove  128 T, an upper vane  127 T is disposed to be slidable. The lower cylinder  121 S has a lower side protruding portion  122 S which is overhung from the round outer circumference. In the lower side protruding portion  122 S, a lower vane groove  128 S which extends from the lower cylinder chamber  130 S to the outside in a radial shape, is provided. On the inside of the lower vane groove  128 S, a lower vane  127 S is disposed to be slidable. 
     At a position which overlaps the upper vane groove  128 T from the outside surface of the upper cylinder  121 T, an upper spring hole  124 T is provided at a depth which does not reach the upper cylinder chamber  130 T. An upper spring  126 T is disposed in the upper spring hole  124 T. At a position which overlaps the lower vane groove  128 S from the outside surface of the lower cylinder  121 S, a lower spring hole  124 S is provided at a depth which does not reach the lower cylinder chamber  130 S. A lower spring  126 S is disposed in the lower spring hole  124 S. 
     In addition, in the lower cylinder  121 S, a lower pressure guiding-in path  129 S which communicates with the outer side in the radial direction of the lower vane groove  128 S and the inside of the compressor housing  10 , has an opening portion that introduces the compressed refrigerant on the inside of the compressor housing  10 , and applies a back pressure to the lower vane  127 S by a pressure of the refrigerant, is formed. In addition, the refrigerant compressed on the inside of the compressor housing  10  is also introduced from the lower spring hole  124 S. In addition, in the upper cylinder  121 T, an upper pressure guiding-in path  129 T which communicates with the outer side in the radial direction of the upper vane groove  128 T and the inside of the compressor housing  10 , has an opening portion that introduces the compressed refrigerant on the inside of the compressor housing  10 , and applies a back pressure to the upper vane  127 T by a pressure of the refrigerant, is formed. In addition, the refrigerant compressed on the inside of the compressor housing  10  is also introduced from the upper spring hole  124 T. 
     As illustrated in  FIG. 3 , in the upper side protruding portion  122 T of the upper cylinder  121 T, an upper inlet hole  135 T which is fitted to the upper inlet pipe  105  is provided. In the lower side protruding portion  122 S of the lower cylinder  121 S, a lower inlet hole  135 S which is fitted to the lower inlet pipe  104  is provided. 
     As illustrated in  FIG. 2 , upper and lower parts of the upper cylinder chamber  130 T are closed by each of the upper end plate  160 T and the intermediate partition plate  140 . Upper and lower parts of the lower cylinder chamber  130 S is closed by each of the intermediate partition plate  140  and the lower end plate  160 S. 
     As illustrated in  FIG. 3 , as the upper vane  127 T is pressed to the upper spring  126 T, and abuts against the outer circumferential surface of the upper piston  125 T, the upper cylinder chamber  130 T is divided into an upper inlet chamber  131 T which communicates with the upper inlet hole  135 T, and the upper compression chamber  133 T which communicates with an upper discharge hole  190 T provided in the upper end plate  160 T. As the lower vane  127 S is pressed to the lower spring  126 S, and abuts against the outer circumferential surface of the lower piston  125 S, the lower cylinder chamber  130 S is divided into a lower inlet chamber  131 S which communicates with the lower inlet hole  135 S, and the lower compression chamber  133 S which communicates with a lower discharge hole  190 S provided in the lower end plate  160 S. 
     As illustrated in  FIG. 2 , in the upper end plate  160 T, the upper discharge hole  190 T which penetrates the upper end plate  160 T and communicates with the upper compression chamber  133 T of the upper cylinder  121 T, is provided, and an upper valve seat (not illustrated) is formed around the upper discharge hole  190 T on an outlet side of the upper discharge hole  190 T. In the upper end plate  160 T, an upper discharge valve accommodation concave portion  164 T which extends from a position of the upper discharge hole  190 T in a shape of a groove in the circumferential direction of the upper end plate  160 T, is formed. 
     In the upper discharge valve accommodation concave portion  164 T, all of a reed valve type upper discharge valve  200 T which includes a rear end portion fixed to the inside of the upper discharge valve accommodation concave portion  164 T by an upper rivet  202 T, and a front portion which opens and closes the upper discharge hole  190 T; and an upper discharge valve cap  201 T which overlaps the upper discharge valve  200 T, and includes a rear end portion fixed to the inside of the upper discharge valve accommodation concave portion  164 T by the upper rivet  202 T, and a curved (distorted) front portion which controls an opening degree of the upper discharge valve  200 T, are accommodated. 
     In the lower end plate  160 S, the lower discharge hole  190 S which penetrates the lower end plate  160 S and communicates with the lower compression chamber  133 S of the lower cylinder  121 S, is provided. In the lower end plate  160 S, a lower discharge valve accommodation concave portion (not illustrated) which extends from the position of the lower discharge hole  190 S in a shape of a groove in the circumferential direction of the lower end plate  160 S, is formed. 
     In the lower discharge valve accommodation concave portion, all of a reed valve type lower discharge valve  200 S which includes a rear end portion fixed to the inside of the lower discharge valve accommodation concave portion by a lower rivet  202 S, and a front portion which opens and closes the lower discharge hole  190 S; and a lower discharge valve cap  201 S which overlaps the lower discharge valve  200 S, and includes a rear end portion fixed to the inside of the lower discharge valve accommodation concave portion by the lower rivet  202 S, and a curved (distorted) front portion which controls an opening degree of the lower discharge valve  200 S, are accommodated. 
     Between the upper end plate  160 T and the upper end plate cover  170 T having a bulging portion which are fixed to adhere to each other, an upper end plate cover chamber  180 T is formed. Between the lower end plate  160 S and the flat plate-like lower end plate cover  170 S which are fixed to adhere to each other, a lower end plate cover chamber  180 S (refer to  FIG. 1 ) is formed. A refrigerant path hole  136  which penetrates the lower end plate  160 S, the lower cylinder  121 S, the intermediate partition plate  140 , the upper end plate  160 T, and the upper cylinder  121 T, and communicates with the lower end plate cover chamber  180 S and the upper end plate cover chamber  180 T, is provided. 
     Hereinafter, a flow of the refrigerant due to the rotation of the rotation shaft  15  will be described. On the inside of the upper cylinder chamber  130 T, the upper piston  125 T which is fitted to the upper eccentric portion  152 T of the rotation shaft  15  revolves along the outer circumferential surface (the inner circumferential surface of the upper cylinder  121 T) of the upper cylinder chamber  130 T due to the rotation of the rotation shaft  15 . Accordingly, the upper inlet chamber  131 T suctions the refrigerant from the upper inlet pipe  105  while enlarging capacity, and the upper compression chamber  133 T compresses the refrigerant while reducing the capacity. When the pressure of the compressed refrigerant becomes higher than the pressure of the upper end plate cover chamber  180 T on the outer side of the upper discharge valve  200 T, the upper discharge valve  200 T is open, and the refrigerant is discharged to the upper end plate cover chamber  180 T from the upper compression chamber  133 T. The refrigerant discharged to the upper end plate cover chamber  180 T is discharged to the inside of the compressor housing  10  from an upper end plate cover discharge hole  172 T (refer to  FIG. 1 ) provided in the upper end plate cover  170 T. 
     In addition, in the lower cylinder chamber  130 S, the lower piston  125 S fitted to the lower eccentric portion  152 S of the rotation shaft  15  revolves along the outer circumferential surface (the inner circumferential surface of the lower cylinder  121 S) of the lower cylinder chamber  130 S due to the rotation of the rotation shaft  15 . Accordingly, the lower inlet chamber  131 S suctions the refrigerant from the lower inlet pipe  104  while enlarging the capacity, and the lower compression chamber  133 S compresses the refrigerant while reducing the capacity. When the pressure of the compressed refrigerant becomes higher than the pressure of the lower end plate cover chamber  180 S on the outer side of the lower discharge valve  200 S, the lower discharge valve  200 S is open, and the refrigerant is discharged to the lower end plate cover chamber  180 S from the lower compression chamber  133 S. The refrigerant discharged to the lower end plate cover chamber  180 S is discharged to the inside of the compressor housing  10  from the upper end plate cover discharge hole  172 T provided in the upper end plate cover  170 T through the refrigerant path hole  136  and the upper end plate cover chamber  180 T. 
     The refrigerant discharged to the inside of the compressor housing  10  is guided to the upper part of the motor  11  through a cutout (not illustrated) which is provided on the outer circumference of the stator  111 , and communicates with the upper and lower parts, a void (not illustrated) of a winding portion of the stator  111 , or a void  115  (refer to  FIG. 1 ) between the stator  111  and the rotor  112 , and is discharged from the discharge pipe  107  which serves as a discharging unit disposed in the upper portion of the compressor housing  10 . 
     Characteristic Configuration of Rotary Compressor 
     Next, a characteristic configuration of the rotary compressor  1  according to the embodiment will be described.  FIG. 4  is a plan view illustrating the intermediate partition plate  140  of the rotary compressor  1  according to the embodiment.  FIG. 5  is a partially perspective view illustrating a concave portion of the intermediate partition plate  140  of the rotary compressor  1  according to the embodiment. 
     As illustrated in  FIGS. 4 and 5 , in the outer circumferential portion, of the intermediate partition plate  140 , a sectional arc-like concave portion  141  is provided at a position at which the upper vane  127 T and the lower vane  127 S slide. In other words, the concave portion  141  is formed at a position which respectively opposes the end portion on the outer circumference side of the intermediate partition plate  140  in the upper vane groove  128 T and the lower vane groove  128 S. In addition, the concave portion  141  is formed from one surface side to the other surface side in the direction of the rotation shaft  15  in the intermediate partition plate  140 . 
     As illustrated in  FIG. 5 , in the concave portion  141 , a width W with respect to the circumferential direction of he intermediate partition plate  140  is greater than a thickness T of the upper vane  127 T and the lower vane  127 S. Accordingly, as will be described later, the upper vane  127 T and the lower vane  127 S can enter the inside of the concave portion  141 , and it becomes possible to correct inclination with respect to the sliding direction of the upper vane  127 T and the lower vane  127 S. 
     In the embodiment, at a lower dead center of the upper piston  125 T and the lower piston  125 S, 80% or more of the entire length L in the sliding direction (the reciprocating direction with respect to the upper cylinder  121 T and the lower cylinder  121 S) of the upper vane  127 T and the lower vane  127 S are accommodated respectively on the inside of the upper cylinder  121 T and the inside of the lower cylinder  121 S. 
     In the concave portion  141 , a depth D with respect to the radial direction of the intermediate partition plate  140  is equal to or greater than 10% of the entire length L of the upper vane  127 T and the lower vane  127 S. In other words, when the depth of the concave portion  141  is D and the entire length of the upper vane  127 T and the lower vane  127 S is L, D≥0.1×L Expression 1) is satisfied. 
     Action of Concave Portion of Intermediate Partition Plate 
     In the rotary compressor  1 , when the refrigerant is compressed by the upper piston  125 T and the lower piston  125 S on the inside of the upper cylinder  121 T and on the inside of the lower cylinder  121 S, the rotation shaft  15  is bent only by an extremely small amount with respect to the shaft direction. As illustrated in  FIG. 6A , the upper piston  125 T and the lower piston  125 S are inclined with respect to the direction orthogonal to the rotation shaft  15  in accordance with the bending of the rotation shaft  15 . In accordance with the inclination of the upper piston  125 T and the lower piston  125 S, the upper vane  127 T and the lower vane  127 S are inclined with respect to the sliding direction only by an amount of clearance between the upper vane  127 T and the upper vane groove  121 T, and only by an amount of clearance between the lower vane  127 S and the lower vane groove  128 S in the upward-and-downward direction (the shaft direction of the rotation shaft  15 ) of the rotary compressor  1 , as illustrated in  FIG. 6B . Therefore, a contact state between a tip end of the upper vane  127 T and an outer circumferential surface of the upper piston  125 T, and a contact state between a tip end of the lower vane  127 S and an outer circumferential surface of the lower piston  125 S change, there is a concern that the tip ends of the upper vane  127 T and the lower vane  127 S which slide in a state of being bound on the inside of the upper vane groove  128 T and the lower vane groove  128 S, are placed in a partially contact with the outer circumferential surface of the upper piston  125 T and the lower piston  125 S. 
     However, in the embodiment, as illustrated in  FIG. 6B , even in a case where the inclination is generated in the upper piston  125 T and the lower piston  125 S, and the upper vane  127 T and the lower vane  127 S in accordance with the bending of the rotation shaft  15 , as illustrated in  FIG. 6C , as the end portion of the upper vane  127 T and the lower vane  127 S enters the inside of the concave portion  141  in an inclined state, the concave portion  141  acts as a clearance (allowance) of the upper vane  127 T and the lower vane  127 S. Therefore, a binding force is reduced in the height direction. (the direction of the rotation shaft  15 ) of the upper vane  127 T and the lower vane  127 S that slide while being bound on the inside of the upper vane groove  128 T and the inside of the lower vane groove  128 S, and postures of the upper vane  127 T and the lower vane  127 S are likely to change on the inside of the upper vane groove  128 T and the inside of the lower vane groove  128 S. Accordingly, in the upper vane  127 T (lower vane  127 S), an inclined state (solid line in  FIG. 6C ) when a jumping amount to the upper cylinder chamber  130 T (lower cylinder chamber  130 S) is small, can be smoothly corrected to era appropriate state (broken line in  FIG. 6C ) when the jumping amount to the upper cylinder chamber  130 T (lower cylinder chamber  130 S) is large, and the upper vane  127 T (lower vane  127 S) can return to an appropriate sliding state. In the concave portion  141  of the intermediate partition plate  140 , as the depth D satisfies the above-described expression 1, an inclination correction action of the upper vane  127 T and the lower vane  127 S with respect to the height direction can be appropriately obtained. In addition,  FIGS. 6B and 6C  illustrate the inclined state of the upper vane  127 T on the inside of the upper vane groove  128 T in accordance with the inclination of the upper piston  125 T, but the inclined state of the lower vane  127 S on the inside of the lower vane groove  128 S in accordance with the inclination of the lower piston  125 S, is also similar. 
     A case where the depth D of the concave portion  141  is less than 10% of the entire length L of the upper vane  127 T and the lower vane  127 S, is not preferable since the depth is not sufficient, and the action of correcting the inclined state of the upper vane  127 T and the lower vane  127 S is not sufficiently performed. 
     In addition, when cutting processing is performed with respect to the intermediate partition plate  140  in the thickness direction, the concave portion  141  is used as a positioning concave portion for fitting a positioning pin that positions the intermediate partition plate  140  with respect to a processing jig. Therefore, in the embodiment, by using the positioning concave portion as the concave portion  141  for correcting the inclination of the upper vane  127 T and the lower vane  127 S, it is not necessary to perform additional processing with respect to the concave portion  141  in the outer circumferential portion of the intermediate partition plate  140 , and an increase in manufacturing costs of the rotary compressor  1  is suppressed. 
     In addition, when casting the intermediate partition plate  140 , the concave portion  141  is formed as a part of an outer shape of the intermediate partition plate  140 . Therefore, in the concave portion  141 , a cut taper for removing the intermediate partition plate  140  from the inside of a molding die when casting the intermediate partition plate  140 , is provided. Specifically, the concave portion.  141  is formed in a tapered shape in which the depth D with respect to the radial direction of the intermediate partition plate  140  gradually decreases from the one surface side to the other surface side in the direction of the rotation shaft  15  in the intermediate partition plate  140 . Accordingly, it becomes possible to take out the intermediate partition plate  140  from the inside of the molding die during the casting. In the embodiment, since the concave portion  141  is used as the concave portion  141  for correcting the inclination of the upper vane  127 T and the lower vane  127 S, the taper is provided. Therefore, even in a case of the depth D of the concave portion  141  at the other end of the intermediate partition plate  140 , the above-described expression 1 is satisfied. 
     Effect of Embodiment. 
     As described above, in the outer circumferential portion of the intermediate partition plate  140  in the rotary compressor  1  according to the embodiment, the concave portion  141  is provided at a position at which the upper vane  127 T and the lower vane  127 S slide, and at the lower dead center of the upper piston  125 T and the lower piston  125 S, 80% or more of the entire length in the sliding direction of the upper vane  127 T and the lower vane  127 S are accommodated respectively on the inside of the upper cylinder  121 T and the inside of the lower cylinder  121 S. In addition, when the depth of the concave portion  141  is D and the entire length of this upper vane  127 T and the lower vane  127 S is L, D≥0.1×L (Expression 1) is satisfied. Accordingly, generation of a partially contact state of the upper vane  127 T and the upper piston  125 T, and a partially contact state of the lower vane  127 S and the lower piston  125 S, can be suppressed, and wear or damage of the upper vane  127 T, the lower vane  127 S, the upper piston  125 T, and the lower piston  125 S, can be suppressed. Therefore, operation reliability of the upper vane  127 T and the lower vane  127 S can be improved. 
     In addition, in the rotary compressor  1  according to the embodiment, by using the positioning concave portion for processing the intermediate partition plate  140  as the concave portion  141  for correcting the inclination of the upper vane  127 T and the lower vane  127 S, it is not necessary to perform additional processing with respect to the concave portion  141  in the outer circumferential portion of the intermediate partition plate  140 . Therefore, it is possible to suppress an increase in manufacturing costs of the rotary compressor  1 . 
     Above, the embodiments are described, but the embodiments are not limited to the above-described contents. In addition, in the above-described configuration elements, configuration elements which can be easily considered by those skilled in the art, and which are in substantially the same range, that is, a so-called equivalent range, are included. Furthermore, it is possible to appropriately combine the above-described configuration elements. Furthermore, at least any one of various omissions, replacements, and changes of the configuration elements can be performed within a range which does not depart from the scope of the embodiments.