JP2017180167A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor capable of suppressing vibrations sufficiently.SOLUTION: A compressor 100 comprises a motor 5, and a compressor body 4 having a piston 12 caused to reciprocate in a cylinder 11 by the rotation of the drive shaft 14 of the motor 5. The compressor 100 includes a plurality of vibration preventing members 6 for suppressing the vibrations of the compressor body 4, at a first region or a region at the side, on which the revolving speed of the drive shaft 14 is delayed, and at a second region or a region at the side, on which the revolving speed of the drive shaft 14 is accelerated. In the first region, a vibration preventing member 6b arranged on the side of the motor 5 more than a vibration preventing member 6a arranged on the side of the compressor body 4 is arranged at a position remote from the center G of gravity of the compressor. In the second region, a vibration preventing member 6c, which is arranged closer to the side of the compressor body 4 than a vibration preventing member 6d arranged on the side of the motor 5, is arranged at a position remote from the center of gravity G of the compressor.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a compressor.

  2. Description of the Related Art Conventionally, a compressor compresses a fluid taken from outside in a cylinder by reciprocating a piston by the rotational force of a drive shaft driven by a motor.

  In recent years, in order to save space, a direct connection type compressor in which a crankshaft fitted with a piston is directly connected to a motor to reduce the size of the entire apparatus is often used. In a direct-coupled compressor, the vibration caused by the reciprocating motion of the piston and the vibration caused by the rotational motion of the drive shaft are combined to increase the inertial force acting on the compressor, and the vibration tends to increase. , There is a tendency for deviation in the direction of vibration.

  Therefore, in the compressor, it is required to suppress vibrations that occur during operation of the motor. For example, Patent Document 1 discloses a compressor in which a plurality of vibration absorbing members are interposed between a support member that supports a motor and a compression unit that is rotationally driven by the motor and compresses fluid, and a base member. ing.

JP 2010-37961 A

  In the compressor described in Patent Document 1, although vibration can be suppressed to some extent by the vibration absorbing member, it is difficult to sufficiently absorb vibration that is biased in a predetermined direction. Patent Document 1 does not fully suggest how to suppress vibration in a direct-coupled compressor.

  Then, the objective of this invention is providing the compressor which can fully suppress a vibration.

  As a preferred embodiment of the compressor according to the present invention, a compressor having a motor and a compressor main body having a piston that reciprocates in a cylinder by rotation of a drive shaft of the motor, the compressor The vibration of the compressor body is divided into a first region that is a region where the rotational speed of the drive shaft is slow and a second region that is a region where the rotational speed of the drive shaft is fast. There are a plurality of anti-vibration members to be suppressed, and the anti-vibration members are respectively provided on the compressor main body side and the motor side in the first region and the second region with reference to the center of gravity of the compressor. At least one at a time, and in the first region, the vibration isolating member disposed on the motor side is closer to the center of gravity of the compressor than the vibration isolating member disposed on the compressor main body side. Arranged at a remote location, In this region, the vibration isolating member disposed on the compressor main body side is disposed at a position farther from the center of gravity of the compressor than the vibration isolating member disposed on the motor side. And

  As a preferred embodiment of the compressor according to the present invention, a compressor having a motor and a compressor main body having a piston that reciprocates in a cylinder by rotation of a drive shaft of the motor, the compressor Has a vibration isolating member that suppresses vibration of the compressor body, and the vibration isolating member is disposed in a first region that is a region on the side where the rotational speed of the drive shaft is slow. A vibration isolator and a second anti-vibration member, and a third anti-vibration member and a fourth anti-vibration member disposed in the second area which is an area where the rotational speed of the drive shaft increases. The first vibration isolation member and the third vibration isolation member are disposed on the compressor main body side with respect to the center of gravity of the compressor, and the second vibration isolation member is disposed on the motor side. A member and the fourth vibration isolation member are disposed, and the first vibration isolation member and the second vibration isolation member are disposed. And the third vibration isolating member and the fourth vibration isolating member are disposed asymmetrically with respect to the drive shaft, and in the rotation direction of the motor or the compression direction of the compressor body. Accordingly, the distance between the first vibration isolation member and the fourth vibration isolation member is different from the distance between the second vibration isolation member and the third vibration isolation member. Features.

  According to the present invention, the vibration of the compressor can be sufficiently suppressed by arranging the vibration isolating member in consideration of the rotation direction of the motor and the moving direction of the piston.

1 is a side view illustrating a configuration of a compressor 100 according to Embodiment 1. FIG. 1 is a schematic cross-sectional view for explaining an internal configuration of a compressor 100 according to Embodiment 1. FIG. 3 is a diagram schematically showing the magnitude of inertial force acting on the compressor 100. FIG. 4 is a perspective view for explaining a vibration state of the compressor 100 when the motor 5 is operating. FIG. It is a figure for demonstrating arrangement | positioning of the vibration isolator 6 of the compressor 100. FIG. 4 is a perspective view for explaining a vibration state of the compressor 200 when the motor 5 is operating. FIG. It is a figure for demonstrating arrangement | positioning of the vibration isolator 6e-6h of the compressor 200 which concerns on Example 2. FIG. FIG. 6 is a diagram for explaining the arrangement of vibration isolation members 6i to 6l of a compressor 300 according to a third embodiment. FIG. 6 is a diagram for explaining the arrangement of vibration isolation members 6m to 6p of a compressor 400 according to a fourth embodiment.

  Hereinafter, an embodiment of a compressor according to the present invention will be described with reference to FIGS. FIG. 1 is a side view illustrating the configuration of the compressor 100 according to the first embodiment.

  The compressor 100 includes a pedestal 2 installed horizontally on the floor surface and the bottom surfaces of various devices, a plate-like member 3 installed on the pedestal 2, and a compressor main body 4 installed on the plate-like member 3. And a motor 5 installed on the plate-like member 3. The plate-like member 3 is installed on the pedestal 2 via a plurality of vibration isolation members 6. The anti-vibration member 6 is for suppressing the vibration of the compressor body 4 and is made of, for example, a rubber-like member.

  FIG. 2 is a schematic cross-sectional view for explaining the internal configuration of the compressor 100 according to the first embodiment. In FIG. 2, the pedestal 2, the plate-like member 3, and the vibration isolation member 6 are not shown.

  The compressor body 4 includes a cylinder 11, a piston 12 installed in the cylinder 11, and a cylinder head 13 that closes the upper portion of the cylinder 11.

  The motor 5 is a drive source that rotationally drives the drive shaft 14, is housed in the motor case 51, and is provided adjacent to the side of the compressor body 4. The end of the motor 5 opposite to the compressor body 4 is covered with an end bracket 52.

  The drive shaft 14 is rotatably held at both ends by a large-diameter bearing 53 held in the bearing holding portion of the motor case 51 and a small-diameter bearing 54 held in the bearing holding portion of the end bracket 52. The rotor 56 fixed to the drive shaft 14 is rotated by the magnetic force generated by the stator 55, whereby the drive shaft 14 is rotated.

  The piston 12 is connected to the drive shaft 14 via a connecting rod 15, a crankshaft (not shown), and a flywheel balance 16. Thereby, the compressor body 4 is directly connected to the motor 5 via the drive shaft 14.

  When the drive shaft 14 is rotationally driven by the motor 5, the piston 12 reciprocates in the cylinder 11 in the direction perpendicular to the drive shaft 14 by the eccentric rotation of the crankshaft. Thereby, the piston 12 performs the compression operation of the gas sucked into the compression chamber 21 from the outside while defining the compression chamber 21 between the piston 12 and the cylinder head 13.

  The flywheel balance 16 rotates with the drive shaft 14 to reduce the reciprocating inertial force accompanying the reciprocating motion of the piston 12. The piston 12 is provided with a lip ring 17 having a sealing function, and the airtightness between the piston 12 and the cylinder 11 is maintained.

  The cylinder head 13 is disposed on a partition plate 20 provided so as to cover the upper opening of the cylinder 11. The partition plate 20 is provided with a suction port (not shown) and a discharge port (not shown) penetrating in the plate thickness direction. The partition plate 20 is provided with a plate-like suction valve (not shown) whose opening is opened and closed on the cylinder 11 side, for example, and a plate-like discharge valve whose opening is opened and closed on the cylinder head 13 side. (Not shown) is attached.

  The cylinder head 13 is a covered cylinder having a cylinder part and a lid part. The cylindrical portion is divided into two chambers by a partition wall (not shown), and a suction chamber communicating with the suction port and a discharge chamber communicating with the discharge port are formed.

  A cooling fan 18 is attached to the end of the drive shaft 14 on the piston 12 side. The compressor body 4 is covered with a resin cover 19 from the side surface on the cooling fan 18 side to the upper surface and the lower surface. The resin cover 19 is connected to the motor case 51 at the end on the motor 5 side.

  Next, the operation of the compressor body 4 when the motor 5 is operated will be described with reference to FIGS. 2 and 3.

  In the following, when the piston 12 moves in a direction away from the plate-like member 3 that is the installation surface of the vibration-proof member 6 (the upper direction in FIG. The case of the compressor 100 that compresses the gas and is driven to rotate clockwise when the drive shaft 14 is viewed from the motor 5 side will be described. 3 (1) to 3 (3) are diagrams schematically showing the magnitude of the inertial force acting on the compressor 100. FIG. 3 (1) to (3) show the compressor 100 as viewed from the compressor body 4 side. Therefore, in FIGS. 3 (1) to 3 (3), the rotation direction is counterclockwise as indicated by the arrows in the figure.

  Suction process in which a predetermined reference point of the drive shaft 14 moves from the position indicated by A1 in FIGS. 3 (1) to (3) to the position indicated by A2 in FIGS. 3 (1) to (3) in the direction of the arrow b1. Then, the piston 12 moves to the side opposite to the cylinder head 13 and reaches the bottom dead center from the top dead center. As a result, the compression chamber 21 in the cylinder 11 expands, the discharge valve remains closed, the suction valve opens, and the gas in the suction chamber of the cylinder head 13 is introduced into the compression chamber 21.

  Next, the predetermined reference point of the drive shaft 14 moves from the position indicated by A2 in FIGS. 3 (1) to (3) to the position indicated by A1 in FIGS. 3 (1) to (3) in the arrow b2 direction. In the compression process, the piston 12 moves toward the cylinder head 13 and reaches the top dead center from the bottom dead center. Thereby, the compression chamber 21 in the cylinder 11 is reduced, the suction valve is closed, the discharge valve is opened, and the gas compressed in the compression chamber 21 is discharged into the discharge chamber of the cylinder head 31.

  Next, the inertial force that acts on the compressor 100 during the operation of the compressor body 4 described above will be described. The inertial force that acts on the compressor 100 during operation of the motor 5 includes an inertial force due to reciprocating mass (see FIG. 3 (1)) and an inertial force due to rotating mass (see FIG. 3 (2)). The inertial force (see FIG. 3 (3)) that combines these works.

  FIG. 3A schematically shows the magnitude of the inertial force due to the reciprocating mass acting on the compressor 100. 3 (1) to 3 (3), the inner circle schematically shows the range of the compressor 100, and the outer curve shows the inertial force. As shown in FIG. 3 (1), due to the reciprocating mass resulting from the reciprocating motion of the piston 12, an inertial force is exerted on the compressor 100 substantially equally on the top dead center side and the bottom dead center side.

  FIG. 3B schematically shows the magnitude of the inertial force of the rotating mass that acts on the compressor 100. In the compressor 100 that compresses the gas when the piston 12 moves upward and the drive shaft 14 is driven to rotate clockwise as viewed from the motor 5 side, as shown in FIG. The inertial force due to is large on the suction process side and small on the compression process side. The reason will be described below.

  As described above, in the compressor 100, the piston 12 is connected to the drive shaft 14 of the motor 5, and the motor 5 and the compressor body 4 are directly connected by the drive shaft 14. For this reason, the load applied to the rotation of the drive shaft 14 varies greatly between the suction process side and the compression process side, and the rotation speed varies while the drive shaft 14 rotates once.

  Specifically, on the suction process side (the left side of the line A1-A2 in FIGS. 3 (1) to (3)), since the load applied to the rotation of the drive shaft 14 is small, the rotation speed increases. For this reason, as indicated by a position α in FIG. 3B, the inertial force due to the rotating mass increases on the suction step side. On the other hand, on the compression process side (the right side of the line A1-A2 in FIGS. 3 (1) to (3)), since the load applied to the rotation of the drive shaft 14 is large, the rotation speed decreases. For this reason, as shown in FIG. 3B, the inertial force due to the rotating mass is reduced on the compression process side.

  FIG. 3 (3) schematically shows the magnitude of the inertial force obtained by synthesizing the inertial force (1) and the inertial force (2). As shown in FIGS. 3 (1) to 3 (3), the inertial force due to the reciprocating mass and the inertial force due to the rotating mass are substantially opposite to each other. Further, the inertial force due to the reciprocating mass (see FIG. 3 (1)) is generally larger than the inertial force due to the rotating mass (see FIG. 3 (2)). For this reason, as shown in FIG. 3 (3), on the suction step side where the inertial force due to the rotating mass becomes larger, the resultant force with the inertial force due to the reciprocating mass becomes smaller and the inertial force due to the rotating mass becomes smaller. On the process side, the resultant force with the inertial force due to the reciprocating mass increases.

  As a result, in the compressor 100 in which the gas in the compression chamber 21 is compressed by the upward movement of the piston 12 and the drive shaft 14 is driven to rotate clockwise as viewed from the motor 5 side, the drive shaft 14 rotates once. The inertial force acting on the compressor 100 in the meantime increases in the direction indicated by the arrow C1 in FIG.

Example 1
Hereinafter, as Example 1, the gas in the compression chamber 21 is compressed by the upward movement of the piston 12, and the drive shaft 14 is driven to rotate clockwise as viewed from the motor 5 side to reciprocate the piston 12. The case of the compressor 100 will be described.

  FIG. 4 is a perspective view for explaining a vibration state of the compressor 100 when the motor 5 is in operation. In FIG. 4, an arrow C <b> 2 is a direction in which the inertial force is increased in the compressor body 4 during operation of the motor 5, and indicates the same direction as the arrow C <b> 1 shown in FIG. When the inertial force increases in the direction of the arrow C2 in the compressor main body 4 when the compressor 100 is operated, the both sides are actually based on the center of gravity (the center position of the motor 5) G of the compressor 100. The vibration in the direction indicated by the arrow D1, that is, the direction from the left front E1 to the right rear E2 of the compressor 100 increases as viewed from the compressor body 4 side.

  In the compressor 100, when viewed from the motor 5 side, a region on the left side of the drive shaft 14 (hereinafter, referred to as a left region P) among the regions divided into two with respect to the drive shaft 14 is the drive shaft 14. A first region where the rotational speed is slow, and a region on the right side of the drive shaft 14 (hereinafter referred to as right region Q) is a second region where the rotational speed of the drive shaft 14 is fast. Therefore, the arrow D1 direction shown in FIG. 4 is the direction from the compressor body 4 side of the second region (right region Q) to the motor 5 side of the first region (left region P).

  In this case, the vibration isolation member 6 is arranged as shown in FIG. FIG. 5 is a view for explaining the arrangement of the vibration isolation member 6 of the compressor 100 described in FIGS. 1 to 4 and is a view of the compressor 100 as viewed from above. As shown in FIG. 5, in the compressor 100, the vibration isolation members 6 a and 6 b are disposed in the left region P, and the vibration isolation members 6 c and 6 d are disposed in the right region Q.

  In the example shown in FIG. 5, in each of the left region P and the right region Q, one vibration isolation member 6 is disposed on each of the compressor body 4 side and the motor 5 side with reference to the center of gravity G of the compressor 100. ing. Specifically, in the left region P, a vibration isolating member 6a is disposed on the compressor body 4 side, and a vibration isolating member 6b is disposed on the motor 5 side. In the right region Q, a vibration isolating member 6c is disposed on the compressor body 4 side, and a vibration isolating member 6d is disposed on the motor 5 side.

  As shown in FIG. 5, the vibration isolating members 6 a to 6 d are arranged such that the anti-vibration member 6 a and the anti-vibration member 6 b and the anti-vibration member 6 c and the anti-vibration member 6 d are asymmetrical with respect to the drive shaft 14. ing. Specifically, in the left region P, the vibration isolation member 6b disposed in the motor 5 side region is separated from the center of gravity G of the compressor 100 rather than the vibration isolation member 6a disposed in the region on the compressor body 4 side. Placed in position. In the right region Q, the vibration isolating member 6c disposed in the region on the compressor body 4 side is disposed at a position farther from the center of gravity G of the compressor 100 than the vibration isolating member 6d disposed in the region on the motor 5 side. doing.

  In other words, the vibration isolation members 6a to 6d are arranged such that the distance L1 between the vibration isolation member 6b and the vibration isolation member 6c is different from the distance L2 between the vibration isolation member 6a and the vibration isolation member 6d. Specifically, the anti-vibration members 6a to 6d are the anti-vibration member 6b disposed in the region on the motor 5 side in the left region P, and the anti-vibration member disposed in the region on the compressor body 4 side in the right region Q. A distance L1 between the vibration isolation member 6a disposed in the region on the compressor body 4 side in the left region P, and a vibration isolation member 6d disposed in the region on the motor 5 side in the right region Q. Are arranged so as to satisfy the relationship of L1> L2.

  By arranging the vibration isolating members 6a to 6d as described above, vibration that greatly shakes in the direction of the double arrow D1 can be efficiently suppressed. For this reason, it is possible to efficiently suppress vibration that is biased in a predetermined direction while saving space as a structure in which the compressor body 4 and the motor 5 are directly connected.

(Example 2)
Next, in the second embodiment, the compressor 12 compresses the gas in the compression chamber 21 by the upward movement of the piston 12, and the drive shaft 14 is rotated counterclockwise when viewed from the motor 5 side to perform the compression operation. 200 will be described.

  In the compressor 200, as shown in FIG. 6, when the motor 5 is operated, the direction indicated by the double-headed arrow D2 with respect to the center of gravity position (center position of the motor 5) G of the compressor 200, that is, the compressor As viewed from the main body 4 side, the vibration in the direction from the right front E3 to the left rear E4 of the compressor 200 increases.

  In the compressor 200, the right region Q is a first region where the rotational speed of the drive shaft 14 is slow, and the left region P is a second region where the rotational speed of the drive shaft 14 is fast. Therefore, the arrow D2 direction shown in FIG. 6 is the direction from the compressor body 4 side of the second region (left region P) to the motor 5 side of the first region (right region Q).

  In this case, the vibration isolation member 6 is arranged as shown in FIG. FIG. 7 is a diagram for explaining the arrangement of the vibration isolation members 6e to 6h of the compressor 200 according to the second embodiment. In the compressor 200, as shown in FIG. 7, the vibration isolation members 6e and 6f are disposed in the left region P, and the vibration isolation members 6g and 6h are disposed in the right region Q.

  As shown in FIG. 7, the anti-vibration members 6 e to 6 h of the compressor 200 are arranged at positions where the anti-vibration members 6 a to 6 d (see FIG. 5) in the compressor 100 are reversed left and right around the drive shaft 14. ing. That is, in the vibration isolating members 6e to 6h, the anti-vibration member 6e and the anti-vibration member 6f, and the anti-vibration member 6g and the anti-vibration member 6h are arranged asymmetrically with the drive shaft 14 as the center.

  Specifically, in the left region P, the vibration isolating member 6e disposed in the region on the compressor body 4 side is separated from the center of gravity G of the compressor 200 rather than the vibration isolating member 6f disposed in the region on the motor 5 side. Placed in position. Further, in the right side area Q, the vibration isolating member 6h arranged in the area on the motor 5 side is arranged at a position farther from the center of gravity G of the compressor 200 than the vibration isolating member 6g arranged in the area on the compressor body 4 side. doing.

  Further, the vibration isolating members 6e to 6h include a vibration isolating member 6f disposed in the region on the motor 5 side in the left region P, and a vibration isolating member 6g disposed in the region on the compressor body 1 side in the right region Q. And a distance L2 between the vibration isolating member 6e disposed in the region on the compressor body 1 side in the left region P and the vibration isolating member 6h disposed in the region on the motor 5 side in the right region Q. , L1 <L2 are satisfied.

  By arranging the vibration isolating members 6e to 6h as described above, vibration that greatly shakes in the direction of the double arrow D2 can be efficiently suppressed. For this reason, it is possible to efficiently suppress vibration that is biased in a predetermined direction while saving space as a structure in which the compressor body 4 and the motor 5 are directly connected.

(Example 3)
Next, in Example 3, the gas in the compression chamber 21 is compressed when the piston 12 moves in a direction close to the plate-like member 3 that is the installation surface of the vibration-proof member 6 (hereinafter referred to as “downward”). In addition, a description will be given of the case of the compressor 300 in which the drive shaft 14 is rotationally driven clockwise as viewed from the motor 5 side to reciprocate the piston 12.

  The compressor 300 according to the third embodiment and the compressor 400 according to the fourth embodiment, which will be described below, are basically the same as those shown in FIG. 2 except that the piston 12 moves downward to compress the gas. Since it is the same as 100, the description is omitted.

  In the compressor 300, when the motor 5 is operated, the compressor 300 is viewed from the compressor main body 4 side with respect to the center of gravity position of the compressor 300 (center position of the motor 5). Vibration increases. In this case, the vibration isolation member 6 is arranged as shown in FIG. FIG. 8 is a diagram for explaining the arrangement of the vibration isolation members 6i to 6l of the compressor 300 according to the third embodiment.

  In the compressor 300, when viewed from the motor 5 side, a right region Q that is a region on the right side with respect to the drive shaft 14 is a first region in which the rotational speed of the drive shaft 14 is slow. On the other hand, the left region P, which is the left region, is a second region in which the rotational speed of the drive shaft 14 increases. As shown in FIG. 8, the vibration isolation members 6 i and 6 j are arranged in the left region P, and the vibration isolation members 6 k and 6 l are arranged in the right region Q.

  The anti-vibration members 6i to 6l of the compressor 300 are arranged so as to have the same positional relationship as the arrangement of the anti-vibration members 6e to 6h (see FIG. 7) in the compressor 200. Further, the vibration isolating members 6i to 6l have a distance L1 between a vibration isolating member 6j installed on the motor 5 side in the left region P and a vibration isolating member 6k disposed on the compressor main body 5 side in the right region Q, and the left side. The distance L2 between the vibration isolating member 6i disposed on the compressor body 5 side in the region P and the vibration isolating member 6l disposed on the motor 5 side in the right region Q is disposed so as to satisfy the relationship L1 <L2. ing.

  By arranging the vibration isolating members 6i to 6l as described above, it is possible to efficiently suppress vibration that greatly shakes in the direction from the right front position to the left rear position of the compressor 300 when viewed from the compressor body 4 side. . For this reason, it is possible to efficiently suppress vibration that is biased in a predetermined direction while saving space as a structure in which the compressor body 4 and the motor 5 are directly connected.

Example 4
Next, in the fourth embodiment, the gas in the compression chamber 21 is compressed by the downward movement of the piston 12, and the drive shaft 14 is driven to rotate counterclockwise as viewed from the motor 5 side to reciprocate the piston 12. The case of the compressor 400 to be performed will be described with reference to FIG.

  In the compressor 400, when the motor 5 is operated, the center of gravity of the compressor 400 (the center position of the motor 5) is used as a reference when viewed from the compressor body 4 side in the direction from the left front to the right rear of the compressor 400. Vibration increases. In this case, the vibration isolation member 6 is arranged as shown in FIG. FIG. 9 is a diagram for explaining the arrangement of the vibration isolation members 6m to 6p of the compressor 400 according to the fourth embodiment.

  In the compressor 400, when viewed from the motor 5 side, the left side region P that is the left side region with respect to the drive shaft 14 is a first region in which the rotational speed of the drive shaft 14 is slow. On the other hand, the right area Q, which is the right area, is a second area in which the rotational speed of the drive shaft 14 increases. As shown in FIG. 9, the anti-vibration members 6m and 6n are disposed in the left region P, and the anti-vibration members 6o and 6p are disposed in the right region Q.

  The anti-vibration members 6m to 6p of the compressor 300 are arranged so as to have the same positional relationship as the arrangement of the anti-vibration members 6a to 6d (see FIG. 5) in the compressor 100. Further, the vibration isolating members 6m to 6p have a distance L1 between the vibration isolating member 6n installed on the motor 5 side in the left side region P and the vibration isolating member 6o arranged on the compressor body 4 side in the right side region Q, and the left side. The distance L2 between the vibration isolating member 6m disposed on the compressor body 4 side in the region P and the vibration isolating member 6p disposed on the motor 5 side in the right region Q is disposed so as to satisfy the relationship L1> L2. ing.

  By arranging the vibration isolating members 6m to 6p as described above, it is possible to efficiently suppress vibration that greatly shakes in the direction from the left front position to the right rear position of the compressor 400 when viewed from the compressor body 4 side. . For this reason, it is possible to efficiently suppress vibration that is biased in a predetermined direction while saving space as a structure in which the compressor body 4 and the motor 5 are directly connected.

  In the first to fourth embodiments described above, an example in which one vibration isolation member 6 is disposed on the compressor body 4 side and the motor 5 side in the left region P and the right region Q, respectively. In the left region P and the right region Q, a plurality of members 6 may be arranged on the compressor body 4 side and the motor 5 side, respectively.

  Moreover, in Examples 1-4, although the case where gas was compressed in the cylinder 11 was demonstrated to the example, the compression object may be a liquid.

DESCRIPTION OF SYMBOLS 100-400 ... Compressor, 2 ... Base, 3 ... Plate-shaped member, 4 ... Compressor main body, 5 ... Motor, 6, 6a-6p ... Vibration isolator, 11 ... Cylinder, 12 ... Piston, 13 ... Cylinder head, DESCRIPTION OF SYMBOLS 14 ... Drive shaft, 15 ... Connecting rod, 16 ... Flywheel balance, 17 ... Lip ring, 18 ... Cooling fan, 19 ... Resin cover, 20 ... Partition plate, 21 ... Compression chamber, 51 ... Motor case, 52 ... End bracket 53, 54 ... bearings, 55 ... stator, 56 ... rotor, A1, A2 ... position, b1, b2, C1, C2 ... arrows, D1, D2 ... double arrows, E1 ... left front of the compressor 100, E2 ... compressor 100 right, E3 ... front right of compressor 200, E4 ... left rear of compressor 200, L1, L2 ... distance, G ... center of gravity of compressor 100, P ... left region, Q ... right region, α ... position

Claims (9)

A motor,
A compressor body including a piston that reciprocates in a cylinder by rotation of a drive shaft of the motor,
The compressor has a main body of the compressor in a first region that is a region where the rotational speed of the drive shaft is slow and a second region that is a region where the rotational speed of the drive shaft is fast. A plurality of vibration-proof members that suppress vibrations of
The vibration isolating member is disposed at least one each on the compressor main body side and the motor side with respect to the center of gravity of the compressor in the first region and the second region,
In the first region, the vibration isolating member disposed on the motor side is disposed at a position farther from the center of gravity of the compressor than the vibration isolating member disposed on the compressor main body side. In the second region, the vibration isolating member disposed on the compressor main body side is disposed at a position farther from the center of gravity of the compressor than the vibration isolating member disposed on the motor side. The compressor characterized by having. A motor,
A compressor body including a piston that reciprocates in a cylinder by rotation of a drive shaft of the motor,
The compressor has a vibration isolating member that suppresses vibration of the compressor body,
The anti-vibration member includes a first anti-vibration member and a second anti-vibration member disposed in a first region which is a region where the rotation speed of the drive shaft is slow, and the rotation speed of the drive shaft is A third vibration isolating member and a fourth vibration isolating member disposed in the second region, which is the region on the speed increasing side,
The first vibration isolation member and the third vibration isolation member are disposed on the compressor main body side with respect to the center of gravity of the compressor, and the second vibration isolation member and the second vibration isolation member are disposed on the motor side. 4 anti-vibration members are arranged,
The first vibration isolation member and the second vibration isolation member, the third vibration isolation member and the fourth vibration isolation member are disposed asymmetrically with respect to the drive shaft; and Depending on the rotation direction of the motor or the compression direction of the compressor body, the distance between the first vibration isolation member and the fourth vibration isolation member, the second vibration isolation member, and the third vibration isolation member. A compressor characterized by being arranged with a different distance from a vibration member. When the piston moves in a direction away from the installation surface of the vibration isolation member to compress the fluid in the cylinder, and the drive shaft is driven to rotate clockwise as viewed from the motor side,
The first region is a region on the left side of the drive shaft when viewed from the motor side, and the second region is relative to the drive shaft when viewed from the motor side. The compressor according to claim 1, wherein the compressor is a right region. When the piston moves in a direction away from the installation surface of the vibration isolation member to compress the fluid in the cylinder, and the drive shaft is driven to rotate counterclockwise as viewed from the motor side ,
The first region is a region on the right side of the drive shaft when viewed from the motor side, and the second region is relative to the drive shaft when viewed from the motor side. The compressor according to claim 1, wherein the compressor is a left region. When the piston moves in a direction close to the installation surface of the vibration isolation member to compress the fluid in the cylinder, and the drive shaft is driven to rotate clockwise as viewed from the motor side,
The first region is a region on the right side of the drive shaft when viewed from the motor side, and the second region is relative to the drive shaft when viewed from the motor side. The compressor according to claim 1, wherein the compressor is a left region. A distance L1 between the vibration isolating member installed on the motor side in the left region and the vibration isolating member disposed on the compressor body side in the right region;
The distance L2 between the vibration isolating member disposed on the compressor body side in the left region and the vibration isolating member disposed on the motor side in the right region satisfies the relationship L1 <L2. The compressor according to claim 4 or 5, characterized by these. When the piston moves in a direction close to the installation surface of the vibration isolation member to compress the fluid in the cylinder, and the drive shaft is driven to rotate counterclockwise as viewed from the motor side ,
The first region is a region on the left side of the drive shaft when viewed from the motor side, and the second region is relative to the drive shaft when viewed from the motor side. The compressor according to claim 1, wherein the compressor is a right region. A distance L1 between the vibration isolating member installed on the motor side in the left region and the vibration isolating member disposed on the compressor body side in the right region;
A distance L2 between the vibration isolating member disposed on the compressor main body side in the left region and the vibration isolating member disposed on the motor side in the right region is L1> L2. The compressor according to claim 3 or 7.   The compressor according to claim 1, wherein the piston is connected to a drive shaft of the motor.

Images