JP2006200527A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor suppressing shaking motion of a rotor and reducing vibration and noise of the rotor during operation. <P>SOLUTION: A compression part is driven by the rotor 6 of a motor via a driving shaft 12. One end part of the driving shaft 12 is supported by the compression part, and the rotor 6 is mounted to the other end part of the driving shaft 12 which is a free end side. A first balance weight 71 is provide on an end face of the rotor 6 which is the free end of the driving shaft 12. A center 12a of the driving shaft 12 is displaced in the first balance weight 71 side with respect to a center 6a of the rotor 6. During operation of the compressor, eccentric amount of the center 6a of the rotor 6 is approximately balanced with movement amount of the rotor 6 caused by deformation of the driving shaft 12. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a compressor such as a rotary compressor used in, for example, an air conditioner.

  Conventionally, the compressor has driven the compression part by the rotor of the motor via the drive shaft. One end portion of the drive shaft is supported by the housing of the compression portion, and the other end portion on the free end side of the drive shaft is attached with the rotor. An eccentric pin for fitting the roller of the compression unit is provided at one end of the drive shaft.

  A first balance weight is provided on the end surface of the rotor far from the eccentric pin on the same side as the eccentric pin with respect to the drive shaft. A second balance weight is provided on the end face of the rotor near the eccentric pin on the side opposite to the first balance weight with respect to the drive shaft.

  As shown in FIG. 4, the center of the rotor 102 and the center of the drive shaft 101 are concentric when viewed from the other end (free end side) of the drive shaft 101 (Japanese Patent Laid-Open No. Hei 6-2689). : Patent Document 1).

  However, in the conventional compressor, as shown in FIG. 4, the center of the rotor 102 and the center of the drive shaft 101 are concentric, so that the rotation of the rotor 102 during operation of the compressor As shown in the direction of arrow A, the centrifugal force of the first balance weight 103 is generated.

The centrifugal force of the first balance weight 103 causes the rotor 102 to swing while the free end side of the drive shaft 101 is bent. Due to the swing of the rotor 102, vibration and noise are generated in the rotor 102.
Japanese Patent Laid-Open No. 6-2687 (FIG. 12)

  SUMMARY OF THE INVENTION An object of the present invention is to provide a compressor that suppresses the vibration of the rotor during operation and reduces the vibration and noise of the rotor.

In order to solve the above problems, the compressor of the present invention is:
A compression portion, a motor, and a drive shaft having an eccentric pin on the compression portion side with respect to the motor, and a rotor of the motor provided on the free end side;
By setting the center of the drive shaft between the first balance weight provided on the axial front end side of the rotor and the center of the rotor, the drive shaft is driven by the centrifugal force of the first balance weight. It is characterized by reducing bending.

  According to the compressor of the present invention, the first balance is set by setting the center of the drive shaft between the first balance weight provided on the axial front end side of the rotor and the center of the rotor. Since the deflection of the drive shaft due to the centrifugal force of the weight is reduced, the swinging of the rotor is suppressed, and the vibration and noise of the rotor are reduced.

The compressor of the present invention is
In the compressor in which the drive shaft is bent by the rotation of the rotor of the motor provided on the free end side of the drive shaft having an eccentric pin fitted to the roller of the compression unit,
By setting the center of the drive shaft between the first balance weight provided on the axial front end side of the rotor and the center of the rotor, the drive shaft is driven by the centrifugal force of the first balance weight. It is characterized by reducing bending.

  According to the compressor of the present invention, the first balance is set by setting the center of the drive shaft between the first balance weight provided on the axial front end side of the rotor and the center of the rotor. Since the deflection of the drive shaft due to the centrifugal force of the weight is reduced, the swinging of the rotor is suppressed, and the vibration and noise of the rotor are reduced.

The compressor of the present invention is
The drive shaft on both sides of the eccentric pin fitted to the roller of the compression portion is supported by the housing of the compression portion, and the rotor of the motor is attached to the free end side of the drive shaft, and the rotor on the side far from the compression portion The first balance weight provided on the end face side of the rotor is installed in the same direction as the eccentric direction of the eccentric pin, while the second balance weight provided on the end face side of the rotor on the side close to the compression portion is In the compressor installed in the direction opposite to the eccentric direction of the eccentric pin,
The center of the drive shaft is displaced toward the first balance weight side with respect to the center of the rotor.

  According to the compressor of the present invention, during the operation of the compressor, the rotor rotates about a position away from the center of the drive shaft due to the deflection of the drive shaft. At this time, since the center of the drive shaft is displaced to the first balance weight side with respect to the center of the rotor, the amount of movement due to the deflection of the drive shaft of the rotor and the eccentricity of the center of the rotor The amount is almost balanced.

  Thus, during the operation of the compressor, the amount of movement due to the deflection of the drive shaft of the rotor is canceled by the amount of eccentricity of the center of the rotor, and the center of the rotor becomes the rotation center of the rotor. The vibration of the rotor and the noise are reduced.

  According to the compressor of the present invention, since the center of the drive shaft is displaced toward the first balance weight side with respect to the center of the rotor, the rotor swings during operation of the compressor. The vibration and noise of the rotor are reduced.

  Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments.

(First embodiment)
FIG. 1 is a front sectional view showing a first embodiment of a compressor according to the present invention. This compressor is a so-called high-pressure dome-type rotary compressor, and has a casing 1 with a compression section 2 on the bottom and a motor 3 on the top. The compressor 6 is driven by the rotor 6 of the motor 3 via the drive shaft 12.

  The compression unit 2 sucks refrigerant gas through an intake pipe 11 from an accumulator (not shown). The refrigerant gas is obtained by controlling a condenser, an expansion mechanism, and an evaporator (not shown) that constitute an air conditioner as an example of a refrigeration system together with the compressor.

  The compressor discharges the compressed high-temperature and high-pressure discharge gas from the compression unit 2 to fill the inside of the casing 1, and passes the motor 3 through the gap between the stator 5 and the rotor 6 of the motor 3. After cooling, it is discharged from the discharge pipe 13 to the outside. Lubricating oil 9 is stored in the lower portion of the high pressure region in the casing 1.

  The compression unit 2 includes a cylinder body 21, and an upper end plate member 50 and a lower end plate member 60 that are attached to the upper and lower opening ends of the cylinder body 21. A cylinder chamber 22 is formed by the cylinder body 21, the upper end plate member 50, and the lower end plate member 60.

  The upper end plate member 50 includes a disk-shaped main body 51 and a boss 52 provided upward in the center of the main body 51. The main body 51 and the boss 52 are inserted through the drive shaft 12. The main body 51 is provided with the discharge port 51 a communicating with the cylinder chamber 22.

  A discharge valve 31 is attached to the main body 51 so as to be located on the opposite side of the main body 51 from the cylinder main body 21. The discharge valve 31 is, for example, a reed valve, and opens and closes the discharge port 51a.

  A cup-type muffler main body 40 is attached to the main body 51 so as to cover the discharge valve 31. The muffler main body 40 is fixed to the main body 51 by a fixing member 35 (such as a bolt). The muffler body 40 is inserted through the boss portion 52.

  The muffler body 42 and the upper end plate member 50 form a muffler chamber 42. The muffler chamber 42 and the cylinder chamber 22 communicate with each other via the discharge port 51a.

  The muffler main body 40 has a hole 43. The hole 43 communicates the muffler chamber 42 with the outside of the muffler main body 40.

  The lower end plate member 60 includes a disc-shaped main body portion 61 and a boss portion 62 provided downward in the center of the main body portion 61. The main body 61 and the boss 62 are inserted through the drive shaft 12.

  In short, one end of the drive shaft 12 is supported by the upper end plate member 50 and the lower end plate member 60. That is, the drive shaft 12 is cantilevered. One end portion (support end side) of the drive shaft 12 enters the cylinder chamber 22.

  An eccentric pin 26 is provided on the support end side of the drive shaft 12 so as to be located in the cylinder chamber 22 on the compression portion 2 side. The eccentric pin 26 is fitted to the roller 27. The roller 27 is disposed so as to be able to revolve in the cylinder chamber 22, and performs a compression action by the revolving motion of the roller 27.

  In other words, one end portion of the drive shaft 12 is supported by the housing 7 of the compression portion 2 on both sides of the eccentric pin 26. The housing 7 includes the upper end plate member 50 and the lower end plate member 60.

  Here, the compression action of the cylinder chamber 22 will be described.

  As shown in FIG. 2, the cylinder chamber 22 is partitioned by a blade 28 provided integrally with the roller 27. That is, the chamber on the right side of the blade 28 has the suction pipe 11 opened on the inner surface of the cylinder chamber 22 to form a suction chamber (low pressure chamber) 22a. On the other hand, in the chamber on the left side of the blade 28, the discharge port 51a (shown in FIG. 1) opens on the inner surface of the cylinder chamber 22 to form a discharge chamber (high pressure chamber) 22b.

  Semi-circular bushes 25, 25 are in close contact with both surfaces of the blade 28 for sealing. Lubrication is performed between the blade 28 and the bushes 25, 25 with the lubricating oil 9.

  The eccentric pin 26 rotates eccentrically together with the drive shaft 12, and the roller 27 fitted to the eccentric pin 26 contacts the outer peripheral surface of the roller 27 with the inner peripheral surface of the cylinder chamber 22. , Revolve.

  As the roller 27 revolves in the cylinder chamber 22, the blade 28 advances and retreats with both side surfaces of the blade 28 being held by the bushes 25, 25. Then, a low-pressure refrigerant gas is sucked into the suction chamber 22a from the suction pipe 11 and compressed to a high pressure in the discharge chamber 22b. Discharge.

  Thereafter, as shown in FIG. 1, the refrigerant gas discharged from the discharge port 51 a is discharged to the outside of the muffler main body 40 through the muffler chamber 52.

  As shown in FIG. 1, the rotor 6 is attached to the other end which is the free end side of the drive shaft 12. A first balance weight 71 is provided on the end surface of the rotor 6 on the side far from the eccentric pin 26. That is, the first balance weight 71 is attached to the end surface of the rotor 6 opposite to the end surface of the rotor 6 facing the compression portion 2. The first balance weight 71 is located on the same side as the center of the eccentric pin 26 with respect to the drive shaft 12. That is, the first balance weight 71 is eccentric in the same direction as the eccentric direction of the eccentric pin 26.

  A second balance weight 72 is provided on the end face of the rotor 6 on the side close to the eccentric pin 26. That is, the second balance weight 72 is attached to the end surface of the rotor 6 that faces the compression section 2. The second balance weight 72 is located on the side opposite to the first balance weight 71 with respect to the drive shaft 12. That is, the second balance weight 72 is installed in a direction opposite to the eccentric direction of the eccentric pin 26.

  As shown in FIG. 3, the first balance weight 71 is formed in a substantially arc shape. Although not shown, the second balance weight 72 is also formed in a substantially arc shape.

  The center 12a of the drive shaft 12 is displaced toward the first balance weight 71 with respect to the center 6a of the rotor 6. In FIG. 3, for easy understanding, the distance between the center 6a of the rotor 6 and the center 12a of the drive shaft 12 (the eccentric amount of the center 6a of the rotor 6) is exaggerated. Further, the position of the conventional drive shaft 101 is indicated by a virtual line.

  During the operation of the compressor, the center (shaft) 12a of the drive shaft 12 is bent by the centrifugal force (in the direction of arrow B) of the first balance weight 71 generated by the rotation of the rotor 6. Move in the direction of the balance weight 71. At this time, the amount of movement of the center 12a of the drive shaft 12 is substantially balanced with the distance between the center 6a of the rotor 6 and the center 12a of the drive shaft 12 (the amount of eccentricity of the center 6a of the rotor 6).

  Therefore, during the operation of the compressor, the center 6a of the rotor 6 becomes the rotation center of the rotor 6, so that the swinging of the rotor 6 is suppressed and the vibration and noise of the rotor 6 are reduced. That is, by setting the center 12a of the drive shaft 12 between the first balance weight 71 provided on the axial front end side of the rotor 6 and the center 6a of the rotor 6, the first balance is set. The bending of the drive shaft 12 due to the centrifugal force of the weight 71 is reduced.

  In short, the amount of eccentricity of the center 6a of the rotor 6 is an amount that corrects the deflection of the drive shaft 12. More specifically, the amount of eccentricity of the center 6a of the rotor 6 is the amount of deflection of the drive shaft 12 at the operation frequency at which the product value of the operation frequency and the number of poles + 1 matches the natural frequency of the rotor 6. For example, the amount of eccentricity is several μm to less than 1 mm. Note that, in a normal rotary type compressor, even if the eccentricity is several μm to 200 μm, the deflection of the drive shaft 12 can be corrected. The eccentric direction of the rotor 6 is a direction for canceling the amount of bending of the drive shaft 12.

  Thus, in the present invention, at the operating frequency at which the natural frequency of the rotor 6 and the frequency of the excitation force generated by the swing match, the swinging of the rotor 6 is suppressed and the excitation force is reduced. The vibration and noise of the rotor 6 are reduced.

  In contrast, in the conventional example shown in FIG. 4, the center of the rotor 102 and the center of the drive shaft 101 are concentric, so that the drive shaft 101 is bent during the operation of the compressor. The rotor 102 swings around. The swinging motion of the rotor 102 generates an exciting force having a frequency that is a product of the operating frequency and the number of poles + 1. When the excitation force matches the natural frequency of the rotor 102, the rotor 102 resonates and noise is generated.

(Second Embodiment)
FIG. 5 shows a second embodiment of the compressor of the present invention. The difference from the first embodiment (FIG. 1) will be described. In the second embodiment, the configuration of the compression unit and the positional relationship between the compression unit and the motor are different. Note that the same reference numerals as those in the first embodiment in FIG. 1 have the same configurations as those in the first embodiment, and thus description thereof is omitted.

  In the casing 1, the motor 3 and the compression unit 220 are arranged in order from the bottom to the top.

  The motor 3 is disposed in a region in the casing 1 where the low-pressure refrigerant gas to be sucked into the compression unit 220 is filled. Specifically, the inside of the casing 1 is partitioned into a high pressure region H and a low pressure region L with the compression unit 220 interposed therebetween, and the motor 3 is disposed in the low pressure region L. This compressor is a so-called low-pressure dome type.

  The compression unit 3 includes a main body 221 attached to the casing 1, a fixed scroll 222 fixed and supported by the main body 221, and a turning scroll 223 that meshes with the fixed scroll 222.

  The main body 221 holds one end of the drive shaft 212 while inserting the drive shaft 212 fixed to the rotor 6 of the motor 3 through a bearing, for example. The fixed scroll 222 has a spiral wrap on the end plate, and meshes with the orbiting scroll 223 to form a plurality of compression chambers 224.

  The orbiting scroll 223 is attached to an eccentric pin 226 at one end of the drive shaft 212 so as to freely rotate and revolves as the drive shaft 212 rotates.

  The main body 221 has a suction hole 221 a that communicates the low pressure region L and the compression chamber 224, and the fixed scroll 222 has a discharge hole 222 a that communicates the high pressure region H and the compression chamber 224. .

  A first balance weight 271 is provided on the front end side (lower end) of the rotor 6 of the motor 3 in the same direction as the eccentric direction of the eccentric pin 226 with respect to the center 212 a of the drive shaft 212.

  On the eccentric pin 226 side of the drive shaft 212, a second balance weight 272 is provided in a direction opposite to the eccentric direction of the eccentric pin 226 with respect to the center 212a of the drive shaft 212.

  Similarly to the first embodiment, a center 212 a of the drive shaft 212 is set between the first balance weight 271 and the center 6 a of the rotor 6.

  The casing 1 is provided with a refrigerant gas suction pipe 11 and a refrigerant gas discharge pipe 13. The suction pipe 11 opens to the low pressure region L between the stator 21 of the motor 3 and the compression unit 3. The discharge pipe 13 is open to the high pressure region H.

  Next, the operation of the compressor will be described.

  The refrigerant gas is sucked into the low pressure region L in the casing 1 from the suction pipe 11, sucked into the compression chamber 224 through the suction hole 221 a, and compressed by the operation of the motor 3. The compressed refrigerant gas is discharged from the discharge hole 222a to the high-pressure region H in the casing 1 and discharged from the discharge pipe 13 to the outside of the casing 1.

  According to the scroll type compressor having the above configuration, since the center 212a of the drive shaft 212 is set between the first balance weight 271 and the center 6a of the rotor 6, the first balance is set. The bending of the drive shaft 212 due to the centrifugal force of the weight 271 is reduced. Therefore, the whirling of the rotor 6 is suppressed, and the vibration and noise of the rotor 6 are reduced.

(Third embodiment)
FIG. 6 shows a third embodiment of the compressor of the present invention. The difference from the first embodiment (FIG. 1) will be described. In the third embodiment, the configuration of the compression unit is different. Note that the same reference numerals as those in the first embodiment in FIG. 1 have the same configurations as those in the first embodiment, and thus description thereof is omitted.

  The compression section 320 of the third embodiment includes a cylinder body 321, a piston 322 that is movably fitted in a cylinder chamber 321 a of the cylinder body 321, and a connecting rod 323 connected to the piston 322.

  One end of the connecting rod 323 is connected to the piston 322, and the other end of the connecting rod 323 is connected to a drive shaft 212 fixed to the rotor 6 of the motor 3.

  The drive shaft 312 has an eccentric pin 326 at the end of the rotor 6 on the compression unit 320 side. The other end of the connecting rod 323 is connected to the eccentric pin 326. That is, the connecting rod 323 converts the rotational motion of the drive shaft 312 into the reciprocating linear motion of the piston 322.

  A first balance weight 371 is provided on the tip side (upper end) of the rotor 6 of the motor 3 in the same direction as the eccentric direction of the eccentric pin 326 with respect to the center 312 a of the drive shaft 312.

  On the base end side (lower end) of the rotor 6 of the motor 3, a second balance weight 372 is provided in the direction opposite to the eccentric direction of the eccentric pin 326 with respect to the center 312 a of the drive shaft 312.

  As in the first embodiment, the center 312a of the drive shaft 312 is set between the first balance weight 371 and the center 6a of the rotor 6.

  Next, the operation of the compressor will be described.

  When the piston 322 moves from the bottom dead center position to the top dead center position in the cylinder chamber 321a, the refrigerant gas is sucked into the cylinder chamber 321a. Thereafter, when the piston 322 moves from the top dead center position to the bottom dead center position, the refrigerant gas is compressed in the cylinder chamber 321a and discharged to the outside of the cylinder chamber 321a.

  The refrigerant gas is sucked into the cylinder chamber 321a by a valve attached to the cylinder body 321 so as to open when the cylinder chamber 321a is under negative pressure. On the other hand, the refrigerant gas is discharged from the cylinder chamber 321a by a valve attached to the cylinder body 321 so as to open when the cylinder chamber 321a is at a positive pressure.

  According to the reciprocating type compressor having the above configuration, since the center 312a of the drive shaft 312 is set between the first balance weight 371 and the center 6a of the rotor 6, the first balance is set. The bending of the drive shaft 312 due to the centrifugal force of the weight 371 is reduced. Therefore, the whirling of the rotor 6 is suppressed, and the vibration and noise of the rotor 6 are reduced.

  In addition, this invention is not limited to the above-mentioned embodiment. For example, at least one of the first balance weights 71, 271, 371 and the second balance weights 72, 272, 372 may be provided on the drive shafts 12, 212, 312.

It is a front sectional view showing a 1st embodiment of a compressor of the present invention. It is a top view of the principal part of a compressor. It is a top view of the rotor seen from the free end side of the drive shaft of a compressor. It is a top view of the rotor seen from the free end side of the drive shaft of the conventional compressor. It is front sectional drawing which shows 2nd Embodiment of the compressor of this invention. It is front sectional drawing which shows 3rd Embodiment of the compressor of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Casing 2,220,320 Compression part 3 Motor 5 Stator 6 Rotor 6a (Rotor) center 7 Housing 9 Lubricating oil 12, 212, 312 Drive shaft 12a, 212a, 312a (Drive shaft) center 21 Cylinder body 22 Cylinder chamber 22a Suction chamber 22b Discharge chamber 25 Bushing 26, 226, 326 Eccentric pin 27 Roller 28 Blade 31 Discharge valve 40 Muffler body 42 Muffler chamber 43 Hole 50 (Upper) end plate member 51 Body 51a Discharge port 52 Boss 60 (Lower) end plate member 61 main body 62 boss 71 271 371 first balance weight 72 272 372 second balance weight 221 main body 222 fixed scroll 223 orbiting scroll 224 compression chamber 321 cylinder main body 321a cylinder Room 322 Ston 323 connecting rod

Claims (3)

A compression part (2, 220, 320), a motor (3), and a rotor (6) of the motor (3) are provided on the free end side, and the compression part (2, 220, 320) with respect to the motor (3). A drive shaft (12, 212, 312) having an eccentric pin (26, 226, 326) on the side;
Between the first balance weights (71, 271 and 371) provided on the axial front end side of the rotor (6) and the center (6a) of the rotor (6), the drive shafts (12, 212 and 312) are arranged. ) Center (12a, 212a, 312a) is set to reduce the bending of the drive shaft (12, 212, 312) due to the centrifugal force of the first balance weight (71, 271, 371). A compressor characterized by that. When the rotor (6) of the motor (3) provided on the free end side of the drive shaft (12) having the eccentric pin (26) fitted to the roller (27) of the compression section (2) rotates, the drive In the compressor in which the shaft (12) is bent,
The center (12a) of the drive shaft (12) is set between the first balance weight (71) provided on the front end side in the axial direction of the rotor (6) and the center (6a) of the rotor (6). By doing this, the bending of the said drive shaft (12) by the centrifugal force of the said 1st balance weight (71) was reduced, The compressor characterized by the above-mentioned. The drive shaft (12) on both sides of the eccentric pin (26) fitted to the roller (27) of the compression portion (2) is supported by the housing (7) of the compression portion (2), while the drive shaft (12) The rotor (6) of the motor (3) is attached to the free end of the first balance weight (71) provided on the end face side of the rotor (6) far from the compression section (2). While being installed in the same direction as the eccentric direction of the eccentric pin (26), the second balance weight (72) provided on the end face side of the rotor (6) on the side close to the compression part (2) is provided with the eccentricity. In the compressor installed in the direction opposite to the eccentric direction of the pin (26),
The compressor characterized in that the center (12a) of the drive shaft (12) is displaced toward the first balance weight (71) with respect to the center (6a) of the rotor (6).

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