JP2003049903A - Dynamic damper and rotary machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a dynamic damper for preventing the lowering of vibration suppressing effect due to the influence of an external magnetic source on a mass which performs pendular movement. SOLUTION: A hub 44 constituting an electromagnetic clutch part 17 having a solenoid coil 43, fixed to the front end of a driving shaft 16, is provided with a damper part 50. The damper part 50 is formed with a plurality of recessed portions 51 each of which stores a roller 53. The roller 53 is moved along a rolling guide surface 52 of the recessed portion 51 to perform pendular movement. The pendular movement suppresses the rotational vibration of the driving shaft 16, generated during the rotation. The roller 53 is formed at a stainless steel (a non-magnetic material). Thus, the effective vibration suppressing effect with the pendular movement is achieved without receiving the influences of magnetic force generated by the solenoid coil 43.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dynamic damper and a rotary machine equipped with the dynamic damper.

[0002]

2. Description of the Related Art Conventionally, in order to suppress vibration of a rotary machine such as a compressor, a damper mechanism for suppressing torque fluctuation of a rotary shaft that rotationally drives the rotary machine is sometimes used. As this damper mechanism, for example, Japanese Patent Laid-Open No.
000-213600 and Japanese Patent Laid-Open No. 2000-27448.
A configuration in which a mass body (mass) reciprocates (performs a pendulum motion) along an arcuate locus as disclosed in Japanese Patent Laid-Open Publication No. 9-90 is adopted. Generally, this damper mechanism is provided by using a pulley for transmitting a driving force from an external drive source to the rotary shaft of the rotary machine.

[0003]

However, in many cases, the pulley is provided with an electromagnetic clutch for connecting and disconnecting the power transmission between the external drive source and the rotary shaft. In this case, the mass body is magnetic. When composed of a body, the pendulum movement is affected by the magnetic force generated by the electromagnetic clutch and the like. When the pendulum motion of the mass body is disturbed by the influence of this magnetic force, the damper mechanism cannot perform a predetermined vibration suppressing action, and the vibration suppressing effect in the rotary machine is reduced. In the configurations disclosed in both of the above publications, no consideration is given to the above problems.

A first object of the present invention is to provide a dynamic damper capable of preventing the vibration suppressing effect from being lowered due to the influence of an external magnetic force source on the mass body which performs the pendulum motion. A second object is to provide a rotary machine equipped with the dynamic damper.

[0005]

In order to solve the above problems, the invention according to claim 1 is provided in a rotating body, and is provided with a point separated from the center axis of rotation of the rotating body by a predetermined distance. A gist of the present invention is a dynamic damper having a mass body that passes through and performs a pendulum motion about an axis substantially parallel to the rotation center axis, wherein the mass body is made of a non-magnetic material.

According to the present invention, the vibration generated in the rotating body due to the pendulum movement of the mass body is suppressed. Since the mass body is a non-magnetic body, the pendulum motion is not disturbed by the influence of an external magnetic source. That is, it is possible to prevent the vibration suppressing effect from being lowered due to the influence of the external magnetic source.

According to a second aspect of the present invention, in the first aspect of the present invention, the mass body moves along a guide surface having an arcuate cross section of a guide portion provided on the rotating body. The main point is to perform a pendulum exercise.

According to the present invention, it is not necessary to pivot the mass body in order to cause the mass body to perform the pendulum motion. Therefore, the structure is simple as compared with the structure in which the mass body is supported. Further, as compared with the structure in which the mass body is pivotally supported, the pendulum movement center (fulcrum) of the mass body due to the existence of a gap between the support shaft and the shaft hole of the mass body through which the support shaft is inserted, There is no change in the distance from the center of gravity. Therefore, the suppression of vibration is
Better done.

A third aspect of the invention is characterized in that, in the first or second aspect of the invention, the non-magnetic material is stainless steel or copper. According to the invention, the mass is made of stainless steel or copper. Stainless steel and copper are relatively inexpensive and have a large specific gravity, and are suitable as a non-magnetic material for a mass body that performs pendulum motion.

The invention according to a fourth aspect is summarized as including the dynamic damper according to any one of the first to third aspects. According to this invention, in the rotary machine,
It is possible to obtain the effects of the invention according to any one of claims 1 to 3.

According to a fifth aspect of the invention, in the invention according to the fourth aspect, the dynamic damper is provided in an electromagnetic clutch portion arranged on a power transmission path between the main body of the rotating machine and an external drive source. That is the summary.

According to the present invention, the dynamic damper is provided in the electromagnetic clutch section. Since the mass body of the dynamic damper is made of a non-magnetic body, the pendulum motion is not disturbed by the influence of the magnetic force generated by the electromagnetic clutch section. That is, in the rotary machine, it is not necessary to install the dynamic damper separately from the electromagnetic clutch unit, and the degree of freedom in installing the dynamic damper is increased.

A sixth aspect of the present invention is, in the fourth or fifth aspect, a gist of having a compression mechanism for performing a compression action of the refrigerant. According to the present invention, in the rotary machine having the compression mechanism for performing the compression action of the refrigerant,
The effect of the invention described in claim 4 or 5 can be obtained.

[0014]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of the present invention will be described below with reference to FIG.
2 and FIG. In FIG. 1, the left side of the drawing is the front of the compressor and the right side of the drawing is the rear.

As shown in FIG. 1, a compressor C as a main body of a rotary machine includes a cylinder block 11, a front housing 12 joined and fixed to a front end thereof, and a valve forming body 13 at a rear end of the cylinder block 11. And a rear housing 14 that is joined and fixed. Cylinder block 1
1, the front housing 12, the valve forming body 13, and the rear housing 14 form a housing of the compressor C.

A crank chamber 15 is defined in a region surrounded by the cylinder block 11 and the front housing 12. A drive shaft 16 as a rotary shaft arranged so as to pass through the crank chamber 15 is rotatably supported in the housing.

The front end portion of the drive shaft 16 is arranged so as to penetrate the front wall of the front housing 12 and project to the outside. The front end portion of the drive shaft 16 is connected to an external drive source via an electromagnetic clutch portion 17 described later and a belt 18 mounted on the electromagnetic clutch portion 17 (specifically, a pulley 42 forming the electromagnetic clutch portion 17). Is operatively connected to the vehicle engine E.

A lug plate 19 is integrally rotatably fixed to the drive shaft 16 in the crank chamber 15. A swash plate 20 as a cam plate is housed in the crank chamber 15. The swash plate 20 is supported so as to be slidable and tiltable with respect to the drive shaft 16. Swash plate 20
Are operatively connected to the lug plate 19 via a hinge mechanism 21. The swash plate 20 can rotate synchronously with the lug plate 19 and the drive shaft 16 by the above-mentioned operation connection with the lug plate 19 via the hinge mechanism 21 and the support of the drive shaft 16, and the rotation center axis of the drive shaft 16. It is tiltable with respect to the drive shaft 16 while sliding in the direction.

The swash plate 20 has a minimum inclination of the swash plate 20 by a locking ring 22 fixed to the drive shaft 16 and a spring 23 disposed between the locking ring 22 and the swash plate 20. The angle is specified. The minimum tilt angle of the swash plate 20 refers to the tilt angle of the swash plate 20 when the angle with the axial direction of the drive shaft 16 is closest to 90 °.

A plurality of cylinder bores 24 (only one is shown in FIG. 1) are formed through the cylinder block 11 so as to extend along the direction of the rotation center axis of the drive shaft 16.
A single-headed piston 25 is reciprocally housed in the cylinder bore 24. The front and rear openings of the cylinder bore 24 are closed by the valve forming body 13 and the piston 25, and a compression chamber whose volume changes according to the reciprocating movement of the piston 25 is defined in the cylinder bore 24.
Each piston 25 is moored to the outer peripheral portion of the swash plate 20 via a shoe 26. As a result, the rotational movement of the swash plate 20 accompanying the rotation of the drive shaft 16 is converted into the reciprocating linear movement of the piston 25 via the shoe 26.

The drive shaft 16, the lug plate 19, the swash plate 20, the hinge mechanism 21, the piston 25 and the shoe 26.
The piston-type compression mechanism is constituted by. The rear housing 14 has a suction chamber 27 and a discharge chamber 28 defined therein. The front sides of the suction chamber 27 and the discharge chamber 28 are closed by the valve forming body 13. The refrigerant gas in the suction chamber 27 moves from the top dead center side of each piston 25 to the bottom dead center side thereof, and through the suction port 29 and the suction valve 30 formed in the valve body 13, the cylinder bore 24.
(Compression chamber) The low-pressure refrigerant gas introduced into the cylinder bore 24 is compressed to a predetermined pressure by the movement of the piston 25 from the bottom dead center side to the top dead center side, and the discharge port 31 and the discharge valve formed in the valve body 13 are discharged. It is introduced into the discharge chamber 28 via 32.

The suction chamber 27 and the discharge chamber 28 are connected by an external refrigerant circuit (not shown). The refrigerant discharged from the discharge chamber 28 is introduced into the external refrigerant circuit. In this external refrigerant circuit, heat exchange using the refrigerant is performed.
The refrigerant discharged from the external refrigerant circuit is introduced into the suction chamber 27, sucked into the cylinder bore 24, and subjected to the compression action again.

A bleed passage 33 is provided in the housing to connect the crank chamber 15 and the suction chamber 27.
Further, the discharge chamber 28 and the crank chamber 1 are provided in the housing.
An air supply passage 34 that communicates with the fuel cell 5 is provided. The opening of the air supply passage 34 can be adjusted by a control valve 35 provided on the air supply passage 34 (on the way of the air supply passage 34).

By adjusting the opening degree of the control valve 35, the amount of high-pressure refrigerant gas introduced into the crank chamber 15 through the air supply passage 34 and the amount of gas discharged from the crank chamber 15 through the extraction passage 33 are adjusted. The balance is controlled, and the crank pressure (internal pressure of the crank chamber 15) Pc is determined. The difference between the crank pressure Pc through the piston 25 and the internal pressure of the compression chamber is changed according to the change of the crank pressure Pc, and the inclination angle of the swash plate 20 is changed. Is adjusted.

As shown in FIGS. 1 and 2, the electromagnetic clutch unit 17 includes a pulley 42 rotatably supported by a bearing 41 on the front cylindrical portion of the front housing 12.
The solenoid coil 43 (magnetic force source) fixed to the front wall of the front housing 12 is provided. Further, the electromagnetic clutch unit 17 is arranged so as to be movable in the front-rear direction while being biased by a hub 44 fixed to the front end of the drive shaft 16 so as to be integrally rotatable and a leaf spring 45 provided on the hub 44. The armature 46 is provided.

The drawing shows a state in which the armature 46 is joined to the front end face of the pulley 42 against the biasing force of the leaf spring 45. When the armature 46 is attracted and joined to the front end surface of the pulley 42 by the electromagnetic force generated by energizing the coil 43, the driving force of the vehicle engine E is transmitted to the drive shaft 16 via the belt 18, the pulley 42 and the armature 46. It When the electromagnetic force disappears due to the stop of the power supply to the coil 43, the armature 46 is separated from the pulley 42 by the urging force of the leaf spring 45, and the power transmission is cut off. In this way, the engine power is selectively transmitted to the drive shaft 16 based on the energization control of the coil 43.

On the front side of the hub 44, the drive shaft 1 is
A damper part 5 having a circular outer shape when viewed in the axial direction of 6
0 is integrally rotatable with the hub 44.
In addition, the drive shaft 16, the lug plate 19, the pulley 42, the hub 44, the leaf spring 45, the armature 46, and the damper portion 5.
A rotating body is constituted by 0. Also, the damper part 5
The electromagnetic clutch 17 including 0 and the compressor C constitute a rotary machine.

The damper portion 50 has a concave portion 5 as a guide portion.
Eight 1's are formed (only two are shown in FIG. 1). The recesses 51 are arranged at equal intervals in the circumferential direction of the damper part 50. A rolling guide surface 52 as a guide surface having a circular cross section is formed in each recess 51. The rolling guide surface 52 is
It is formed of a cylindrical inner peripheral surface having a radius r ₁ centered on an axis parallel to the rotation center axis and spaced from the rotation center axis of the damper part 50 by a predetermined distance (this distance is referred to as R ₁ ).

Each of the recesses 51 accommodates one roller 53 (whose mass of each roller 53 is m ₁ ) which is a cylindrical rigid member as a mass body. Roll 5
3 is made of stainless steel (non-magnetic material).

The diameter d _{1 of the} roller 53 is the diameter 2r _{1 of the} recess 51.
And the axial length thereof is set to be slightly smaller than the depth of the recess 51 (the axial depth of the damper portion 50). That is, each roller 53 is accommodated in each recess 51 so as to be movable along the rolling guide surface 52. Each roller 53 is prevented from rolling down to the outside of each recess 51 by an annular lid 54 fixed to the opening side (front side) of each recess 51.

Each roller 53 is driven when the compressor C is driven by the vehicle engine E (at this time, the pulley 42 and the armature 46).
Is in a joined state), that is, when the drive shaft 16 rotates, centrifugal force acts to bring it into contact with the rolling guide surface 52 (states of FIGS. 1 and 2). In this state, when a torque fluctuation due to the rotational vibration of the damper portion 50 or the like occurs, each roller 53 starts reciprocating along the rolling guide surface 52 in each recess 51. In other words, (the center of gravity of) each roller 53 performs a pendulum motion about the central axis of the inner peripheral surface of the cylinder forming the rolling guide surface 52. Therefore, each roller 53 acts as a centrifugal pendulum when the compressor C is driven by the vehicle engine E.
In this embodiment, in order to suppress the torque fluctuation by the pendulum motion of the roller 53, the damper portion 5 of the roller 53 is suppressed.
The arrangement position, size, mass, etc. at 0 are set.

The concave portion 51 and the roller 53 constitute a dynamic damper. Here, each of the above-mentioned settings for the roller 53 acting as a centrifugal pendulum will be described.

The roller 53 functions to suppress the torque fluctuation (the fluctuation width of the torque fluctuation) at a frequency equal to the natural frequency of the roller (centrifugal pendulum) 53. Therefore, the damper portion 50 of the roller 53 is set so that the natural frequency of the roller 53 becomes equal to the peak frequency of the torque fluctuation.
By setting the arrangement position, size, mass, etc. in
It is possible to suppress the peak torque fluctuation and effectively suppress the overall effect of the torque fluctuation. The peak of the torque fluctuation indicates the peak of the fluctuation width of the torque fluctuation, that is, the rotation order component.

The frequency of the torque fluctuation and the natural frequency of the roller 53 are proportional to the angular velocity ω ₁ of the drive shaft 16 which is correlated with the rotational speed of the drive shaft 16. Further, the frequency of the torque fluctuation when the peak having the largest fluctuation range among the peaks of the torque fluctuation of the compressor C appears is the rotation speed (= ω ₁ / 2π) of the drive shaft 16 per unit time. It is given by the product of the number of cylinders (the number of cylinder bores 24) N (ω ₁ / 2π) · N. In the compressor C, the frequency of the nth (n is a natural number) largest one of the peaks of the torque fluctuation tends to show a value equivalent to the product n · (ω ₁ / 2π) · N. Has been determined by experiments.

On the other hand, the natural frequency of the roller 53 is the drive shaft 1
6 rotations per unit time (= ω ₁/ 2π) and the ratio R
It is given by the product of the square root value of / r. In addition, here
R is the center axis of rotation of the rotating body and the swing of the roller 53.
It is the distance from the center axis of the child motion, and r is the swing of the roller 53.
It is the distance between the center axis of the child motion and the center of gravity of the roller 53.

Therefore, the square root value of the ratio R / r is multiplied by n.
By setting it equal to the value of N, it is possible to match the n-th largest peak frequency of the torque fluctuation with the natural frequency of the roller 53. This makes it possible to suppress the torque fluctuation at the frequency of the nth largest peak.

Accordingly, in the present embodiment, in order to suppress the largest peak of the torque fluctuation, the ratio R /
The magnitudes of R and r are set so that the square root value of r is equal to the value of N (the value of n · N when n = 1).

In order to efficiently suppress the torque fluctuation by the pendulum motion of the roller 53, the torque T about the rotation center axis of the damper portion 50 acted by the roller 53 is equal to the fluctuation width of the torque fluctuation. We need to counter it. It is understood that the magnitude of the torque T in a state where the peak frequency of the torque fluctuation and the natural frequency of the roller 53 match is given by the following formula.

(Equation 1) T = m · (ω _a ) ² · (R + r) · R · φ where m is the total mass of all rollers 53 (m = 8 · m ₁ ), and ω _a is It is the average angular velocity of the roller 53 that performs the pendulum motion at the minute swing angle φ.

In the roller 53 of this embodiment, the mass m
Is set as large as possible to suppress the values R, r, and φ to be small, and to suppress the size increase of the damper part 50 as much as possible, while ensuring the large torque T.

In the present embodiment, the central axis of the cylindrical inner peripheral surface forming the rolling guide surface 52 is the central axis of the pendulum motion of the roller 53 (the fulcrum of the pendulum motion is on this central axis). ). That is, the distance R ₁ between the rotation center axis of the damper part 50 and the center axis of the inner peripheral surface of the cylinder.
Corresponds to the distance R.

The distance between the center axis of the pendulum motion of the roller 53 and the center of gravity of the roller 53 is a value obtained by subtracting half the diameter d ₁ of the roller 53 from the radius r ₁ of the inner peripheral surface of the cylinder. be equivalent to. That is, the difference _{{r 1 - (d 1/} 2)}
Corresponds to the distance r.

That is, in this embodiment, in order to suppress the largest peak of the torque fluctuation, the ratio R / r is reduced.
Corresponds to the square root values, the ratio _{R 1 / {r 1 - (} d 1/2)}
The magnitudes of R ₁ , r ₁ and d ₁ are set so that the square root value of is equal to the value of N (the value of n · N when n = 1).

In the pendulum motion described above, various settings are made with the roller 53 as a mass point where the mass is concentrated on the center of gravity thereof. Next, the compressor C configured as described above
The action of will be described.

Power from the vehicle engine E is applied to the drive shaft 16 in a state where the armature 46 and the pulley 42 are joined by the electromagnetic force generated by energizing the solenoid coil 43.
Swash plate 20 rotates together with drive shaft 16. As each swash plate 20 rotates, each piston 25
The cylinder is reciprocated with a stroke corresponding to the inclination angle, and suction, compression, and discharge of the refrigerant are sequentially repeated in each cylinder bore 24.

When the opening of the control valve 35 becomes small,
From the discharge chamber 28 through the air supply passage 34 to the crank chamber 15
The amount of high-pressure refrigerant gas supplied to the crankshaft is reduced, the crank pressure Pc is reduced, and the inclination angle of the swash plate 20 is increased.
The discharge capacity of the compressor C increases. Conversely, when the opening degree of the control valve 35 increases, the amount of high-pressure refrigerant gas supplied from the discharge chamber 28 to the crank chamber 15 via the air supply passage 34 increases, the crank pressure Pc increases, and the swash plate increases. The inclination angle of 20 becomes small, and the discharge capacity of the compressor C becomes small.

At the time of rotation of the drive shaft 16, the compression reaction force of the refrigerant and the reaction force due to the reciprocating motion of the piston 25 are transmitted to the drive shaft 16 via the swash plate 20, the hinge mechanism 21, etc. Torsional vibration (rotational vibration) is generated in 16. This torsional vibration causes torque fluctuations. The torque fluctuation causes resonance between the compressor C itself and an external rotation system (vehicle engine E, auxiliary machinery, etc.) operatively connected to the pulley 42 via the belt 18, and the compressor C. It will be.

When the torque fluctuation occurs, the damper unit 5
The roller 53 provided at 0 starts the pendulum movement. The torque applied around the rotation center axis of the damper part 50 by this pendulum motion acts to suppress the torque fluctuation. Since the natural frequency of the roller 53 is set to be equal to the frequency of the largest peak of the torque fluctuation, the torque fluctuation of the maximum peak is suppressed, and the torque fluctuation of the rotating body is effectively reduced as a whole. To be done.

In this embodiment, since the roller 53 is made of a non-magnetic material, the pendulum movement is performed without being affected by the electromagnetic force generated by the solenoid coil 43. That is, the torque fluctuation suppressing action of the roller 53 is effectively performed without being affected by the electromagnetic force.

In this embodiment, the following effects can be obtained. (1) The rotating body is provided with a roller 53 which is separated from the rotation center axis of the rotation body by a predetermined distance R ₁ and performs a pendulum motion about an axis parallel to the rotation center axis.
According to this, the torsional vibration is suppressed by the pendulum movement of the roller 53, and the rotating body and the compressor C including the rotating body are suppressed.
The resonance that occurs between the compressor C and the external rotation system that is operatively connected to the pulley 42 via the belt 18 is suppressed.

(2) The roller 53 is made of a non-magnetic material. According to this, the pendulum motion of the roller 53 is not disturbed by the influence of the external magnetic source such as the solenoid coil 43. That is, it is possible to prevent the vibration suppressing effect from being lowered due to the influence of the external magnetic source.

(3) Roller 53 which is a cylindrical rigid member
Is arranged so as to be movable along the rolling guide surface 52 having a circular cross section of the concave portion 51 provided in the damper portion 50. According to this, since the roller 53 is not pivotally supported at the fulcrum of the pendulum motion, the structure becomes simpler than the structure in which the mass body is pivotally supported. Further, as compared with the structure in which the mass body is pivotally supported, the pendulum movement center (fulcrum) of the mass body due to the existence of a gap between the support shaft and the shaft hole of the mass body through which the support shaft is inserted, There is no change in the distance from the center of gravity. Therefore, the vibration can be suppressed better.

(4) The roller 53 is made of stainless steel. Since stainless steel is relatively inexpensive and has a large specific gravity, it is suitable as a non-magnetic material for a mass body that performs pendulum motion.

(5) The dynamic damper is provided in the electromagnetic clutch portion 17 arranged on the power transmission path between the drive shaft 16 of the compressor C and the vehicle engine E. Since the roller 53 is formed of a non-magnetic material, the pendulum motion is not disturbed by the influence of the magnetic force generated by the solenoid coil 43. That is, in the rotary machine, it is not necessary to install the dynamic damper apart from the solenoid coil 43, and the degree of freedom in installing the dynamic damper is increased.

The embodiment is not limited to the above, but may have the following modes, for example. In the above embodiment, the roller 53 may be formed of a non-magnetic material other than stainless steel. Examples of the non-magnetic material include copper, tungsten, silver, aluminum and ceramics. Among them, copper is relatively inexpensive and has a large specific gravity, so that it is suitable as a non-magnetic material for the mass body that performs the pendulum motion.

In the above embodiment, the solenoid coil 43 is used as the magnetic force source, but the magnetic force source is not limited to this. For example, a magnetic source such as an electric motor arranged near the dynamic damper can generate a magnetic force. Examples of the electric motor include an electric motor as a drive source for driving an automobile that can be electrically driven. Since this electric motor is required to have a relatively large output, it produces a relatively large magnetic force as a magnetic force source.

In the above embodiment, the mass body may be formed in a spherical shape. ○ In the above-mentioned embodiment, the concave portion 5 accommodating the roller 53.
Any number of 1 may be provided. It is not necessary to set the number in correlation with the number of cylinders of the compressor C and the like.

In the above embodiment, the cross-sectional shape of the recess 51 (the cross-sectional shape in a plane orthogonal to the rotation center axis of the rotating body) is the contact portion between the roller 53 and the rolling guide surface 52 in the pendulum motion. The shape may be other than circular except for. In the recess 51, if the cross-sectional shape of the contact portion between the roller 53 and the rolling guide surface 52 in the pendulum movement (the cross-sectional shape in a plane orthogonal to the rotation center axis of the rotating body) is formed in an arc shape. Good.

In the above embodiment, the value corresponding to the square root value of the ratio R / r is set to the value of n · N with n = 1, that is, equal to N, but n is a natural number of 2 or more (for example, 2, 3, etc.) may be set equal to the value of n · N.

In the above embodiment, a plurality of mass bodies (rollers) may be provided, and the value corresponding to the ratio R / r (square root value) may be set to a different value for each mass body. According to this, by setting a plurality of values corresponding to the ratio R / r, it becomes possible to suppress the fluctuation range for a plurality of peaks (rotational orders) of the torque fluctuation. In this case, the value to be matched with the square root value of the value corresponding to the ratio R / r is, for example, n
It is preferable to select several kinds of values from 1 (for example, 1, 2 and 3 when three kinds of values are targeted) and multiply them by N (product n · N). .
According to this, it becomes possible to suppress several kinds (three kinds in this case) from the largest peak of the torque fluctuation, and the resonance suppressing effect becomes large.

In the above embodiment, the pendulum movement is performed by the roller 53 rolling along the rolling guide surface 52 of the recess 51 formed in the damper portion 50. On the other hand, the damper part may be provided with a mass body that performs a pendulum motion with a support shaft fixed to the damper part as a fulcrum. Also,
A support shaft may be provided on the mass body itself, and the support shaft may be inserted into a hole formed in the damper portion to support the mass body in the damper portion so as to allow pendulum movement.

In the above embodiment, in the pendulum motion, various settings were made with the mass body as a mass point at which the mass is concentrated at the center of gravity thereof. However, it is desirable to consider the inertial mass of the mass body and perform the various settings described above. It is better to make settings.
In this case, for example, in the pendulum motion of the cylindrical roller 53, the ratio R / r in the above-described embodiment is replaced with the ratio 2R / 3r, so that the setting can be performed in consideration of the inertial mass. Further, in this case, the magnitude of the torque T in a state in which the peak frequency of the torque fluctuation and the natural frequency of the roller 53 match is given by the following formula.

[0063] (Equation 2) T = (3/2) · m · (ω a) 2 · (R + r) · R · φ also performs the pendulum motion by rolling along the rolling guide surface When the mass body has a spherical shape, the ratio R / r is replaced with the ratio 5R / 7r to enable the setting in consideration of the inertial mass. Further, in this case, the magnitude of the torque T in a state where the peak frequency of the torque fluctuation and the natural frequency of the spherical mass body match each other is given by the following formula.

[0064] (Equation 3) T = (7/5) · m · (ω a) 2 · (R + r) · R · φ Even when the mass was shape other than the above cylindrical or spherical By performing the various settings in consideration of the inertial mass corresponding to each shape, it becomes possible to more effectively suppress the resonance.

The electromagnetic clutch portion 17 is not a single-sided compressor that causes a single-headed piston to perform a compression operation, such as the compressor C, but is a double-headed cylinder bore provided on both front and rear sides with the crank chamber interposed therebetween. It may be provided in a double-sided compressor that causes a piston of the mold to perform a compression operation.

○ The compressor C is replaced by a cam plate (swash plate 2
0) may rotate integrally with the drive shaft 16, and may be a type in which a cam plate is supported so as to be rotatable relative to the drive shaft and swings, for example, a wobble type compressor.

The compressor C may be a fixed capacity type in which the stroke of the piston 25 is constant. In the above-described embodiment, the application example of the piston type compressor in which the piston reciprocates has been shown, but it may be applied to a rotary type compressor such as a scroll type compressor.

In the above embodiment, a sprocket, a gear or the like may be applied instead of the pulley as the member forming the rotating body. In the above-described embodiment, the damper section 50 is provided on the electromagnetic clutch section 17, but the damper section 50 may be directly fixed to the drive shaft 16 of the compressor C to which the electromagnetic clutch section 17 is not assembled. Good.

○ The dynamic damper is replaced by a compressor C.
It may be provided on a rotary member housed in the housing. For example, the dynamic damper may be provided in the lug plate 19 or other specially provided member operatively connected to the drive shaft 16 in the housing to suppress the rotational vibration generated in the drive shaft 16.

In the above embodiment, the configuration in which the drive shaft is driven only by the external drive source has been shown. However, for example, a compression having a rotating electric machine unit such as a motor capable of driving the drive shaft in the housing is provided. May be applied to the machine. In this case, for example, the mass body that performs the pendulum motion may be provided on the rotor of the rotating electric machine unit. The rotor is a magnetic force source (coil, permanent magnet, etc.) provided in the rotating electrical machine section.
However, since the mass body of the present invention is formed of a non-magnetic material, the pendulum motion of the mass body is not disturbed by the magnetic force.

In the above-described embodiment, the application example of the compressor is shown. However, a configuration is provided in which a rotating body is provided with a dynamic damper having a mass body that performs the pendulum motion, and rotational vibration can be generated in the rotating body. Any rotating machine may be applied.

In the above embodiment, the central axis of the pendulum motion of the mass body does not necessarily have to be parallel to the central axis of rotation of the rotating body on which the mass body is provided. In this case, the central axis of the pendulum motion may be inclined with respect to the central axis of rotation of the rotating body within a range where a desired effect can be obtained in suppressing (the maximum amount of) the transmission torque fluctuation.

[0073]

As described in detail above, according to the inventions described in claims 1 to 3, in the dynamic damper, the reduction of the vibration suppressing effect due to the influence of the external magnetic force source on the mass body performing the pendulum motion is prevented. be able to.

According to the invention described in claims 4 to 6, in the rotating machine, the dynamic damper included in the rotating machine is constituted, and the vibration suppressing effect due to the influence of the external magnetic source on the mass body performing the pendulum motion is exerted. The decrease can be prevented.

[Brief description of drawings]

FIG. 1 is an overall schematic sectional view of a compressor including an electromagnetic clutch unit according to an embodiment.

FIG. 2A is a schematic front view showing the outline of the damper portion, and FIG. 2B is a partial schematic cross-sectional view taken along line bb of FIG. 2A.

[Explanation of symbols]

16 ... Drive shaft, 17 ... Electromagnetic clutch part, 19 ... Lug plate, 20 ... Swash plate, 21 ... Hinge mechanism, 24 ... Cylinder bore, 25 ... Piston, 26 ... Shoe (16, 19, 2)
0, 21, 25 and 26 constitute a piston type compression mechanism), 42 ... pulley, 44 ... hub, 45 ... leaf spring, 46
... Armature, 50 ... Damper part (16, 19, 42,
44, 45, 46 and 50 constitute a rotating body), 51
... Recesses as guide parts, 52 ... Rolling guide surfaces as guide surfaces, 53 ... Rollers as mass bodies (51 and 53 constitute a dynamic damper), C ... Compressors (17 and C as main bodies of rotating machines) Constitutes a rotating machine), E ... Vehicle engine as an external drive source.

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Masaki Ota             2-1, Toyota-cho, Kariya City, Aichi Stock Association             Inside Toyota Toyota Industries (72) Inventor Taku Yasaya             2-1, Toyota-cho, Kariya City, Aichi Stock Association             Inside Toyota Toyota Industries (72) Inventor Akinori Kanai             2-1, Toyota-cho, Kariya City, Aichi Stock Association             Inside Toyota Toyota Industries (72) Inventor Ryoto Yamanouchi             2-1, Toyota-cho, Kariya City, Aichi Stock Association             Inside Toyota Toyota Industries F term (reference) 3H076 AA06 BB02 CC12 CC17 CC40

Claims (6)

[Claims] 1. A rotary body, which passes through a point separated by a predetermined distance from a center axis of rotation of the rotary body,
A dynamic damper having a mass body that performs a pendulum motion about an axis substantially parallel to the rotation center axis, wherein the mass body is made of a non-magnetic material. 2. The dynamic damper according to claim 1, wherein the mass body performs the pendulum movement by moving along a guide surface having a circular arc-shaped cross section of a guide portion provided on the rotating body. 3. The dynamic damper according to claim 1, wherein the non-magnetic material is stainless steel or copper. 4. A rotating machine comprising the dynamic damper according to claim 1. Description: 5. The rotary machine according to claim 4, wherein the dynamic damper is provided in an electromagnetic clutch portion arranged on a power transmission path between the rotary machine main body and an external drive source. 6. The rotary machine according to claim 4, further comprising a compression mechanism that compresses the refrigerant.