KR20200033638A - Compressor - Google Patents

Abstract

The present invention relates to a compressor. The compressor includes: a disc hub assembly combined with a rotary shaft of a compressing machine; and a pulley rotated by receiving power from a driving source and selectively confined to the disc hub assembly. The pulley includes an inner slot and an outer slot. The inner slot includes a centrifugal inner surface, a centripetal inner surface and an end side inner surface. The end side inner surface of the inner slot includes: a first curved surface of the end inner surface, curved from the centrifugal inner surface towards the centrifugal side in a radial direction of the pulley; and a second curved surface of the end side inner surface, curved from the first curved surface of the end side inner surface towards the center in a radial direction of the pulley. Therefore, an increase in contact force between the pulley and the disc hub assembly, the hardness securement of the pulley, a size reduction, a weight reduction and a cost reduction can be achieved at the same time. In addition, as damage to a slot of the pulley is prevented, damage to the pulley can be prevented.

Description

Compressor {COMPRESSOR}

The present invention relates to a compressor, and more particularly, to a compressor including a clutch that is magnetized and demagnetized and capable of selectively connecting and disconnecting a drive source and a rotating shaft.

Generally, an air conditioner (A / C) for indoor air conditioning is installed in a vehicle. The air conditioning system includes a compressor that compresses a low-temperature, low-pressure gaseous refrigerant drawn from an evaporator into a high-temperature and high-pressure gaseous refrigerant and sends it to a condenser.

The compressor includes a reciprocating type for compressing a refrigerant according to a reciprocating motion of a piston and a rotating type for performing compression while rotating. In the reciprocating type, there are a crank type that uses a crank to transfer a plurality of pistons according to a transmission method of a driving source, and a swash plate type that transmits to a rotating shaft provided with a swash plate. In the rotary type, a rotary rotary shaft and a vane rotary type using vanes, There are scrolling types using orbiting scroll and fixed scroll.

Such a compressor typically includes a rotating shaft that transmits rotational force to a compressor mechanism that compresses refrigerant, and includes a driving source (for example, an engine) of the compressor and a clutch that selectively interrupts the rotating shaft, from the driving source. It is configured to operate by selectively receiving power.

1 is a cross-sectional view showing a conventional compressor, FIG. 2 is a front view showing a pulley in the compressor of FIG. 1, FIG. 3 is an enlarged portion A of FIG. 2, and FIG. 4 is an enlarged portion B of FIG. .

1 to 4, the conventional compressor is provided inside the casing 1000, the casing 1000, the compressor mechanism for compressing the refrigerant (2000), provided outside the casing 1000 A rotating shaft 3000 for transmitting rotational force from a driving source (for example, an engine) (not shown) to the compressor mechanism 2000 and a clutch 4000 for selectively controlling the driving source (not shown) and the rotating shaft 3000 ).

The clutch 4000 is a pulley 4100 that is rotated by receiving power from the driving source (not shown), a disk hub assembly 4200 that is fastened to the rotation shaft 3000 and selectively contacts and spaces the pulley 4100 ), A field coil assembly 4300 that magnetizes when power is applied to contact the pulley 4100 and the disk hub assembly 4200.

The pulley 4100 is formed in a substantially annular shape, and a driving belt (not shown) for transmitting a driving force from the driving source (not shown) to the pulley 4100 is installed on the outer peripheral surface side of the pulley 4100. An annular wall 4110 is formed, and an annular wall 4190 for bearing fastening is formed on an inner circumferential surface side of the pulley 4100 where a bearing for rotatably supporting the pulley 4100 is installed.

In addition, a friction surface contactable with a disk 4220 to be described later of the disk hub assembly 4200 is formed on one side of the pulley 4100, and the field coil assembly 4300 is formed on the other side of the pulley 4100. A field coil assembly accommodating groove into which the insertion is mounted is formed.

In addition, the pulley 4100 increases the suction magnetic flux of the field coil assembly 4300 transmitted to the disk hub assembly 4200 so that the contact force between the pulley 4100 and the disk hub assembly 4200 increases. , A plurality of slots (4130, 4160) formed along the rotational direction of the pulley (4100) while passing through the pulley (4100).

Further, the pulley 4100 includes a plurality of bridges 4140 and 4170 interposed between the plurality of slots 4130 and 4160 so that the rigidity of the pulley 4100 is improved.

Specifically, the pulley 4100 includes a plurality of inner slots 4160 formed along the rotational direction of the pulley 4100 at a position spaced apart from the rotation center of the pulley 4100 by a predetermined first distance, and The pulley 4100 includes a plurality of outer slots 4130 formed along the rotational direction of the pulley 4100 at a position spaced apart by a second distance farther than the first distance from the center of rotation.

In addition, the pulley 4100 is based on the inner slot 4160, the inner peripheral portion 4180 positioned on the centripetal side in the rotational radial direction of the pulley 4100, the pulley based on the outer slot 4130 The outer peripheral portion 4120 positioned on the centrifugal side in the radial direction of rotation of the 4100, the intermediate portion 4150 positioned between the inner slot 4160 and the outer slot 4130, between the plurality of inner slots 4160 Interposed between each of the plurality of inner bridges 4170 and the plurality of outer slots 4130 connecting the inner circumference 4180 and the intermediate portion 4150, the intermediate portion 4150 and the outer circumference portion 4120 ), A plurality of outer bridges 4140.

The disk hub assembly 4200 includes a hub 4210 fastened to the rotating shaft 3000 and a disk 4220 extending from the hub 4210 and selectively contacting and spaced from the pulley 4100.

The field coil assembly 4300 includes a coil housing and a coil accommodated in the coil housing and generating electromagnetic force when power is applied.

The conventional compressor according to this configuration operates as follows.

That is, the pulley 4100 is rotated by receiving a driving force from the driving source (not shown).

In this state, when power is applied to the coil, the disk hub assembly 4200 is moved to the pulley 4100 side by the suction force due to the magnetic induction of the coil to be in close contact with the pulley 4100. That is, as the disk hub assembly 4200 and the pulley 4100 are engaged, power of the driving source (not shown) is transmitted to the rotating shaft 3000 through the pulley 4100 and the disk hub assembly 4200. do. Then, the rotating shaft 3000 operates the compressor mechanism 2000 with the received power to compress the refrigerant.

On the other hand, when the application of power to the coil is stopped, the suction force due to magnetic induction of the coil is no longer generated, and the disk hub assembly 4200 is moved in a direction away from the pulley 4100 to pulley 4100. And are separated. That is, power transmission from the driving source (not shown) to the rotating shaft 3000 is stopped. Then, the compressor mechanism 2000 is stopped, and refrigerant compression is stopped.

However, in such a conventional compressor, there is a problem that the contact force between the pulley 4100 and the disk hub assembly 4200, the rigidity of the pulley 4100, size reduction, weight reduction, cost reduction cannot be achieved at the same time.

Specifically, as the length of the slots 4130 and 4160 (a value measured along the rotational direction of the pulley 4100) increases, the area of the slots 4130 and 4160 increases, and the disk hub assembly 4200 The suction magnetic flux of the field coil assembly 4300 transmitted to is increased, thereby improving contact force between the pulley 4100 and the disk hub assembly 4200. However, as the length of the slots 4130 and 4160 increases, the length of the bridges 4140 and 4170 (a value measured along the rotational direction of the pulley 4100) decreases, and the rigidity of the pulley 4100 increases. Weaken.

On the other hand, as the lengths of the slots 4130 and 4160 become shorter, the area of the slots 4130 and 4160 decreases, and the suction magnetic flux of the field coil assembly 4300 delivered to the disk hub assembly 4200 increases. By reducing, the contact force between the pulley 4100 and the disk hub assembly 4200 is weakened. However, as the lengths of the slots 4130 and 4160 become shorter, the lengths of the bridges 4140 and 4170 become longer, and the rigidity of the pulley 4100 is improved.

In consideration of this, the lengths of the bridges 4140 and 4170 are increased to improve the rigidity of the pulley 4100, and the contact force between the pulley 4100 and the disk hub assembly 4200 generated as the opposite is weakened. In order to solve the above, a method of increasing the capacity of the field coil assembly 4300 may be considered. However, in this case, there is a problem in that the size, weight, and cost of the bridge 4140 and 4170 increase as the length increases and the capacity of the field coil assembly 4300 increases.

In addition, in the conventional compressor, the bridges 4140 and 4170 are included to secure the rigidity of the pulley 4100, but breakage occurs in the slots 4130 and 4160, and the pulley 4100 is damaged. There was a problem.

Republic of Korea Patent Publication No. 10-2016-0041454

Accordingly, an object of the present invention is to provide a compressor capable of simultaneously achieving an increase in contact force between a pulley and a disk hub assembly, securing pulley rigidity, reducing size, reducing weight, and reducing cost.

In addition, another object of the present invention is to provide a compressor capable of preventing damage to the pulley by preventing damage from occurring in the slot of the pulley.

The present invention, in order to achieve the above object, a disk hub assembly that is fastened to the rotating shaft of the compression mechanism; And a pulley rotated by receiving power from a driving source and selectively intermittent with the disk hub assembly. The pulley includes an inner slot formed along a rotational direction of the pulley at a position spaced apart from the rotation center of the pulley; And an outer slot formed along the rotational direction of the pulley at a position spaced apart from the inner slot of the pulley from the center of rotation, wherein the inner slot rotates the pulley on the centrifugal side in the radial direction of the pulley. An inner slot centrifugal side inner surface facing the central side; An inner slot centrifugal side inner surface opposite to the inner slot centrifugal side inner side at the centripetal side in the radial direction of the pulley; And an inner slot end side inner surface connecting the inner slot centrifugal side inner surface and the inner slot centrifugal side inner surface; and the inner slot end side inner surface curved from the inner slot centrifugal side inner surface to a radially centrifugal side of the pulley. An inner slot first side curved surface; And an inner surface end surface second curved surface curved from the inner surface end side first curved surface to the centripetal side in the radial direction of the pulley.

The center of curvature of the inner surface of the inner slot centrifugal side is formed at the center of rotation of the pulley, and the radius of curvature of the inner surface of the inner slot centrifugal side is formed smaller than the radius of the pulley, and the center of curvature of the inner surface of the inner slot centrifugal side is the pulley. It is formed in the center of rotation, the radius of curvature of the inner surface of the inner slot centripetal side is formed smaller than the radius of curvature of the inner surface of the inner slot centrifugal side, the center of curvature of the inner surface second curved surface of the inner slot end side is inside the inner slot Formed, the radius of curvature of the inner surface of the inner surface of the inner slot end side may be greater than half of a value obtained by subtracting the radius of curvature of the inner surface of the inner slot from the radius of curvature of the inner surface of the inner slot centrifugal side.

When the center line of the inner slot is an imaginary line connecting dots having the same distance to the inner surface of the inner slot centrifugal side and the distance to the inner surface of the inner slot centrifugal direction in the radial direction of the pulley, the inner surface end side inner surface second The center of curvature of the curved surface may be formed on the center line of the inner slot.

The center of curvature of the inner curved surface of the inner slot end side is formed on the centrifugal side in the radial direction of the pulley based on the inner surface of the inner slot centrifugal side, and the radius of curvature of the inner curved surface of the inner surface of the inner slot end side is the inner slot The inner slot end is formed to be equal to a value obtained by subtracting the radius of curvature of the inner surface second curved surface from the inner slot at a distance between the center of curvature of the inner curved surface of the end surface and the inner center of the curvature of the inner curved surface of the inner slot. The radius of curvature of the inner surface first curved surface is formed equal to a value obtained by subtracting the radius of curvature of the inner surface of the inner slot centrifugal distance from the distance between the center of curvature of the inner surface first curved surface and the center of curvature of the inner surface of the inner slot. Can be.

The pulley further includes a ring-shaped wall for fastening a bearing extending along a rotational direction of the pulley from a centripetal side of the pulley on the basis of the inner slot, and further including a radius of curvature of the inner surface of the inner surface of the inner slot end May be formed to be less than or equal to a value obtained by subtracting the radius of curvature of the outer circumferential surface of the annular wall for fastening the bearing at a distance between the center of curvature of the inner curved surface of the inner slot end side and the center of curvature of the circular wall for fastening the bearing.

The radius of curvature of the inner surface first curved surface of the inner slot end side may be larger than the radius of curvature of the inner surface second curved surface of the inner slot end side.

The inner slot end side inner surface is curved from the inner slot centripetal side inner surface to the radially centripetal side, and the inner slot end side inner surface is curved from the second curved surface to the radially centrifugal side of the pulley from the inner slot end side inner surface. The third curved surface; may further include.

The center of curvature of the inner surface third curved surface of the inner slot end side is formed on the centripetal side in the radial direction of the pulley based on the inner surface of the inner slot centrifugal side, and the radius of curvature of the inner surface third curved surface is the inner slot end It is formed equal to a value obtained by subtracting the radius of curvature of the inner surface end surface second curved surface at a distance between the center of curvature of the inner surface third curved surface and the center of curvature of the inner surface end surface of the inner slot end, and the inner slot end side The radius of curvature of the inner surface third curved surface may be formed to be equal to a value obtained by subtracting the distance between the radius of curvature of the inner surface third curved surface and the center of curvature of the inner surface of the inner slot at the radius of curvature of the inner surface of the inner slot centroid. You can.

The radius of curvature of the inner surface end side third curved surface may be formed larger than the radius of curvature of the inner surface end side second curved surface.

The inner slot end side inner surface is curved toward the centrifugal side in the radial direction of the pulley from the inner surface of the inner slot centripetal side, and the inner surface of the inner slot end side is curved from the second curved surface to the centripetal side in the radial direction of the pulley. It may further include a fourth curved surface.

A curvature center of the inner curved surface of the inner slot end side is formed inside the slot, and the radius of curvature of the inner curved surface of the inner surface of the inner slot end side is the inner slot at the radius of curvature of the inner curved surface of the inner surface of the inner slot end side. It is formed equal to a value obtained by subtracting the distance between the center of curvature of the inner surface of the fourth curved surface at the end side and the center of curvature of the inner surface of the inner curved surface at the end portion of the inner slot, and the radius of curvature of the inner surface fourth curved surface at the inner slot end side It may be formed to be equal to a value obtained by subtracting the radius of curvature of the inner surface of the inner slot centroid from the distance between the center of curvature of the fourth inner surface and the center of curvature of the inner slot centripetal side.

The center of curvature of the inner curved surface of the inner slot end side is formed on the center line of the inner slot, and the radius of curvature of the inner curved surface of the inner slot end side is the inner slot centroid at the radius of curvature of the inner surface of the inner slot centrifugal side. It may be formed equal to half of the value obtained by subtracting the radius of curvature of the inner surface of the side.

The outer slot includes: an outer slot centripetal inner surface having a center of curvature formed at a center of rotation of the pulley, and having a radius of curvature larger than a radius of curvature of the inner surface of the inner slot centrifugal side; An outer slot centrifugal side inner surface having a center of curvature formed at a center of rotation of the pulley, and having a radius of curvature larger than a radius of curvature of the inner surface of the outer slot centroid; And an outer slot end side inner surface connecting the outer slot centrifugal side inner surface and the outer slot centripetal side inner surface; wherein the outer slot end side inner surface is the pulley from the outer slot centrifugal side inner surface to the outer slot centrifugal side inner surface. It may be formed to be curved toward the center of the radial direction.

The center of curvature of the inner surface of the outer slot end side is formed inside the outer slot, and the radius of curvature of the inner surface of the outer slot end side subtracts the radius of curvature of the inner surface of the outer slot centrifugal side from the radius of curvature of the inner surface of the outer slot centrifugal side. It can be formed equal to half of a value.

The compressor according to the present invention, a disc hub assembly that is engaged with the rotating shaft of the compression mechanism; And a pulley rotated by receiving power from a drive source and selectively intermittent with the disk hub assembly; and the pulley includes an inner slot and an outer slot; wherein the inner slot is an inner slot centrifugal side inner surface, an inner slot centripetal side An inner surface and an inner slot end side inner surface, wherein the inner slot end side inner surface includes: an inner slot end side inner surface first curved surface curved from the inner slot centrifugal side inner surface to a radially centrifugal side of the pulley; And an inner slot end side inner surface second curved surface curved from the inner curved surface of the inner slot end side to a centripetal side in the radial direction of the pulley, thereby increasing contact force between the pulley and the disk hub assembly, securing pulley rigidity, and reducing size , Weight reduction, cost reduction can be achieved at the same time.

In addition, damage to the pulley can be prevented by preventing breakage in the slot of the pulley.

1 is a cross-sectional view showing a conventional compressor,
Figure 2 is a front view showing the pulley in the compressor of Figure 1,
3 is an enlarged view of part A of FIG. 2,
Figure 4 is an enlarged view of part B of Figure 2,
5 is a front view showing a pulley in a compressor according to an embodiment of the present invention,
Figure 6 is an enlarged view of part C of Figure 5,
7 is an enlarged view of a portion D of FIG. 5,
8 is a front view showing a part of the pulley in the compressor according to another embodiment of the present invention.

Hereinafter, a clutch according to the present invention and a compressor including the same will be described in detail with reference to the accompanying drawings.

5 is a front view showing a pulley in the compressor according to an embodiment of the present invention, FIG. 6 is an enlarged view of part C of FIG. 5, and FIG. 7 is an enlarged view of part D of FIG. 5.

Meanwhile, components not shown in FIGS. 5 to 7 are referred to in FIG. 1 for convenience of description.

5 to 7 and 1, the compressor according to an embodiment of the present invention is provided in the casing 1000, the casing 1000, the compressor mechanism for compressing the refrigerant (2000), A rotating shaft 3000 that transmits rotational force from a driving source (for example, an engine) (not shown) provided to the compressor mechanism 2000 to the outside of the casing 1000 and the driving source (not shown) and the rotating shaft 3000 ) May optionally include a power transmission mechanism for connecting and disconnecting.

The compressor mechanism 2000 is fastened to the piston 2100 and the rotating shaft 3000 provided for reciprocating movement inside the bore of the casing 1000 and rotated together with the rotating shaft 3000 and the piston 2100 It may include a swash plate (2200) for reciprocating motion.

Here, the compressor mechanism 2000 is formed in a swash plate method including the piston 2100 and the swash plate 2200 in the present embodiment, but with a turning scroll that is rotated by receiving rotational force of the rotating shaft 3000 It can be formed in various ways, such as a scrolling method including a fixed scroll that fits into the orbiting scroll.

The rotating shaft 3000, one end is connected to the compression mechanism (2000), the other end penetrates the casing 1000 and protrudes to the outside of the casing 1000, the disk hub assembly to be described later of the power transmission mechanism It can be fastened with (4200).

The power transmission mechanism is magnetized when power is applied to connect the driving source (not shown) and the rotating shaft 3000, and when the power is cut off, the device is demagnetized to separate the driving source (not shown) and the rotating shaft 3000 ( 4000).

The clutch 4000 is a pulley 4100 that is rotated by receiving power from the driving source (not shown), a disk hub assembly 4200 that is fastened to the rotation shaft 3000 and selectively contacts and spaces the pulley 4100 ), The field coil assembly 4300 and the field coil assembly 4300 that are magnetized when power is applied to contact the pulley 4100 and the disk hub assembly 4200 and the field coil assembly 4300 is cut off. When the device is made, it may include a separating means (not shown) separating the pulley 4100 and the disk hub assembly 4200.

The pulley 4100, the pulley 4100 is formed in a substantially annular shape, a drive belt (not shown) that transmits a driving force from the driving source (not shown) to the pulley 4100 on the outer peripheral surface side of the pulley 4100 A drive belt fastening annular wall 4110 is formed, and an inner peripheral surface side of the pulley 4100 is formed with a bearing fastening annular wall 4190 in which a bearing rotatably supporting the pulley 4100 is installed. You can.

In addition, a friction surface contactable with a disk 4220 to be described later of the disk hub assembly 4200 is formed on one side of the pulley 4100, and the field coil assembly 4300 is formed on the other side of the pulley 4100. A field coil assembly receiving groove into which the insertion is mounted may be formed.

In addition, the pulley 4100 increases the suction magnetic flux of the field coil assembly 4300 transmitted to the disk hub assembly 4200 so that the contact force between the pulley 4100 and the disk hub assembly 4200 increases. , It may include a plurality of slots (4130, 4160) formed through the pulley 4100 along the rotational direction of the pulley 4100.

In addition, the pulley 4100 may include a plurality of bridges 4140 and 4170 interposed between the plurality of slots 4130 and 4160 so that the rigidity of the pulley 4100 is improved.

Specifically, the pulley 4100 includes a plurality of inner slots 4160 formed along the rotational direction of the pulley 4100 at a position spaced apart from the rotation center of the pulley 4100 by a predetermined first distance, and The pulley 4100 may include a plurality of outer slots 4130 formed along the rotational direction of the pulley 4100 at a position spaced apart by a second distance farther than the first distance from the rotation center of the pulley 4100.

In addition, the pulley 4100 is based on the inner slot 4160, the inner peripheral portion 4180 positioned on the centripetal side in the rotational radial direction of the pulley 4100, the pulley based on the outer slot 4130 The outer peripheral portion 4120 positioned on the centrifugal side in the radial direction of rotation of the 4100, the intermediate portion 4150 positioned between the inner slot 4160 and the outer slot 4130, between the plurality of inner slots 4160 Interposed between each of the plurality of inner bridges 4170 and the plurality of outer slots 4130 connecting the inner circumference 4180 and the intermediate portion 4150, the intermediate portion 4150 and the outer circumference portion 4120 ) May include a plurality of outer bridges 4140.

The plurality of inner slots 4160, the plurality of inner bridges 4170, the plurality of outer slots 4130, and the plurality of outer bridges 4140 include the pulley 4100 and the disk hub assembly 4200. While the contact force between them is included in the predetermined contact force range, the stiffness of the pulley 4100 is included in the predetermined stiffness range, and noise and vibration generated when contact is made between the pulley 4100 and the disk hub assembly 4200 It can be formed to be included in a predetermined noise vibration range.

Specifically, the plurality of inner slots 4160 and the plurality of inner bridges 4170 are formed of n (eg, six), and the n inner slots 4160 and the n inner bridges ( 4170) are alternately formed along the rotational direction of the pulley 4100, the n inner slots 4160 are formed in the same shape, and the n inner bridges 4170 can be formed in the same shape. have. That is, each inner slot 4160 is formed of an arcuate long hole extending along the rotational direction of the pulley 4100, spaced apart from each other along the rotational direction of the pulley 4100, and the plurality of inner slots 4160 All are formed in the same shape and may be spaced apart at equal intervals along the rotational direction of the pulley 4100.

In addition, the plurality of outer slots 4130 and the plurality of outer bridges 4140 are each formed of m different from the n pieces (for example, four), and the m outer slots 4130 and the m The four outer bridges 4140 are alternately formed along the rotational direction of the pulley 4100, the m outer slots 4130 are formed in the same shape, and the m inner bridges 4170 are the same shape. It can be formed as. That is, each outer slot 4130 is formed of an arcuate long hole extending along the rotational direction of the pulley 4100, spaced apart from each other along the rotational direction of the pulley 4100, the plurality of outer slots 4130 All are formed in the same shape and may be spaced apart at equal intervals along the rotational direction of the pulley 4100.

In addition, the plurality of inner slots 4160, the plurality of outer slots 4130, the plurality of inner bridges 4170, and the plurality of outer bridges 4140 may include the plurality of inner bridges 4170 and the plurality. The outer bridge 4140 of the pulley 4100 may be partially overlapped and partially non-overlapping in the rotational radial direction.

Here, the slots 4130 and 4160 and the bridges 4140 and 4170 are alternately formed, so that the length of the slots 4130 and 4160 (a value measured along the rotational direction of the pulley 4100) and the bridge ( The lengths of 4140 and 4170 (measured along the rotational direction of the pulley 4100) are inversely related to each other, and between the pulley 4100 and the disk hub assembly 4200 by the slots 4130 and 4160. The effect of improving the contact force and the effect of improving the rigidity of the pulley 4100 by the bridges 4140 and 4170 are inversely related to each other.

That is, when the length of the plurality of inner slots 4160 is increased, the cross-sectional area of the plurality of inner slots 4160 is increased, which is transmitted to the disk hub assembly 4200 through the plurality of inner slots 4160. The suction magnetic flux of the field coil assembly 4300 is increased, and a contact force between the pulley 4100 and the disk hub assembly 4200 can be improved. However, the length of the plurality of inner bridges 4170 is reduced, so that the rigidity of the pulley 4100 may be weakened.

On the other hand, when the length of the plurality of inner slots 4160 is reduced, the area of the plurality of inner slots 4160 is reduced, which is transmitted to the disk hub assembly 4200 through the plurality of inner slots 4160. The suction magnetic flux of the field coil assembly 4300 is reduced, and a contact force between the pulley 4100 and the disk hub assembly 4200 can be reduced. However, the length of the plurality of inner bridges 4170 is increased, so that the rigidity of the pulley 4100 can be enhanced.

Similarly, when the length of the plurality of outer slots 4130 is increased, the area of the plurality of outer slots 4130 is increased, and the disk hub assembly 4200 is provided through the plurality of outer slots 4130. The suction magnetic flux of the transmitted field coil assembly 4300 is increased, and a contact force between the pulley 4100 and the disk hub assembly 4200 can be improved. However, the length of the plurality of outer bridges 4140 is reduced, so that the rigidity of the pulley 4100 may be weakened.

And, when the length of the plurality of outer slots 4130 is reduced, the area of the plurality of outer slots 4130 is reduced, which is transmitted to the disk hub assembly 4200 through the plurality of outer slots 4130. The suction magnetic flux of the field coil assembly 4300 is reduced, and a contact force between the pulley 4100 and the disk hub assembly 4200 can be reduced. However, the length of the plurality of outer bridges 4140 is increased, so that the rigidity of the pulley 4100 can be enhanced.

In consideration of this, the lengths of the slots 4130 and 4160 and the lengths of the bridges 4140 and 4170 may be determined in advance when designing the first clutch 4000 in accordance with the performance and fatigue durability required for the clutch 4000.

Then, after the lengths of the slots 4130 and 4160 and the lengths of the bridges 4140 and 4170 are determined in advance, within the ranges of the determined lengths of the slots 4130 and 4160 and the lengths of the bridges 4140 and 4170. By forming the shapes of the slots 4130 and 4160 in a predetermined shape, the contact force between the pulley 4100 and the disk hub assembly 4200 and the rigidity of the pulley 4100 may be further improved. It will be described later.

The disk hub assembly 4200 may include a hub 4210 fastened to the rotating shaft 3000 and a disk 4220 extending from the hub 4210 and selectively contacting and spaced from the pulley 4100. have.

The field coil assembly 4300 may include a coil housing and a coil accommodated in the coil housing and generating electromagnetic force when power is applied.

The separation means (not shown) may be formed of an elastic member that applies a force to the disk hub assembly 4200 in a direction away from the pulley 4100.

The compressor according to this embodiment can be operated as follows.

That is, the pulley 4100 may be rotated by receiving a driving force from the driving source (not shown).

In this state, when power is applied to the coil, the disk hub assembly 4200 may be moved toward the pulley 4100 by the suction force due to the magnetic induction of the coil to be in close contact with the pulley 4100. That is, as the disk hub assembly 4200 and the pulley 4100 are engaged, power of the driving source (not shown) is transmitted to the rotating shaft 3000 through the pulley 4100 and the disk hub assembly 4200. Can be. In addition, the rotating shaft 3000 may compress the refrigerant by operating the compressor mechanism 2000 with the received power.

On the other hand, when the application of power to the coil is stopped, the suction force due to the magnetic induction of the coil is no longer generated, and the disk hub assembly 4200 is moved away from the pulley 4100 by the separation means (not shown). It may be moved in the direction to be spaced apart from the pulley 4100. That is, power transmission from the driving source (not shown) to the rotating shaft 3000 may be stopped. In addition, the compressor mechanism 2000 may be stopped and refrigerant compression may be stopped.

In this process, as the slots 4130 and 4160 are formed in the pulley 4100, when the power is applied to the coil, the suction flux of the field coil assembly 4300 delivered to the disk hub assembly 4200 By increasing this, the contact force between the pulley 4100 and the disk hub assembly 4200 may be increased.

Further, as the bridges 4140 and 4170 are formed in the pulley 4100, the weakening of the rigidity of the pulley 4100 by the slots 4130 and 4160 can be prevented.

Here, as described above, the lengths of the slots 4130 and 4160 and the lengths of the bridges 4140 and 4170 that are inversely related to each other are the first clutch 4000 in accordance with the performance and fatigue durability required for the clutch 4000. In design, it is determined in advance, and the shapes of the slots 4130 and 4160 are determined in a predetermined shape within the ranges of the lengths of the determined slots 4130 and 4160 and the lengths of the bridges 4140 and 4170, so that the pulley ( 4100) and the contact force between the disk hub assembly 4200 and the rigidity of the pulley 4100 may be further improved.

Specifically, referring to FIGS. 6 and 7, the inner slot 4160 has an inner slot centrifugal side inner surface opposite to a center of rotation of the pulley 4100 on a radially centrifugal side of the pulley 4100 ( 4161), the inner slot opposite to the inner slot centrifugal side inner surface 4161 at the centrifugal side in the radial direction of the pulley 4100, and the inner slot 4160 in the circumferential direction of the pulley 4100 ) May include an inner slot end side inner surface 4163 that connects the inner slot centrifugal side inner surface 4161 at the end side of the inner slot and the inner slot centripetal side inner surface 4162.

The inner slot centrifugal side inner surface 4161 has a curvature center 4161c of the inner slot centrifugal side inner surface located at a rotation center of the pulley 4100, and a radius of curvature 4101r of the inner slot centrifugal side inner surface is the It may be formed smaller than the radius of the pulley (4100).

In the inner slot centripetal side inner surface 4202, the center of curvature of the inner slot centripetal side inner surface is located at the center of rotation of the pulley 4100, and the radius of curvature 4202r of the inner surface of the inner slot centripetal side is the It may be formed smaller than the radius of curvature (4161r) of the inner surface of the inner slot centrifugal side.

The inner slot end side inner surface 4163 is curved from the inner slot centrifugal side inner surface 4161 to a radially centrifugal side of the pulley 4100, and then curved to a radially centripetal side of the pulley 4100. Again, it is curved to the centrifugal side in the radial direction of the pulley 4100, and may be formed to extend to the inner surface 4162 of the inner slot centripetal side.

More specifically, the inner slot end side inner surface 4163, the inner slot end side inner surface first curved surface 4164, which is curved in the radial direction of the pulley 4100 from the inner slot centrifugal side inner surface 4161, The inner slot end side inner surface second curved surface 4165 and the inner slot end side inner surface second curved surface 4165 curved from the inner slot end side inner surface first curved surface 4164 to the radially centripetal side of the pulley 4100 The inner slot end side inner surface third curved surface 4166 from the inner slot centripetal side inner surface 4162 curved in the radial direction centrifugal side of the pulley 4100 from the inner slot can do.

The inner slot end side inner surface second curved surface 4165 is such that the width of the inner slot 4160 (a value measured along the radial direction of the pulley 4100) is increased, so that the inner surface end side second curved surface A curvature center (4165c) is located inside the inner slot (4160), the inner slot end side inner surface second surface curvature radius (4165r) of the inner slot centrifugal side inner surface curvature radius (4161r) the inner slot It may be formed of a curved surface larger than half of the value obtained by subtracting the radius of curvature (4162r) of the inner surface of the centripetal side.

In addition, the inner curved surface 4165 of the inner side of the end portion of the inner slot extends along the rotational direction of the pulley 4100 from the centripetal side of the pulley 4100 relative to the inner slot 4160. The radius of curvature 4165r of the inner curved surface of the inner slot end side is prevented from the erosion of the annular wall 4190 for fastening the bearing by the inner curved surface 4165 of the inner slot end side. 2 The distance between the center of curvature of the curved surface (4165c) and the center of curvature of the annular wall for fastening the bearing (4190c) is to be formed with a surface less than or equal to the value obtained by subtracting the radius of curvature (4190r) of the outer peripheral surface of the ring for fastening the bearing. You can.

Here, the inner curved surface 4165 of the inner slot end side may be formed so that the length of the inner bridge 4170 is not reduced than a predetermined value.

That is, the center line 4170a of the inner bridge (an imaginary line connecting the center of the inner bridge 4170 and the center of rotation of the pulley 4100) and the reference curved surface 4169 (the pulley 4100) of the inner surface of the inner slot end side In the circumferential direction, the inner side of the inner slot 4160 is connected to the inner side of the inner slot 4161 at the end side of the inner slot 4160, and a center of curvature 4169c is formed inside the inner slot 4160. , The distance between the radius of curvature (4169r) is equal to half of the value obtained by subtracting the radius of curvature (4162r) of the inner surface of the inner slot from the radius of curvature (4161r) of the inner surface of the inner slot centrifugal side. ) Designed in advance, the distance between the center line (4170a) of the inner bridge and the inner surface second curved surface (4165) of the inner slot end side is a reference curved surface of the inner line (4170a) of the inner bridge and the inner surface of the inner slot end side. (4169) Even if it is equal to the distance between , The inner slot end side inner surface second curved surface 4165 is the inner center end side inner surface second curvature radius (4165r) of the inner surface end side inner surface second curvature center of the inner surface second curved surface (4165c) is It may be formed spaced apart from the inner bridge (4170).

In the inner slot end side inner surface first curved surface 4164, a notch in which stress can be concentrated is formed between the inner slot centrifugal side inner surface 4161 and the inner slot end side inner surface second curved surface 4165. In order not to be, the inner slot centrifugal side inner surface 4161 and the inner slot end side inner surface second curved surface 4165 may be formed in contact with both.

That is, the inner slot end side inner surface first curved surface 4164, the inner slot end side inner surface first curvature center (4164c) of the inner slot centrifugal side inner surface (4161) based on the pulley (4100) It is located on the centrifugal side in the radial direction, the inner surface of the inner surface of the first curved surface, the radius of curvature (4164r) of the inner surface of the inner end surface of the inner end surface of the first curved surface (4164c) and the inner surface of the inner surface end surface It is equal to a value obtained by subtracting the radius of curvature 4165r of the inner surface second curved surface at the distance between the centers of curvature 4165c of the inner slot, and the radius of curvature 4164r of the inner surface first curved surface at the inner slot end side is the inner surface. Same as the value obtained by subtracting the radius of curvature of the inner surface of the inner slot end side 4163 from the inner slot end side inner surface 4163c at a distance between the center of curvature 4164c of the inner surface of the slot end side and the center of curvature 4416c of the inner surface of the inner slot centrifugal side. Can be formed into curved surfaces .

In addition, the inner surface end side first curved surface 4164 may distribute the load applied between the inner slot centrifugal side inner surface 4161 and the inner slot end side inner surface second curved surface 4165 more effectively. A curvature radius 4164r of the inner curved surface of the inner slot end side may be formed as a curved surface larger than a curvature radius 4165r of the inner curved surface of the inner slot end side.

The inner slot end side inner surface third curved surface 4166 is such that a notch is not formed between the inner slot centripetal side inner surface 4162 and the inner slot end side inner surface second curved surface 4165, so that the inner slot centripetal side inner surface is formed. It may be formed of a curved surface that is in contact with both the (4162) and the inner surface second curved surface (4165) of the inner slot end side.

That is, the inner slot end-side inner surface third curved surface 4166 is a center of curvature 4166c of the inner surface end-side third curved surface based on the inner slot centripetal-side inner surface 4162 of the pulley 4100. The radius of curvature (4166r) of the inner surface end side inner surface third curved surface is radially located at the centripetal side, and the inner surface end side side inner surface second curved surface (4166c) and the inner slot end side inner surface second curved surface It is equal to the value obtained by subtracting the radius of curvature 4165r of the inner surface second curved surface at the distance between the centers of curvature 4165c of the inner slot, and the radius of curvature 4166r of the inner surface third curved surface 341r is the inner surface. A curved surface equal to the value obtained by subtracting the distance between the curvature center (4166c) of the inner surface third inner surface and the curvature center (4162c) of the inner slot centripetal side from the radius of curvature (4162r) of the inner surface of the slot centripetal side. Can be.

And, the inner curved surface 366 of the inner side of the inner end of the end slot, to more effectively distribute the load applied between the inner surface of the inner surface of the centripetal side of the inner slot and the second curved surface 4165 of the inner surface of the inner slot end side, A curvature radius 4166r of the inner surface end side third curved surface may be formed as a curved surface larger than a curvature radius 4165r of the inner surface end side second curved surface.

The inner slot 4160 according to the present embodiment having such a shape may increase the area of the inner slot 4160 without reducing the length of the inner bridge 4170. Accordingly, without weakening the rigidity of the pulley 4100, it is possible to improve the contact force between the pulley 4100 and the disk hub assembly 4200. And, as the contact force between the pulley 4100 and the disk hub assembly 4200 is improved without increasing the capacity of the field coil assembly 4300, the size according to the capacity increase of the field coil assembly 4300, The increase in weight and cost can be prevented.

In addition, the inner slot 4160 according to the present embodiment having such a shape can prevent damage to the pulley 4100 by preventing the inner slot 4160 from being damaged.

Specifically, as a result of the analysis, in the conventional case, damage was mainly generated in the inner slot 4160, which was found to be due to the end shape of the inner slot 4160.

More specifically, referring to FIGS. 3 and 4, in the conventional inner slot 4160, the center of curvature 4161c is located at the rotation center of the pulley 4100 and the radius of curvature 4161r is the pulley 4100. ), The inner surface of the inner slot centrifugal side smaller than the radius of (4161), the center of curvature (4162c) is located in the center of rotation of the pulley (4100) and the radius of curvature (4162r) than the radius of curvature (4161r) of the inner surface of the inner slot centrifugal side Connect the inner slot centrifugal side inner surface 4161 at the end side of the inner slot 4160 in the circumferential direction of the small inner slot centripetal side inner surface 4162 and the pulley 4100 and the inner slot centripetal side inner surface 4202 The inner slot end side inner surface 4163 is included, but the inner slot end side inner surface 4163 is different from the inner slot from the inner slot centrifugal side inner surface 4161 to the inner slot centripetal side inner surface 4162. Formed to be curved toward the centripetal side in the radial direction of (4100) do.

That is, in the conventional inner slot end side inner surface 4163, a curvature center 4416c of the inner slot end side inner surface is located inside the inner slot 4160, and a radius of curvature 4416r of the inner surface at the inner slot end side ) Is formed as a curved surface equal to half of a value obtained by subtracting the radius of curvature 4416r of the inner surface of the inner slot from the radius of curvature 4121r of the inner surface of the inner slot centrifugal side.

In the case of the conventional inner slot 4160 having such a shape, the pulley (not shown) by the drive belt (not shown) connecting the drive source (not shown) and the pulley 4100, as shown in the arrow in FIG. 4100) is applied to the inner slot centrifugal side inner surface 4161 and the inner slot end side inner surface 4163, the inner slot end side by the load applied to the inner slot end side inner surface 4163. An inner surface 4163 is bent based on the inner surface 4161 of the inner slot centrifugal side. Thereby, a crack is generated at a connection point between the inner surface centrifugal side inner surface 4161 of the inner slot and the inner surface 4163 of the inner slot end side, and the crack grows, and the inner slot 4160 is damaged, and the pulley ( 4100) is damaged.

On the other hand, in the case of this embodiment, as shown in Figures 6 and 7, the inner slot end side inner surface 4163 is curved from the inner slot centrifugal side inner surface 4161 to a radially centrifugal side of the pulley 4100. Then, it is formed to be curved toward the centripetal side in the radial direction of the pulley 4100 again. That is, the inner slot end side inner surface 4163 according to the present embodiment includes the inner slot end side inner surface first curved surface 4164 and the inner slot end side inner surface second curved surface 4165.

As a result, the load applied to the second curved surface 4165 on the inner surface at the inner slot end side is distributed in both directions, as shown by the arrow illustrated in FIG. 7, so that the inner slot end side inner surface 4163 is the inner slot centrifugal side inner surface. It is prevented from bending based on (4161), and cracks may be prevented from occurring at a connection point between the inner slot centrifugal side inner surface (4161) and the inner slot end side inner surface (4163). At this time, the inner slot end side inner surface first curved surface 4164, by flowing the load transmitted from the inner slot end side inner surface first surface 4164 to the inner slot centrifugal side inner surface 4161 smoothly, the inner It is possible to more effectively prevent a crack from being generated at a connection point between the slot centrifugal side inner surface 4161 and the inner slot end side inner surface 4163. Accordingly, damage to the inner slot 4160 may be prevented, and damage to the pulley 4100 may be prevented.

On the other hand, in the conventional case, the outer slot 4130 is formed in a shape similar to the inner slot 4160, but mainly the inner slot 4160 is damaged, and it is understood that the outer slot 4130 is hardly damaged. Became.

That is, the conventional outer slot 4130, the outer surface of the outer slot centrifugal side (4131), the pulley (4100) opposite to the center of rotation of the pulley (4100) from the centrifugal side in the radial direction of the pulley (4100) Outer slot centrifugal at the end side of the outer slot 4130 in the circumferential direction of the outer slot centrifugal side inner surface 4132 and the pulley 4100 facing the outer slot centrifugal side inner surface 4131 on the radially centripetal side And an outer slot end side inner surface 4133 connecting a side inner surface 4131 and the outer slot centripetal side inner surface 4132, wherein the outer slot end side inner surface 4133 is from the outer slot centrifugal side inner surface 4131. A crack between the outer slot centrifugal side inner surface 4131 and the outer slot end side inner surface 4133 is formed to be curved toward the centripetal side in the radial direction of the pulley 4100 up to the inner surface 4132 of the outer slot center side. Of was identified as not occurred.

As a result of analysis, this phenomenon, although the load applied to the pulley 4100 by the drive belt (not shown) also acts on the inner surface 4131 of the outer slot and the inner surface 4133 of the outer slot end side. As shown in the arrow shown in 3, it was understood that the load applied to the inner surface 4133 on the outer slot end side is distributed to the inner slot 4160 and the inner bridge 4170 through the outer bridge 4140. .

That is, the inner slot 4160 and the inner bridge 4170 between the outer slot 4130 and the annular wall 4190 for fastening the bearing and between the outer bridge 4140 and the annular wall 4190 for fastening the bearing. ) Is interposed, the load acting on the inner surface 4133 on the outer slot end side is distributed to the inner slot 4160 and the inner bridge 4170 through the outer bridge 4140, but the inner slot ( 4160) and the inner bridge 4170, the load acting on the inner surface 4163 of the inner slot end side is not distributed through the inner bridge 4170, as it is directly opposite the annular wall 4190 for fastening the bearing, Cracks hardly occur between the outer slot centrifugal side inner surface 4131 and the outer slot end side inner surface 4133, and between the inner slot centrifugal side inner surface 4161 and the inner slot end side inner surface 4163. It was found that cracks were occurring.

In consideration of this, in the present embodiment, in order to simplify the shape of the outer slot 4130, the shape of the outer slot 4130 may be formed similar to the shape of the conventional outer slot 4130.

That is, referring to FIGS. 6 and 7, the outer slot 4130 according to the present embodiment, the outer slot centrifugal opposite to the center of rotation of the pulley 4100 from the centrifugal side in the radial direction of the pulley 4100 Side inner surface 4131, the outer slot on the radially centripetal side of the pulley 4100 facing the outer slot centrifugal side inner surface 4131, the outer surface in the circumferential direction of the inner surface 4132 of the centripetal side and the pulley 4100 An outer slot end side inner surface 4133 connecting the outer slot centrifugal side inner surface 4131 and the outer slot centripetal side inner surface 4132 at an end side of the slot 4130, and the outer slot end side inner surface 4133 ) May be formed to be curved toward the centripetal side in the radial direction of the pulley 4100 from the outer surface centrifugal side inner surface 4131 of the outer slot to the inner surface 4132 of the outer slot.

Specifically, the outer slot centripetal side inner surface 4132, the center of curvature 4132c of the outer slot centripetal side is located at the rotation center of the pulley 4100, and the radius of curvature 4132r of the inner surface of the outer slot centripetal side ) May be formed as a curved surface larger than the radius of curvature 4161r of the inner surface of the inner slot centrifugal side.

In the outer slot centrifugal side inner surface 4131, the center of curvature 4131c of the outer slot centrifugal side inner surface is located at the center of rotation of the pulley 4100, and the radius of curvature 4131r of the inner surface of the outer slot centrifugal side is the It may be formed of a curved surface larger than the radius of curvature (4132r) of the inner surface of the outer slot centripetal side.

The outer slot end side inner surface 4133 may be formed according to a reference curved surface 4139 of the outer slot end side inner surface. That is, the outer slot end side inner surface 4133, the center of curvature 4133c of the outer slot end side inner surface is located inside the outer slot 4130, the radius of curvature 4133r of the inner surface of the outer slot end side The curvature radius 4131r of the inner surface of the outer slot centrifugal side may be formed as a curved surface equal to half of a value obtained by subtracting the curvature radius 4132r of the outer surface of the outer slot centripetal side.

The outer slot 4130 according to the present embodiment having such a shape can reduce manufacturing cost required to form the outer slot 4130 without causing breakage of the outer slot 4130.

On the other hand, in the present embodiment, the inner slot end side inner surface 4163 is curved from the inner slot centrifugal side inner surface 4161 to the centrifugal side in the radial direction of the pulley 4100, and then again of the pulley 4100. It is curved to the centripetal side in the radial direction, and is further curved to the centrifugal side in the radial direction of the pulley 4100 to be formed to extend to the inner surface 4202 of the inner slot.

However, the present invention is not limited thereto, and as illustrated in FIG. 8, the inner slot end side inner surface 4163 is curved from the inner slot centrifugal side inner surface 4161 to a radially centrifugal side of the pulley 4100. , It may be curved to the centripetal side in the radial direction of the pulley 4100 again to extend to the inner surface 4162 of the inner slot centripetal side.

That is, referring to Figure 8, in the compressor according to another embodiment of the present invention, the inner slot end side inner surface 4163, the inner slot centrifugal side inner surface 4161 from the radial direction of the pulley 4100 Inner slot end side inner surface first curved surface 4164, which is curved toward the centrifugal side, a portion curved from the inner curved end side inner surface first curved surface 4164 toward the centripetal side in the radial direction of the pulley 4100, inner inner end surface 2 The curved surface 4165 and the inner surface of the inner slot end side are curved from the second curved surface 4165 to the centripetal side in the radial direction of the pulley 4100, and the radial direction of the pulley 4100 from the inner slot centripetal side inner surface 4162 It may include a fourth curved surface (4167) the inner surface end side curved inner slot end.

The inner slot end side inner surface first curved surface 4164 and the inner slot end side inner surface second curved surface 4165 may be formed as described above.

On the other hand, the inner slot end side inner surface fourth curved surface (4167) is in contact with both the inner slot centripetal side inner surface (4162) and the inner slot end side inner surface second curved surface (4165), the inner slot end side inner surface agent The curvature center 4171c of the 4 curved surfaces may be formed as a curved surface located inside the inner slot 4160.

That is, in the inner slot end side inner surface fourth curved surface 4167, the inner center end side side inner surface 467c of the curvature center of the fourth curved surface is located inside the inner slot 4160, the inner slot end side inner surface A curvature radius (4167r) of the fourth curved surface is an inner surface of the inner slot end side at an inner surface of the second curved surface (4165r), and a curvature center (4167c) of the fourth curved surface and an inner surface of the inner slot end side (2) It is equal to the value obtained by subtracting the distance between the centers of curvature 4165c of the curved surface, and the radius of curvature 4167r of the inner surface fourth curved surface at the inner slot end side is equal to the center of curvature 4167c of the fourth curved surface at the inner surface at the inner slot end side. It may be formed of a curved surface equal to a value obtained by subtracting the radius of curvature 4416r of the inner surface of the inner slot centripetal distance from a distance between the centers of curvature 4416c of the inner surface of the inner slot centripetal side.

Here, the fourth curved surface (4167) of the inner surface of the inner slot end side allows the load applied between the inner surface of the inner slot centripetal side (4162) and the second curved surface (4165) of the inner slot end side to be more effectively distributed. The inner center end end side and the inner center centrifugal side distance and the distance to the inner surface centrifugal side inner side surface 4161 of the inner curved surface 441a of the inner curved surface 467a (in the rotational radial direction of the pulley 4100) The inner surface 4162 is located on a virtual line connecting the same points), and the inner surface end-side inner surface fourth curvature radius (4167r) of the inner slot centrifugal side inner surface radius of curvature (4161r) It may be formed of a curved surface equal to half of a value obtained by subtracting the radius of curvature 4162r of the inner surface of the inner slot centripetal side.

In this case, the crack generation prevention effect between the inner slot centrifugal side inner surface 4161 and the inner slot end side inner surface 4163 is at the same level, but the area of the inner slot 4160 is reduced, so that the pulley 4100 and the The contact force between the disk hub assemblies 4200 may be somewhat reduced.

However, in this case, the annular wall 4190 for fastening the bearing can be easily prevented from being eroded by the inner surface 4163 of the inner slot end.

That is, according to this case, when the distance between the inner slot 4160 and the annular wall 4190 for fastening the bearing is narrow, without erosion of the annular wall 4190 for fastening the bearing by the inner slot 4160 , While cracking between the inner slot centrifugal side inner surface 4161 and the inner slot end side inner surface 4163 is prevented, the area of the inner slot 4160 is increased to increase the area of the pulley 4100 and the disk hub assembly 4200 ) May increase the contact force.

On the other hand, in the case of the present embodiment, the inner slot end side inner surface 4163 has a favorable symmetrical structure in terms of durability, noise, and vibration, so that the inner surface end side second curved surface has a curvature center (4165c). ) May be formed on the center line 4160a of the inner slot.

However, the present invention is not limited thereto, and the curvature center 4165c of the inner surface second curved surface may be formed at any position inside the inner slot 4160.

2000: Compressor
3000: rotating shaft
4100: pulley
4130: outer slot
4130a: Centerline of outer slot
4131: outer slot centrifugal side inner surface
4131c: Center of curvature of the inner surface of the outer slot
4131r: radius of curvature of the inner surface of the outer slot
4132: outer slot centripetal inner surface
4132c: Center of curvature on the inner side of the outer slot center
4132r: Curvature radius of the inner surface of the outer slot center
4133: outer slot end side inner surface
4133c: Center of curvature on the inner side of the outer slot end
4133r: Curvature radius of the inner surface of the outer slot end
4139: reference surface of the inner surface of the outer slot end side
4139c: Center of curvature of the reference surface of the inner surface at the end of the outer slot
4139r: radius of curvature of the reference surface of the inner surface at the end of the outer slot
4140: outer bridge
4140a: Centerline of outer bridge
4160: inner slot
4160a: Centerline of inner slot
4161: inner slot centrifugal side inner surface
4161c: Center of curvature of the inner surface of the inner slot centrifugal side
4161r: Curvature radius of the inner surface of the inner slot centrifugal side
4162: inner slot inner core
4162c: Inner slot center of curvature inside the center
4162r: Curvature radius of the inner surface of the inner slot centripetal side
4163: inner slot end side inner surface
4136: the outer surface of the outer slot end third curved surface
4164: Inner slot end side inner surface first curved surface
4164c: Center of curvature of the inner surface first curved surface at the end of the inner slot
4164r: Curvature radius of the inner surface first curved surface at the end of the inner slot
4165: Inner slot end side inner surface second curved surface
4165c: Center of curvature of the second curved surface inside the inner slot end
4165r: The radius of curvature of the second curved inner surface of the inner slot end
4166: Inner slot end side inner surface third curved surface
4166c: Center of curvature of the inner third surface
4166r: The radius of curvature of the inner surface end side third curved surface
4167: Inner slot end side inner surface fourth curved surface
4167c: The center of curvature of the fourth curved surface on the inner side of the inner slot
4167r: The radius of curvature of the fourth curved surface on the inner side of the inner slot end
4169: reference surface of the inner surface at the end of the inner slot
4169c: Center of curvature of the reference surface of the inner surface at the end of the inner slot
4169r: radius of curvature of the reference surface of the inner surface at the end of the inner slot
4170: inner bridge
4170a: center line of inner bridge
4190: annular wall for fastening bearings
4190c: Center of curvature of the annular wall for fastening the bearing
4190r: radius of curvature of the outer peripheral surface of the annular wall for fastening the bearing
4200: Disc hub assembly

Claims (14)

A disk hub assembly 4200 engaged with the rotating shaft 3000 of the compression mechanism 2000; And
Includes a pulley (4100) that is rotated by receiving power from a drive source and selectively intermittent with the disk hub assembly (4200);
The pulley 4100 includes an inner slot 4160 and an outer slot 4130,
The inner slot 4160 may include: an inner slot centrifugal side inner surface 4161 opposite to a center of rotation of the pulley 4100 on a radially centrifugal side of the pulley 4100; An inner slot centrifugal side inner surface 4162 opposite to the inner slot centrifugal side inner surface 4161 at the centripetal side in the radial direction of the pulley 4100; And an inner slot end side inner surface 4163 connecting the inner slot centrifugal side inner surface 4161 and the inner slot centripetal side inner surface 4162.
The inner slot end side inner surface 4163 includes: an inner slot end side inner surface first curved surface 4164 that is curved toward the centrifugal side in the radial direction of the pulley 4100 from the inner slot centrifugal side inner surface 4161; And an inner slot end side inner surface second curved surface 4165 curved from the inner slot end side inner surface first curved surface 4164 to a radially centripetal side of the pulley 4100. According to claim 1,
A curvature center 4161c of the inner surface of the inner slot centrifugal side is formed at the rotation center of the pulley 4100,
The radius of curvature (4161r) of the inner surface of the inner slot centrifugal side is formed smaller than the radius of the pulley (4100),
The center of curvature 4416c of the inner surface of the inner slot centripetal side is formed at the rotation center of the pulley 4100,
The radius of curvature 4202r of the inner surface of the inner slot centripetal side is formed smaller than the radius of curvature 4121r of the inner surface of the inner slot centrifugal side,
A curvature center 4165c of the inner surface second curved surface of the inner slot end side is formed inside the inner slot 4160,
The radius of curvature 4165r of the inner curved surface of the inner slot end side is greater than half of a value obtained by subtracting the radius of curvature 4416r of the inner surface of the inner slot centroid from the radius of curvature 4161r of the inner surface of the inner slot centrifugal side. Compressor. According to claim 2,
In the radial direction of rotation of the pulley 4100, a virtual line connecting dots having the same distance to the inner slot centrifugal side inner surface 4161 and the inner slot centripetal side inner surface 4162 is center line 4160a of the inner slot )
A compressor formed at a center line 4160a of the inner slot is the curvature center 4165c of the inner curved surface of the inner slot end side. According to claim 3,
A curvature center (4164c) of the inner surface end surface of the inner slot end side is formed on the centrifugal side in the radial direction of the pulley (4100) with respect to the inner slot centrifugal side inner surface (4161),
The radius of curvature 4164r of the inner surface first curved surface at the inner slot end side is at a distance between the center of curvature 4164c of the inner curved first surface and the inner curved surface 464c of the inner curved surface at the inner slot end side. It is formed equal to the value obtained by subtracting the radius of curvature 4165r of the inner surface second curved surface at the end portion of the inner slot,
The radius of curvature 4164r of the inner surface end surface of the inner slot end side is the inner slot at a distance between the center of curvature 4164c of the inner surface first curved surface and the center of curvature of the inner surface of the inner slot centrifugal side 4161c. Compressor formed equal to the value obtained by subtracting the radius of curvature (4161r) of the inner surface of the centrifugal side. According to claim 4,
The pulley 4100 may include an annular wall 4190 for fastening a bearing extending along a rotational direction of the pulley 4100 on a radially centered side of the pulley 4100 based on the inner slot 4160; Including more,
The radius of curvature 4165r of the inner curved surface of the inner side of the inner slot end is fastened to the bearing at a distance between the center of curvature 4165c of the inner curved surface of the inner slot end and the radius of curvature 4190c of the annular wall for fastening the bearing. Compressor formed less than or equal to the value obtained by subtracting the radius of curvature (4190r) of the outer circumferential surface of the toroidal wall. According to claim 4,
The inner slot end side inner surface of the first surface of the curvature radius (4164r) is formed larger than the inner radius of the second surface of the curvature radius (4165r) of the compressor. According to claim 4,
The inner slot end side inner surface 4163 is curved from the inner slot centripetal side inner surface 4162 to the centripetal side in the radial direction of the pulley 4100, and the inner pulley side inner surface second curved surface 4165 to the pulley ( 4100) radially in the centrifugal side of the inner slot end side of the inner surface of the third curved surface (4166); further comprising a compressor. The method of claim 7,
A curvature center (4166c) of the inner surface third curved surface of the inner slot end side is formed on a radially centripetal side of the pulley (4100) with respect to the inner slot apical inner surface (4162),
The radius of curvature 4166r of the inner surface end side third curved surface is at a distance between the inner center end side inner surface third curved surface center of curvature 4166c and the inner slot end side inner surface second curved surface center of curvature 4165c. It is formed equal to the value obtained by subtracting the radius of curvature 4165r of the inner surface second curved surface at the end portion of the inner slot,
The radius of curvature (4166r) of the inner surface end surface third curved surface at the inner slot end side is the curvature center (4166c) of the inner surface end surface third curved surface and the inner slot centrifugal side at the curvature radius (4162r) of the inner slot centripetal side inner surface. Compressor formed equal to the value obtained by subtracting the distance between the inner curvature centers (4162c). The method of claim 8,
The inner slot end side inner surface of the inner surface of the third surface of the radius of curvature (4166r) is formed larger than the inner radius of the inner surface of the second surface of the radius of curvature (4165r) of the compressor. According to claim 4,
The inner slot end side inner surface 4163 is curved toward the centrifugal side in the radial direction of the inner pulley 4100 from the inner slot centripetal inner side surface 4162, and the inner pulley side inner surface second surface 4165 to the pulley ( The compressor further comprising an inner surface end surface fourth curved surface 4171 that curves toward the centripetal side in the radial direction of 4100). The method of claim 10,
A curvature center (4167c) of the inner surface fourth curved surface of the inner slot end side is formed inside the slot (4160),
The radius of curvature (4167r) of the inner curved surface of the inner surface of the inner slot end side is a curvature center (4167c) of the inner curved surface of the inner surface of the inner curved surface of the inner curved surface of the inner surface of the second curved surface (4165r). It is formed equal to the value obtained by subtracting the distance between the centers of curvature (4165c) of the second curved surface on the inner surface of the slot end,
The inner slot end-side inner surface fourth curvature radius (4167r) is the inner slot at a distance between the inner center end-side inner surface fourth curvature center (4167c) and the inner slot centripetal inner surface curvature center (4162c). Compressor formed equal to the value obtained by subtracting the radius of curvature (4162r) of the inner surface of the centripetal side. The method of claim 11,
A curvature center (4167c) of the inner surface fourth curved surface at the inner slot end side is formed on the center line (4160a) of the inner slot,
The radius of curvature (4167r) of the inner surface of the inner surface of the inner slot end is formed equal to half of a value obtained by subtracting the radius of curvature (4162r) of the inner surface of the inner slot from the radius of curvature (4161r) of the inner surface of the inner slot centrifugal side. Compressor. According to claim 1,
The outer slot 4130,
A center of curvature 4132c is formed at the center of rotation of the pulley 4100, and a radius of curvature 4132r is formed larger than a radius of curvature 4161 of the inner surface of the inner slot centrifugal surface 4132r;
A center of curvature 4131c is formed at the center of rotation of the pulley 4100, and a radius of curvature 4131r is larger than the radius of curvature 4132r of the inner surface of the outer slot centrifugal side 4131r; And
It includes; the outer slot end side inner surface (4133) connecting the outer slot centrifugal side inner surface (4131) and the outer slot centripetal side inner surface (4132);
The outer slot end side inner surface 4133 is a compressor formed to be curved radially on the centripetal side of the pulley 4100 from the outer slot centrifugal side inner surface 4131 to the outer slot centripetal side inner surface 4132. The method of claim 13,
A curvature center 4133c of the inner surface of the outer slot end side is formed inside the outer slot 4130,
The outer slot end side curvature radius (4133r) of the inner surface is equal to half the value formed by subtracting the curvature radius (4132r) of the outer slot centripetal side inner surface from the curvature radius (4131r) of the outer slot centrifugal side.

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