KR102625094B1 - Compressor - Google Patents

Abstract

The present invention relates to a compressor, comprising a disk hub assembly coupled to the rotation axis of the compression mechanism and a pulley that receives power from a drive source and rotates and is selectively interconnected with the disk hub assembly, and the pulley includes an inner slot and an outer slot. And, the inner slot includes an inner slot centrifugal side inner surface, an inner slot centripetal side inner surface, and an inner slot end side inner surface, and the inner slot end side inner surface extends from the inner slot centrifugal side inner surface to the centrifugal side in the radial direction of the pulley. a first curved surface on the inner surface at the end of the inner slot that is curved; and a second inner curved surface on the inner slot end side, which is curved from the first inner surface on the inner slot end side toward the centripetal side in the radial direction of the pulley. By this, it is possible to simultaneously increase the contact force between the pulley and the disk hub assembly, secure the rigidity of the pulley, reduce size, reduce weight, and reduce costs. Additionally, damage to the pulley can be prevented by preventing damage from occurring in the slot of the pulley.

Description

Compressor{COMPRESSOR}

The present invention relates to a compressor, and more specifically, 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, automobiles are equipped with air conditioning (A/C) for interior cooling and heating. This air conditioning device is a component of the cooling system and includes a compressor that compresses low-temperature, low-pressure gaseous refrigerant drawn from the evaporator into high-temperature, high-pressure gaseous refrigerant and sends it to the condenser.

There are two types of compressors: a reciprocating type that compresses the refrigerant according to the reciprocating motion of the piston, and a rotary type that performs compression while rotating the piston. Depending on the transmission method of the drive source, the reciprocating type includes the crank type, which uses a crank to transmit power to a plurality of pistons, and the swash plate type, which uses a rotating shaft with a swash plate installed. The rotary type includes the vane rotary type, which uses a rotating rotary shaft and vanes. There are scroll types that use orbital scrolls and fixed scrolls.

Such a compressor typically includes a rotating shaft that transmits rotational force to a compression mechanism that compresses the 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 selectively receive power and operate.

FIG. 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 view of part A of FIG. 2, and FIG. 4 is an enlarged view of part B of FIG. 2. .

Referring to the attached FIGS. 1 to 4, a conventional compressor includes a casing 1000, a compression mechanism 2000 provided inside the casing 1000 and compressing the refrigerant, and a compression mechanism 2000 provided outside the casing 1000. A rotating shaft 3000 that transmits rotational force from a driving source (e.g., an engine) (not shown) to the compression mechanism 2000, and a clutch 4000 that selectively controls the driving source (not shown) and the rotating shaft 3000. ) includes.

The clutch 4000 includes a pulley 4100 that receives power from the drive source (not shown) and rotates, and a disk hub assembly 4200 that is engaged with the rotation shaft 3000 and selectively contacts and is spaced apart from the pulley 4100. ), and a field coil assembly 4300 that is magnetized when power is applied and brings the pulley 4100 and the disk hub assembly 4200 into contact.

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

In addition, a friction surface that can be contacted with the later-described disk 4220 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 is formed into which the field coil assembly is inserted and mounted.

In addition, the pulley 4100 is configured to increase the attractive magnetic flux of the field coil assembly 4300 transmitted to the disk hub assembly 4200, thereby increasing the contact force between the pulley 4100 and the disk hub assembly 4200. , It includes a plurality of slots (slots) 4130 and 4160 that pass through the pulley 4100 and are formed along the rotation direction of the pulley 4100.

In addition, the pulley 4100 includes a plurality of bridges 4140 and 4170 interposed between the plurality of slots 4130 and 4160 to improve the rigidity of the pulley 4100.

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

In addition, the pulley 4100 has an inner peripheral portion 4180 located on the centripetal side in the rotational radial direction of the pulley 4100 with respect to the inner slot 4160, and an inner peripheral portion 4180 with respect to the outer slot 4130. An outer peripheral portion 4120 located on the centrifugal side in the rotational radial direction of 4100, a middle portion 4150 located between the inner slot 4160 and the outer slot 4130, and between the plurality of inner slots 4160. A plurality of inner bridges 4170 interposed between each and connecting the inner peripheral portion 4180 and the middle portion 4150, and interposed between the plurality of outer slots 4130 and between the middle portion 4150 and the outer peripheral portion 4120. ) includes a plurality of outer bridges 4140 connecting the.

The disk hub assembly 4200 includes a hub 4210 coupled to the rotation shaft 3000 and a disk 4220 extending from the hub 4210 and selectively contacting and spaced apart 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.

A conventional compressor according to this configuration operates as follows.

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

In this state, when power is applied to the coil, the disc hub assembly 4200 moves toward the pulley 4100 and comes into close contact with the pulley 4100 due to the attractive force generated by the magnetic induction of the coil. That is, when the disk hub assembly 4200 and the pulley 4100 are coupled, the power of the drive source (not shown) is transmitted to the rotation shaft 3000 through the pulley 4100 and the disk hub assembly 4200. do. And, the rotating shaft 3000 operates the compression 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 attractive force due to magnetic induction of the coil is no longer generated, and the disk hub assembly 4200 moves in a direction away from the pulley 4100, thereby moving the pulley 4100. is separated from That is, power transmission from the drive source (not shown) to the rotation shaft 3000 is stopped. Then, the compression mechanism 2000 stops operating, and refrigerant compression stops.

However, in this conventional compressor, there was a problem that it was not possible to simultaneously increase the contact force between the pulley 4100 and the disk hub assembly 4200, secure the rigidity of the pulley 4100, reduce size, reduce weight, and reduce cost.

Specifically, as the length of the slots 4130 and 4160 (measured along the rotation direction of the pulley 4100) becomes longer, the area of the slots 4130 and 4160 increases, and the disk hub assembly 4200 The attractive magnetic flux of the field coil assembly 4300 transmitted to increases, thereby improving the 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 (value measured along the rotation direction of the pulley 4100) becomes shorter, and the rigidity of the pulley 4100 decreases. weakened.

On the other hand, as the length of the slots 4130 and 4160 becomes shorter, the area of the slots 4130 and 4160 decreases, and the attractive magnetic flux of the field coil assembly 4300 transmitted to the disk hub assembly 4200 decreases. As a result, the contact force between the pulley 4100 and the disk hub assembly 4200 is weakened. However, as the length of the slots 4130 and 4160 becomes shorter, the length of the bridges 4140 and 4170 increases, thereby improving the rigidity of the pulley 4100.

In consideration of this, the length of the bridges 4140 and 4170 is increased to improve the rigidity of the pulley 4100, and in return, the contact force between the pulley 4100 and the disk hub assembly 4200 is weakened. In order to solve this, a plan to increase the capacity of the field coil assembly 4300 may be considered. However, in this case, there is a problem that the size, weight, and cost increase as the length of the bridges 4140 and 4170 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 ensure the rigidity of the pulley 4100, but damage occurs in the slots 4130 and 4160, causing damage to the pulley 4100. There was a problem.

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

Therefore, the purpose of the present invention is to provide a compressor that can simultaneously increase the contact force between the pulley and the disk hub assembly, secure the rigidity of the pulley, reduce size, reduce weight, and reduce cost.

Another object of the present invention is to provide a compressor that can prevent damage to the pulley by preventing breakage in the slot of the pulley.

The present invention, in order to achieve the above-described object, includes a disk hub assembly coupled to the rotation axis of a compression mechanism; and a pulley that rotates by receiving power from a drive source and is selectively interconnected with the disk hub assembly, wherein the pulley includes: an inner slot formed along the rotation direction of the pulley at a position spaced apart from the rotation center of the pulley; and an outer slot formed along the rotation direction of the pulley at a position spaced further from the rotation center of the pulley than the inner slot, wherein the inner slot rotates the pulley on a distal side in the radial direction of the pulley. an inner surface on the centrifugal side of the inner slot opposite to the center side; an inner slot centripetal side inner surface opposite to the inner slot centrifugal inner surface on 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 centripetal side inner surface, wherein the inner slot end side inner surface is curved from the inner slot centrifugal side inner surface to the centrifugal side in the radial direction of the pulley. a first curved surface on the inner surface of the inner slot end side; and a second inner curved surface on the inner slot end side, which is curved from the first inner surface on the inner slot end side toward the centripetal side in the radial direction of the pulley.

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

If the center line of the inner slot is an imaginary line connecting points where the distance to the inner surface of the centrifugal side of the inner slot and the inner surface of the inner slot centripetal side in the rotation radial direction of the pulley are the same, then the second inner surface of the inner slot end side 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 first curved surface on the inner surface at the end of the inner slot is formed on the distal side in the radial direction of the pulley with respect to the inner surface on the distal side of the inner slot, and the radius of curvature of the first curved surface on the inner surface on the end of the inner slot is the radius of curvature of the first curved surface on the inner surface at the end of the inner slot. It is formed equal to the distance between the center of curvature of the first inner curved surface on the end side and the center of curvature of the second inner curved surface on the end of the inner slot minus the radius of curvature of the second inner curved surface on the end of the inner slot, and the end of the inner slot The radius of curvature of the first inner surface on the inner slot side is formed equal to the value obtained by subtracting the radius of curvature of the inner surface on the centrifugal side of the inner slot from the distance between the center of curvature of the first curved surface on the inner slot end side and the center of curvature on the inner surface on the distal side of the inner slot. It can be.

The pulley further includes an annular wall for bearing fastening extending along the rotational direction of the pulley from a centripetal side in the radial direction of the pulley with respect to the inner slot, and a radius of curvature of the second curved surface on the inner surface at the end of the inner slot. may be formed to be less than or equal to the value obtained by subtracting the radius of curvature of the outer peripheral surface of the annular wall for fastening the bearing from the center of curvature of the second curved surface on the inner surface at the end of the inner slot and the center of curvature of the annular wall for fastening the bearing.

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

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

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

The radius of curvature of the third inner curved surface at the end of the inner slot may be greater than the radius of curvature of the second curved surface of the inner surface at the end of the inner slot.

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

The center of curvature of the fourth inner curved surface at the end of the inner slot is formed inside the slot, and the radius of curvature of the fourth inner curved surface at the end of the inner slot is the radius of curvature of the second curved surface at the end of the inner slot at the end of the inner slot. It is formed equal to the distance between the center of curvature of the fourth inner curved surface on the end side and the center of curvature of the second inner curved surface on the end side of the inner slot, and the radius of curvature of the fourth inner curved surface on the end side of the inner slot is the end of the inner slot. It may be formed equal to the distance between the center of curvature of the fourth curved surface of the inner slot and the center of curvature of the inner surface of the inner slot centripetal side minus the radius of curvature of the inner surface of the inner slot centripetal side.

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

The outer slot has a center of curvature formed at the center of rotation of the pulley, and a radius of curvature is formed to be larger than a radius of curvature of the inner surface on the centrifugal side of the inner slot; an outer slot centrifugal side inner surface whose center of curvature is formed at the rotation center of the pulley and a radius of curvature formed to be larger than a curvature radius of the outer slot centrifugal side inner surface; 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 extends from the outer slot centrifugal-side inner surface to the outer slot centripetal-side inner surface of the pulley. It may be formed to be curved toward the centripetal side in the radial direction.

The center of curvature of the inner surface on the end side of the outer slot is formed inside the outer slot, and the radius of curvature of the inner surface on the end side of the outer slot is calculated by subtracting the radius of curvature of the inner surface on the centrifugal side of the outer slot from the radius of curvature of the inner surface on the centrifugal side of the outer slot. It can be formed to be equal to half of one value.

The compressor according to the present invention includes a disk hub assembly coupled to the rotating shaft of the compression mechanism; and a pulley that receives power from a drive source and rotates and is selectively interconnected with the disk hub assembly, wherein the pulley includes an inner slot and an outer slot, wherein the inner slot is an inner slot on the centrifugal side of the inner slot and an inner slot on the centripetal side of the inner slot. It includes an inner surface and an inner slot side inner surface, wherein the inner slot end side inner surface is a first curved surface of the inner slot end side inner surface curved from the inner slot centrifugal side inner surface to the distal side in the radial direction of the pulley; and a second inner curved surface on the inner slot end side that is curved from the first inner surface on the inner slot end side to the centripetal side in the radial direction of the pulley. By including a, the contact force between the pulley and the disk hub assembly increases, the rigidity of the pulley is secured, and the size is reduced. , weight reduction and cost reduction can be achieved at the same time.

Additionally, damage to the pulley can be prevented by preventing breakage from occurring in the slot of the pulley.

1 is a cross-sectional view showing a conventional compressor;
Figure 2 is a front view showing a pulley in the compressor of Figure 1;
Figure 3 is an enlarged view of part A of Figure 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;
Figure 7 is an enlarged view of part D of Figure 5;
Figure 8 is a front view showing a portion of a pulley in a 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 attached drawings.

Figure 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, and Figure 7 is an enlarged view of part D of Figure 5.

Meanwhile, components not shown in FIGS. 5 to 7 refer to FIG. 1 for convenience of explanation.

Referring to the attached FIGS. 5 to 7 and FIG. 1, the compressor according to an embodiment of the present invention includes a casing 1000, a compression mechanism 2000 provided inside the casing 1000 and compressing the refrigerant, A rotating shaft 3000 that transmits rotational force from a driving source (for example, an engine) (not shown) provided outside the casing 1000 to the compression mechanism 2000, and the driving source (not shown) and the rotating shaft 3000 ) may include a power transmission mechanism that selectively connects and disconnects.

The compression mechanism 2000 is fastened to a piston 2100 capable of reciprocating movement within the bore of the casing 1000 and the rotation shaft 3000 and rotates with the rotation shaft 3000, and the piston 2100 It may include a swash plate 2200 that reciprocates.

Here, in the present embodiment, the compression mechanism 2000 is formed in a swash plate type including the piston 2100 and the swash plate 2200, but includes a rotating scroll that receives the rotational force of the rotating shaft 3000 and rotates. It can be formed in various ways, such as a scroll method including a fixed scroll engaged with the orbiting scroll.

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

The power transmission mechanism is magnetized when power is applied to connect the drive source (not shown) and the rotation shaft 3000, and when power is cut off, it is demagnetized to separate the drive source (not shown) and the rotation shaft 3000 (clutch) 4000).

The clutch 4000 includes a pulley 4100 that receives power from the drive source (not shown) and rotates, and a disk hub assembly 4200 that is engaged with the rotation shaft 3000 and selectively contacts and is spaced apart from the pulley 4100. ), the field coil assembly 4300 is magnetized when power is applied and contacts the pulley 4100 and the disk hub assembly 4200, and the field coil assembly 4300 is cut off when power is cut off. It may include a spacer (not shown) that separates the pulley 4100 and the disk hub assembly 4200 when the device is deviced.

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

In addition, a friction surface that can be contacted with the later-described disk 4220 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 receiving groove for the field coil assembly into which is inserted and mounted may be formed.

In addition, the pulley 4100 is configured to increase the attractive magnetic flux of the field coil assembly 4300 transmitted to the disk hub assembly 4200, thereby increasing the contact force between the pulley 4100 and the disk hub assembly 4200. , It may include a plurality of slots (slots) 4130 and 4160 that pass through the pulley 4100 and are formed along the rotation 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 to improve the rigidity of the pulley 4100.

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

In addition, the pulley 4100 has an inner peripheral portion 4180 located on the centripetal side in the rotational radial direction of the pulley 4100 with respect to the inner slot 4160, and an inner peripheral portion 4180 with respect to the outer slot 4130. An outer peripheral portion 4120 located on the centrifugal side in the rotational radial direction of 4100, a middle portion 4150 located between the inner slot 4160 and the outer slot 4130, and between the plurality of inner slots 4160. A plurality of inner bridges 4170 interposed between each and connecting the inner peripheral portion 4180 and the middle portion 4150 and the plurality of outer slots 4130 and interposed between the middle portion 4150 and the outer peripheral portion 4120 ) may include a plurality of outer bridges 4140 connecting them.

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 are connected to the pulley 4100 and the disk hub assembly 4200. As the contact force between them is included in the predetermined contact force range, the rigidity of the pulley 4100 is included in the predetermined rigidity range, and noise and vibration generated when contact between the pulley 4100 and the disk hub assembly 4200 It can be configured to fall within this predetermined noise and vibration range.

Specifically, the plurality of inner slots 4160 and the plurality of inner bridges 4170 are formed in n pieces (for example, 6 pieces), and the n inner slots 4160 and the n inner bridges ( 4170) may be formed alternately along the rotation direction of the pulley 4100, wherein the n inner slots 4160 may be formed to have the same shape, and the n inner bridges 4170 may be formed to have the same shape. there is. That is, each inner slot 4160 is formed as an arc-shaped long hole extending along the rotation direction of the pulley 4100, and is spaced apart from each other along the rotation direction of the pulley 4100, and the plurality of inner slots 4160 are all formed in the same shape and may be spaced apart at equal intervals along the rotation 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 numbers (e.g., 4 pieces) different from the n number, and the m number of outer slots 4130 and the m number are different from the n number. Outer bridges 4140 are formed alternately along the rotation direction of the pulley 4100, wherein the m outer slots 4130 are formed to have the same shape, and the m inner bridges 4170 are formed to have the same shape. can be formed. That is, each outer slot 4130 is formed as an arc-shaped long hole extending along the rotation direction of the pulley 4100, and is spaced apart from each other along the rotation direction of the pulley 4100, and the plurality of outer slots 4130 are all formed in the same shape and may be spaced apart at equal intervals along the rotation direction of the pulley 4100.

And, 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 are the plurality of inner bridges 4170 and the plurality of outer bridges 4140. The outer bridge 4140 may be formed to partially overlap and partially not overlap in the rotation radius direction of the pulley 4100.

Here, the slots 4130 and 4160 and the bridges 4140 and 4170 are formed alternately, so that the length of the slots 4130 and 4160 (measured along the rotation direction of the pulley 4100) and the bridge ( The lengths (values measured along the rotation direction of the pulley 4100) of 4140 and 4170 are inversely proportional to each other, and the distance 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 proportional to each other.

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

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

In addition, when the length of the plurality of outer slots 4130 is reduced, the area of the plurality of outer slots 4130 is reduced, so that the power transmitted to the disk hub assembly 4200 through the plurality of outer slots 4130 The attractive magnetic flux of the field coil assembly 4300 may be reduced, and the contact force between the pulley 4100 and the disk hub assembly 4200 may be reduced. However, by increasing the length of the plurality of outer bridges 4140, the rigidity of the pulley 4100 can be strengthened.

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

And, after the lengths of the slots (4130, 4160) and the lengths of the bridges (4140, 4170) are determined in advance, the lengths of the slots (4130, 4160) and the bridges (4140, 4170) are within the determined range. By forming the slots 4130 and 4160 into a predetermined shape, the contact force between the pulley 4100 and the disk hub assembly 4200 and the rigidity of the pulley 4100 can be further improved. This will be described later.

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

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

The compressor according to this embodiment may operate as follows.

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

In this state, when power is applied to the coil, the disc hub assembly 4200 may move toward the pulley 4100 and come into close contact with the pulley 4100 due to the attractive force caused by magnetic induction of the coil. That is, when the disk hub assembly 4200 and the pulley 4100 are coupled, the power of the drive source (not shown) is transmitted to the rotation shaft 3000 through the pulley 4100 and the disk hub assembly 4200. It can be. In addition, the rotating shaft 3000 can compress the refrigerant by operating the compression mechanism 2000 with the received power.

On the other hand, when the application of power to the coil is stopped, the attractive force due to the magnetic induction of the coil is no longer generated, and the disc hub assembly 4200 moves away from the pulley 4100 by the separation means (not shown). It may be moved in one direction to be spaced apart from the pulley 4100. That is, power transmission from the drive source (not shown) to the rotation shaft 3000 may be stopped. Then, the compression mechanism 2000 may stop operating, and refrigerant compression may stop.

In this process, as the slots 4130 and 4160 are formed in the pulley 4100, when power is applied to the coil, the attracted magnetic flux of the field coil assembly 4300 is transmitted to the disk hub assembly 4200. As this increases, the contact force between the pulley 4100 and the disk hub assembly 4200 may increase.

In addition, as the bridges 4140 and 4170 are formed in the pulley 4100, weakening of the rigidity of the pulley 4100 due to 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, which are in inverse proportion to each other, are adjusted to match the performance and fatigue durability required for the clutch 4000. It is determined in advance at the time of design, and the shapes of the slots 4130, 4160 are formed in a predetermined shape within the range of the determined lengths of the slots 4130, 4160 and the lengths of the bridges 4140, 4170, so that the pulley ( The contact force between 4100 and the disk hub assembly 4200 and the rigidity of the pulley 4100 can be further improved.

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

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

The center of curvature (4162c) of the inner slot centripetal side inner surface 4162 is located at the rotation center of the pulley 4100, and the radius of curvature (4162r) of the inner slot centripetal side inner surface is located at the center of rotation of the pulley 4100. It may be formed to be smaller than the radius of curvature (4161r) of the inner surface of the inner slot on the centrifugal side.

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

More specifically, the inner slot end side inner surface 4163 includes an inner slot end side inner surface first curved surface 4164 that is curved from the inner slot distal side inner surface 4161 toward the distal side in the radial direction of the pulley 4100, A second inner curved surface 4165 on the inner slot end side curved from the first inner surface 4164 on the inner slot end side to the centripetal side in the radial direction of the pulley 4100, and a second inner curved surface 4165 on the inner slot end side. It includes a third curved surface 4166 on the inner slot end side, which is curved toward the centripetal side in the radial direction of the pulley 4100 and curved from the inner slot centripetal inner surface 4162 toward the centripetal side in the radial direction of the pulley 4100. can do.

The second inner curved surface 4165 at the end of the inner slot is such that the width of the inner slot 4160 (measured along the radial direction of the pulley 4100) is increased. The center of curvature (4165c) is located inside the inner slot (4160), and the radius of curvature (4165r) of the second curved surface of the inner surface on the end side of the inner slot is the radius of curvature (4161r) of the inner surface on the centrifugal side of the inner slot. It can be formed into a curved surface larger than half of the value minus the radius of curvature (4162r) of the inner surface of the centripetal side.

In addition, the second inner curved surface 4165 at the end of the inner slot extends along the rotation direction of the pulley 4100 from the centripetal side in the radial direction of the pulley 4100 with respect to the inner slot 4160. To prevent the annular wall 4190 for bearing fastening from being eroded by the second inner curved surface 4165 on the inner slot end side, the radius of curvature 4165r of the second inner curved surface on the inner slot end side is the inner surface 4165 on the inner slot end side. 2 It is formed as a curved surface that is less than or equal to the value obtained by subtracting the radius of curvature (4190r) of the outer peripheral surface of the annular wall for fastening the bearing from the distance between the center of curvature (4165c) of the curved surface and the center of curvature (4190c) of the annular wall for fastening the bearing. You can.

Here, the second inner curved surface 4165 at the end of the inner slot may be formed so that the length of the inner bridge 4170 is not reduced by 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 rotation center of the pulley 4100) and the reference curved surface 4169 on the inner surface of the inner slot end side (pulley 4100) At the end side of the inner slot 4160 in the circumferential direction, the inner slot centrifugal side inner surface 4161 and the inner slot centripetal side inner surface 4162 are connected, and the center of curvature 4169c is formed inside the inner slot 4160. , the distance between the first clutch (4000) is a virtual curved surface whose 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 centrifugal side of the inner slot from the radius of curvature (4161r) of the inner surface of the centrifugal side of the inner slot. ) It is determined in advance at the time of design, and the distance between the center line (4170a) of the inner bridge and the second curved surface (4165) of the inner surface at the end of the inner slot is the reference curved surface of the center line (4170a) of the inner bridge and the second curved surface (4165) of the inner surface at the end of the inner slot. (4169), the second inner surface 4165 at the end of the inner slot is the second inner surface at the end of the inner slot as the radius of curvature 4165r of the second curved surface at the end of the inner slot increases. 2 The center of curvature 4165c of the curved surface may be formed to be spaced apart from the inner bridge 4170.

In the inner slot end-side first curved surface 4164, a notch where stress can be concentrated is formed between the inner slot centrifugal side inner surface 4161 and the inner slot end-side second inner curved surface 4165. In order to prevent this from happening, it may be formed as a curved surface that contacts both the inner surface 4161 on the centrifugal side of the inner slot and the second curved surface 4165 on the inner surface 4165 on the end side of the inner slot.

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

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

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

That is, the center of curvature (4166c) of the third inner surface on the inner slot end side 4166 is the center of curvature of the pulley 4100 with respect to the inner slot centripetal side inner surface 4162. It is located on the centripetal side in the radial direction, and the radius of curvature (4166r) of the third inner surface at the end of the inner slot is equal to the center of curvature (4166c) of the third curved surface at the end of the inner slot and the second curved surface at the inner surface at the end of the inner slot. It is equal to the value obtained by subtracting the radius of curvature (4165r) of the second curved surface of the inner surface at the end of the inner slot from the distance between the centers of curvature (4165c), and the radius of curvature (4166r) of the third curved surface of the inner surface at the end of the inner slot is the It is formed as a curved surface equal to the distance between the center of curvature (4166c) of the third curved surface on the inner slot end side and the center of curvature (4162c) on the inner surface on the inner slot centripetal side from the radius of curvature (4162r) on the inner surface on the centripetal side of the slot. It can be.

In addition, the third inner surface 4166 on the inner slot end side is to more effectively distribute the load applied between the inner slot centripetal side inner surface 4162 and the inner second curved surface 4165 on the inner slot end side, The radius of curvature (4166r) of the third curved surface of the inner surface at the end of the inner slot may be formed as a larger curved surface than the radius of curvature (4165r) of the second curved surface of the inner surface at the end of the inner slot.

The inner slot 4160 according to this embodiment having this shape can increase the area of the inner slot 4160 without reducing the length of the inner bridge 4170. Accordingly, the contact force between the pulley 4100 and the disk hub assembly 4200 can be improved without weakening the rigidity of the pulley 4100. In addition, 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 increase in capacity of the field coil assembly 4300, Increases in weight and cost can be prevented.

In addition, the inner slot 4160 according to this embodiment having this shape can prevent damage to the pulley 4100 by preventing damage from occurring in the inner slot 4160.

Specifically, as a result of the analysis, it was found that in the conventional case, damage mainly occurred in the inner slot 4160, and that this was due to the shape of the end of the inner slot 4160.

More specifically, referring to the accompanying 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 located at the center of rotation of the pulley 4100. ), the center of curvature (4162c) is located at the rotation center of the pulley 4100, and the radius of curvature (4162r) is smaller than the radius of curvature (4161r) of the inner surface of the centrifugal side of the inner slot. The small inner slot centripetal side inner surface 4162 and the inner slot centrifugal side inner surface 4161 and the inner slot centripetal inner surface 4162 are connected at the end side of the inner slot 4160 in the circumferential direction of the pulley 4100. It includes an inner slot end side inner surface 4163, but unlike the present embodiment, the inner slot end side inner surface 4163 extends from the inner slot centrifugal side inner surface 4161 to the inner slot centripetal side inner surface 4162 of the pulley. It is formed to be curved toward the centripetal side in the radial direction of (4100).

That is, in the conventional inner slot end side inner surface 4163, the center of curvature 4163c of the inner slot end side inner surface is located inside the inner slot 4160, and the curvature radius 4163r of the inner slot end side inner surface is located inside the inner slot 4160. ) is formed as a curved surface equal to half of the value obtained by subtracting the radius of curvature (4162r) of the inner surface of the centrifugal side of the inner slot from the radius of curvature (4161r) of the inner surface of the centrifugal side of the inner slot.

In the case of the conventional inner slot 4160 having this shape, the pulley (not shown) is driven by the drive belt (not shown) connecting the drive source (not shown) and the pulley 4100, as shown by 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 load applied to the inner slot end side inner surface 4163 causes the inner slot end side to be The inner surface 4163 is bent based on the inner surface 4161 on the centrifugal side of the inner slot. As a result, a crack is generated at the connection point between the inner slot centrifugal side inner surface 4161 and the inner slot end side inner surface 4163, the crack grows, 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 FIGS. 6 and 7, the inner slot end side inner surface 4163 is curved from the inner slot distal side inner surface 4161 toward the distal side in the radial direction of the pulley 4100. It is then formed to be curved toward the centripetal side in the radial direction of the pulley 4100. That is, the inner surface 4163 at the end of the inner slot according to this embodiment includes a first curved surface 4164 on the inner surface at the end of the inner slot and a second curved surface 4165 on the inner surface at the end of the inner slot.

As a result, as shown by the arrow in FIG. 7, the load applied to the second curved surface 4165 on the inner slot end side is distributed in both directions, and the inner slot end side inner surface 4163 is the inner slot centrifugal side inner surface. Bending based on 4161 can be prevented, and cracks can be prevented from occurring at the connection point between the inner slot 4161 on the centrifugal side of the inner slot and the inner surface 4163 on the end side of the inner slot. At this time, the inner first curved surface 4164 on the inner slot end side smoothly flows the load transferred from the first inner curved surface 4164 on the inner slot end side to the inner slot distal side inner surface 4161, thereby It is possible to more effectively prevent cracks from occurring at the connection point between the inner surface 4161 on the centrifugal side of the slot and the inner surface 4163 on the end side of the inner slot. Accordingly, damage to the inner slot 4160 can be prevented and damage to the pulley 4100 can be prevented.

Meanwhile, in the conventional case, the outer slot 4130 is formed in a similar shape to the inner slot 4160, but it is found that damage mainly occurs in the inner slot 4160, and almost no damage occurs in the outer slot 4130. It has been done.

That is, the conventional outer slot 4130 has an outer slot centrifugal inner surface 4131 opposite the rotation center side of the pulley 4100 on the centrifugal side in the radial direction of the pulley 4100, The outer slot centripetal side inner surface 4132 is opposite to the outer slot centrifugal inner surface 4131 on the centripetal side in the radial direction, and the outer slot centrifugal surface is on the end side of the outer slot 4130 in the circumferential direction of the pulley 4100. It includes an outer slot end side inner surface 4133 connecting the side inner surface 4131 and the outer slot centripetal side inner surface 4132, and the outer slot end side inner surface 4133 is separated from the outer slot centrifugal side inner surface 4131. The outer slot centripetal side inner surface 4132 is formed to be curved toward the centripetal side in the radial direction of the pulley 4100, but there is almost no crack between the outer slot centrifugal inner surface 4131 and the outer slot end side inner surface 4133. It was determined that this did not occur.

As a result of the analysis, this phenomenon is that the load applied to the pulley 4100 by the drive belt (not shown) also acts on the inner surface 4131 on the centrifugal side of the outer slot and the inner surface 4133 on the end side of the outer slot. As shown by the arrow in Figure 3, it was found that the load applied to the inner surface 4133 at the end of the outer slot is distributed toward 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 are formed 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, so the load applied to the inner surface 4133 at the end of the outer slot 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 are directly opposed to the annular wall 4190 for fastening bearings, so the load applied to the inner surface 4163 at the end of the inner slot is not distributed through the inner bridge 4170, Almost no cracks occur between the outer slot centrifugal side inner surface 4131 and the outer slot end side inner surface 4133, and cracks occur between the inner slot centrifugal inner surface 4161 and the inner slot end side inner surface 4163. It was found that this occurred.

Considering this, in the case of this 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 this embodiment is the outer slot centrifugal opposite to the rotation center side of the pulley 4100 on the centrifugal side in the radial direction of the pulley 4100. A side inner surface 4131, an outer slot centripetal side inner surface 4132 opposing the outer slot centrifugal side inner surface 4131 on the centripetal side in the radial direction of the pulley 4100, and the outer slot on the centripetal side in the radial direction of the pulley 4100. It includes 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 the 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 slot centrifugal side inner surface 4131 to the outer slot centripetal inner surface 4132.

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

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

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

The outer slot 4130 according to this embodiment having this shape does not cause damage to the outer slot 4130, and the manufacturing cost required to form the outer slot 4130 can be reduced.

Meanwhile, in the case of this embodiment, the inner slot end side inner surface 4163 is curved from the inner slot distal side inner surface 4161 toward the distal side in the radial direction of the pulley 4100, and then back to the distal side of the pulley 4100. It is curved toward the centripetal side in the radial direction, and further curved toward the centrifugal side in the radial direction of the pulley 4100 to extend to the inner surface 4162 on the centripetal side of the inner slot.

However, it is not limited to this, and as shown in FIG. 8, the inner slot end side inner surface 4163 is curved from the inner slot distal side inner surface 4161 toward the distal side in the radial direction of the pulley 4100. , Again, the pulley 4100 may be curved toward the centripetal side in the radial direction and may be formed to extend to the centripetal inner surface of the inner slot 4162.

That is, referring to FIG. 8, in the compressor according to another embodiment of the present invention, the inner slot end side inner surface 4163 is located in the radial direction of the pulley 4100 from the inner slot centrifugal side inner surface 4161. A first inner surface 4164 on the inner slot end side that is curved toward the centrifugal side, and a portion curved toward the centripetal side in the radial direction of the pulley 4100 from the first curved surface 4164 on the inner slot end side, is the inner surface 4164 on the inner slot end side. 2 Curved from the curved surface 4165 and the second curved surface 4165 on the end side of the inner slot toward the centripetal side in the radial direction of the pulley 4100, and in the radial direction of the pulley 4100 from the inner surface 4162 on the centripetal side of the inner slot. It may include a fourth curved surface 4167 on the inner surface at the end of the inner slot that is curved toward the distal side.

The first inner curved surface 4164 at the end of the inner slot and the second curved surface 4165 at the end of the inner slot may be formed as in the above-described embodiments.

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

That is, the fourth inner surface 4167 on the inner slot end side is such that the center of curvature 4167c of the fourth inner surface on the inner slot end side is located inside the inner slot 4160, and the inner surface on the inner slot end side is The radius of curvature (4167r) of the fourth curved surface is from the radius of curvature (4165r) of the second inner surface at the end of the inner slot to the center of curvature (4167c) of the fourth inner surface at the end of the inner slot and the second inner surface at the end of the inner slot. 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 fourth curved surface of the inner surface at the end of the inner slot is the center of curvature (4167c) of the fourth curved surface of the inner surface at the end of the inner slot and the It may be formed as a curved surface equal to the value obtained by subtracting the radius of curvature (4162r) of the inner surface of the inner slot's centripetal side from the distance between the centers of curvature (4162c) of the inner surface of the inner slot's centripetal side.

Here, the inner fourth curved surface 4167 on the inner slot end side more effectively distributes the load applied between the inner slot centripetal side inner surface 4162 and the inner slot end side second inner curved surface 4165, The center of curvature (4167c) of the fourth curved surface on the inner surface at the end side of the inner slot is the center line (4160a) of the inner slot (distance to the inner surface (4161) on the centrifugal side of the inner slot in the rotational radial direction of the pulley (4100) and the centripetal side of the inner slot. is located on an imaginary line connecting points with the same distance to the inner slot 4162, and the radius of curvature 4167r of the fourth curved surface of the inner surface on the end side of the inner slot is the radius of curvature 4161r of the inner surface on the centrifugal side of the inner slot. It may be formed as a curved surface equal to half of the value obtained by subtracting the radius of curvature (4162r) of the inner surface of the centripetal side of the inner slot.

In this case, the effect of preventing cracks 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 at the end of the inner slot.

That is, in this case, when the gap between the inner slot 4160 and the annular wall 4190 for bearing fastening is narrow, the annular wall 4190 for fastening bearings is not eroded by the inner slot 4160. , cracks are prevented between the inner slot centrifugal side inner surface 4161 and the inner slot end side inner surface 4163, and the area of the inner slot 4160 is increased to increase the size of the pulley 4100 and the disk hub assembly 4200. ) may increase the contact force between them.

Meanwhile, in the case of this embodiment, the inner surface 4163 at the end of the inner slot has a symmetric structure that is advantageous in terms of durability, noise, and vibration, and the center of curvature 4165c of the second curved surface on the inner surface at the end of the inner slot ) may be formed on the center line 4160a of the inner slot.

However, it is not limited to this, and the center of curvature 4165c of the second inner curved surface at the end of the inner slot may be formed at any position inside the inner slot 4160.

2000: Compression mechanism
3000: Rotation axis
4100: pulley
4130: Outer slot
4130a: Center line of outer slot
4131: Inner surface of outer slot centrifugal side
4131c: Center of curvature on the inner surface of the centrifugal side of the outer slot
4131r: Radius of curvature on the inner surface of the centrifugal side of the outer slot
4132: Outer slot centripetal side inner surface
4132c: Center of curvature on the inner surface of the centripetal side of the outer slot
4132r: Curvature radius of the inner surface of the centripetal side of the outer slot
4133: Inner surface of outer slot end side
4133c: Center of curvature on the inner surface of the outer slot end side
4133r: Curvature radius of the inner surface of the end of the outer slot
4139: Reference curved surface on the inner surface of the end of the outer slot
4139c: Center of curvature of the reference curved surface on the inner surface of the end of the outer slot
4139r: Curvature radius of the reference curved surface on the inner surface of the end of the outer slot
4140: Outer Bridge
4140a: Center line of the outer bridge
4160: Inner slot
4160a: Center line of inner slot
4161: Inner slot centrifugal side inner surface
4161c: Center of curvature on the inner side of the inner slot on the centrifugal side
4161r: Radius of curvature on the inner surface of the centrifugal side of the inner slot
4162: Inner slot centripetal side inner surface
4162c: Center of curvature of inner slot centripetal side
4162r: Radius of curvature on the inner surface of the centripetal side of the inner slot
4163: Inner slot end side inner surface
4136: Third inner curved surface at the end of the outer slot
4164: First inner curved surface at the end of the inner slot
4164c: Center of curvature of the first curved surface on the inner slot end side
4164r: Curvature radius of the first inner curved surface at the end of the inner slot
4165: Second inner curved surface at the end of the inner slot
4165c: Center of curvature of the second inner curved surface at the end of the inner slot
4165r: Curvature radius of the second inner curved surface at the end of the inner slot
4166: Third inner curved surface at the end of the inner slot
4166c: Center of curvature of the third inner curved surface at the end of the inner slot
4166r: Curvature radius of the third inner surface at the end of the inner slot
4167: Fourth inner curved surface at the end of the inner slot
4167c: Center of curvature of the fourth inner curved surface at the end of the inner slot
4167r: Curvature radius of the fourth inner curved surface at the end of the inner slot
4169: Reference curved surface on the inner surface of the inner slot end side
4169c: Center of curvature of the reference curved surface on the inner surface of the inner slot end side
4169r: Curvature radius of the reference curved surface on the inner surface of the inner slot end side
4170: Inner Bridge
4170a: Center line of inner bridge
4190: Annular wall for bearing fastening
4190c: Center of curvature of the annular wall for bearing fastening
4190r: Curvature radius of the outer peripheral surface of the annular wall for bearing fastening
4200: Disk hub assembly

Claims (14)

A disk hub assembly (4200) coupled to the rotation shaft (3000) of the compression mechanism (2000); and
It includes a pulley (4100) that receives power from a drive source and rotates and is selectively interconnected with the disk hub assembly (4200),
The pulley 4100 includes an inner slot 4160 and an outer slot 4130,
The inner slot 4160 includes an inner slot centrifugal side inner surface 4161 opposite the rotation center side of the pulley 4100 on the centrifugal side in the radial direction of the pulley 4100; an inner slot centripetal side inner surface 4162 opposite the inner slot centrifugal inner surface 4161 on 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 a first inner slot end side inner surface 4164 that is curved from the inner slot distal side inner surface 4161 toward the distal side in the radial direction of the pulley 4100; and a second inner curved surface 4165 on the inner slot end side, which is curved from the first inner surface 4164 on the inner slot end side toward the centripetal side in the radial direction of the pulley 4100. According to paragraph 1,
The center of curvature (4161c) on the inner surface of the centrifugal side of the inner slot is formed at the rotation center of the pulley (4100),
The radius of curvature (4161r) of the inner surface of the centrifugal side of the inner slot is smaller than the radius of the pulley (4100),
The center of curvature (4162c) on the inner surface of the inner slot centripetal side is formed at the rotation center of the pulley (4100),
The radius of curvature (4162r) of the inner surface on the centrifugal side of the inner slot is formed to be smaller than the radius of curvature (4161r) of the inner surface on the centrifugal side of the inner slot,
The center of curvature (4165c) of the second inner surface at the end of the inner slot is formed inside the inner slot (4160),
The radius of curvature (4165r) of the second curved surface of the inner surface at the end of the inner slot is greater than half of the value obtained by subtracting the radius of curvature (4162r) of the inner surface of the inner slot centripetal side from the radius of curvature (4161r) of the inner surface of the centrifugal side of the inner slot. compressor. According to paragraph 2,
An imaginary line connecting points having the same distance to the inner slot centrifugal side inner surface 4161 and the inner slot centripetal inner surface 4162 in the rotation radial direction of the pulley 4100 is defined as the center line of the inner slot 4160a. ), then
The center of curvature (4165c) of the second inner surface at the end of the inner slot is formed on the center line (4160a) of the inner slot. According to paragraph 3,
The center of curvature 4164c of the first curved surface on the inner slot end side is formed on the distal side in the radial direction of the pulley 4100 based on the inner slot centrifugal side inner surface 4161,
The radius of curvature (4164r) of the first inner curved surface at the end of the inner slot is the distance between the center of curvature (4164c) of the first curved surface at the end of the inner slot and the center of curvature (4165c) of the second curved surface at the end of the inner slot. It is formed equal to the value obtained by subtracting the radius of curvature (4165r) of the second curved surface on the inner surface at the end of the inner slot,
The radius of curvature (4164r) of the first curved surface of the inner surface at the end of the inner slot is the distance between the center of curvature (4164c) of the first curved surface of the inner surface at the end of the inner slot and the center of curvature (4161c) of the inner surface at the centrifugal side of the inner slot. A compressor formed equal to the value minus the radius of curvature (4161r) of the inner surface of the centrifugal side. According to paragraph 4,
The pulley 4100 includes an annular wall 4190 for fastening a bearing extending along the rotation direction of the pulley 4100 from the centripetal side in the radial direction of the pulley 4100 with respect to the inner slot 4160. Contains more,
The radius of curvature (4165r) of the second inner curved surface at the end of the inner slot is the distance between the center of curvature (4165c) of the second curved surface at the end of the inner slot and the center of curvature (4190c) of the annular wall for fastening the bearing. A compressor formed to be smaller than or equal to the value minus the radius of curvature (4190r) of the outer peripheral surface of the annular wall. According to paragraph 4,
A compressor in which the radius of curvature (4164r) of the first curved surface of the inner surface at the end of the inner slot is larger than the radius of curvature (4165r) of the second curved surface of the inner surface at the end of the inner slot. According to clause 4,
The inner slot end side inner surface 4163 is curved from the inner slot centripetal side inner surface 4162 toward the centripetal side in the radial direction of the pulley 4100, and is curved from the inner slot end side inner surface 4165 to the pulley ( A compressor further comprising a third inner surface curved surface 4166 on the end side of the inner slot that is curved toward the centrifugal side in the radial direction of 4100). In clause 7,
The center of curvature 4166c of the third curved surface on the inner slot end side is formed on the centripetal side in the radial direction of the pulley 4100 based on the inner slot centripetal side inner surface 4162,
The radius of curvature (4166r) of the third inner surface at the end of the inner slot is the distance between the center of curvature (4166c) of the third curved surface at the end of the inner slot and the center of curvature (4165c) of the second curved surface at the end of the inner slot. It is formed equal to the value obtained by subtracting the radius of curvature (4165r) of the second curved surface on the inner surface at the end of the inner slot,
The radius of curvature (4166r) of the third curved surface of the inner surface at the end side of the inner slot is the center of curvature (4166c) of the third curved surface of the inner surface at the centripetal side of the inner slot at the radius of curvature (4162r) of the inner surface at the centripetal side of the inner slot. A compressor formed by subtracting the distance between the inner centers of curvature (4162c). According to clause 8,
A compressor in which the radius of curvature (4166r) of the third curved surface of the inner surface at the end of the inner slot is larger than the radius of curvature (4165r) of the second curved surface of the inner surface at the end of the inner slot. According to paragraph 4,
The inner slot end side inner surface 4163 is curved from the inner slot centripetal side inner surface 4162 toward the centrifugal side in the radial direction of the pulley 4100, and is curved from the inner slot end side inner surface 4165 to the pulley ( A compressor further comprising a fourth inner surface curved surface 4167 on the end side of the inner slot that is curved toward the centripetal side in the radial direction of 4100). According to clause 10,
The center of curvature (4167c) of the fourth inner surface at the end of the inner slot is formed inside the slot (4160),
The radius of curvature (4167r) of the fourth inner curved surface at the end of the inner slot is the center of curvature (4167c) of the fourth curved surface at the end of the inner slot at the radius of curvature (4165r) of the second curved surface at the end of the inner slot. 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 side,
The radius of curvature (4167r) of the fourth inner curved surface on the end side of the inner slot is the distance between the center of curvature (4167c) of the fourth curved surface on the inner surface on the end side of the inner slot and the center of curvature (4162c) on the inner surface on the centripetal side of the inner slot. A compressor formed equal to the value minus the radius of curvature (4162r) of the inner surface of the centripetal side. According to clause 11,
The center of curvature (4167c) of the fourth inner surface at the end of the inner slot is formed on the center line (4160a) of the inner slot,
The radius of curvature (4167r) of the fourth curved surface on the inner surface at the end of the inner slot is equal to half of the value obtained by subtracting the radius of curvature (4162r) on the inner surface on the centrifugal side of the inner slot from the radius of curvature (4161r) on the inner surface on the centrifugal side of the inner slot. compressor. According to paragraph 1,
The outer slot 4130 is,
an outer slot centripetal side inner surface 4132 in which a center of curvature 4132c is formed at the rotation center of the pulley 4100 and a curvature radius 4132r is formed larger than a curvature radius 4161r of the inner slot centrifugal side inner surface;
An outer slot centrifugal side inner surface 4131 in which a center of curvature 4131c is formed at the rotation center of the pulley 4100 and a curvature radius 4131r is formed larger than a curvature radius 4132r of the outer slot centripetal side inner surface; and
It includes; 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),
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 from the outer slot centrifugal side inner surface 4131 to the outer slot centripetal side inner surface 4132. According to clause 13,
The center of curvature 4133c on the inner surface of the end of the outer slot is formed inside the outer slot 4130,
The radius of curvature (4133r) of the inner surface on the end side of the outer slot is equal to half of the value obtained by subtracting the radius of curvature (4132r) of the inner surface on the centrifugal side of the outer slot from the radius of curvature (4131r) of the inner surface on the centrifugal side of the outer slot. Compressor.

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