WO2020022826A1

WO2020022826A1 - Electric compressor comprising eccentric bush

Info

Publication number: WO2020022826A1
Application number: PCT/KR2019/009311
Authority: WO
Inventors: 안현승; 임권수; 문치명; 박창언
Original assignee: 한온시스템 주식회사
Priority date: 2018-07-26
Filing date: 2019-07-26
Publication date: 2020-01-30

Abstract

The present invention relates to an electric compressor comprising an eccentric bush. By means of forming the curvature between the outer peripheral surface of a driving shaft and the inner peripheral surface of a shaft mounting portion of an eccentric bush to be the same and setting the gap movement direction of the eccentric bush, advantages of preventing noise, wearing and damage due to the collision of the driving shaft and the eccentric bush when the operation of an electric compressor stops can be expected.

Description

Electric compressor with eccentric bush

The present invention relates to an electric compressor including an eccentric bush, and more particularly, by forming the same curvature between the outer circumferential surface of the drive shaft and the inner circumferential surface of the shaft seating portion of the eccentric bush, by setting the play movement direction of the eccentric bush, The present invention relates to an electric compressor including an eccentric bush which prevents collision noise, wear and damage of the driving shaft and the eccentric part time when the operation stops.

In general, a vehicle is provided with an air conditioning (A / C) for indoor air conditioning. Such an air conditioner includes a compressor as a configuration of a cooling system that compresses a low temperature low pressure gaseous refrigerant drawn from an evaporator into a high temperature high pressure gaseous refrigerant and sends it to a condenser.

The compressor has a reciprocating type to compress the refrigerant in accordance with the reciprocating motion of the piston and a rotary type to perform the compression while rotating. The reciprocating type includes a crank type for transferring to a plurality of pistons using a crank, a swash plate type for transferring to a rotary shaft with a swash plate, and a rotary type vane rotary type using a rotary shaft and vanes. There are scrolling types that use orbital scrolling and fixed scrolling.

Scroll compressors are widely used for refrigerant compression in air conditioners and the like because they have a relatively high compression ratio compared to other types of compressors, and the suction, compression, and discharge strokes of the refrigerant smoothly lead to stable torque.

The scroll compressor may be implemented electrically, in which case it may belong to the category of motorized compressors.

In the case of the scroll compressor, the refrigerant is compressed through the interaction between the swing scroll and the fixed scroll. At this time, the turning scroll is connected to the eccentric bush disposed at the end of the driving shaft connected to the motor, and forms a compression region with the fixed scroll with the rotational force transmitted by the eccentric bush according to the rotation of the driving shaft.

1A and 1B, the conventional eccentric bush 1 has a pinhole 3 formed on the protrusion 2a of the body 2, and is connected to the connecting pin 7 inserted into the pinhole 3. It is connected to the drive shaft 5 by the.

The drive shaft 5 is inserted into the shaft seating portion 4 formed on one surface of the body portion 2. And the protrusion part 2a of the body part 2 is inserted in the bearing unit 8a, and is connected with the revolving scroll 8.

Here, the outer circumferential curvature of the drive shaft 5 and the inner circumferential curvature of the shaft seating portion 4 are formed differently. In particular, the vertical (vertical) curvature of the inner peripheral surface of the shaft seat portion 4 and the horizontal (lateral) curvature are different from each other.

In addition, the inner circumferential surface of the shaft seating portion 4 is larger than the outer circumferential surface of the driving shaft 5, and there is a gap between the outer circumferential surface of the driving shaft 5 and the inner circumferential surface of the body portion 20 as shown in FIGS. 2A and 2B. (G) is formed.

The clearance G is formed at different intervals between the V1 direction and the V2 direction due to the difference in curvature and size of the inner circumferential surface of the shaft seating portion 4 and the outer circumferential surface of the drive shaft 5. However, V1 and V2 are assumed directions for convenience of description and may be different directions depending on the design.

The clearance G is set by the manufacturer's intention, and the reason for providing the clearance G is to prevent damage to the scroll when liquid refrigerant is generated.

By the way, when the electric compressor is stopped, the drive shaft 5 immediately stops, but the eccentric bush 1 stops after rotating a little more due to inertia.

2A shows the clearances G1 and G2 between the drive shaft 5 and the shaft seating portion 4 during operation of the electric compressor.

In FIG. 2B, when the electric compressor stops, the shaft seating portion 4 of the eccentric bush 1 rotates a little more due to inertia, and is stopped at the inner circumferential surface of the shaft seating portion 4 formed at different curvatures at different portions. A collision occurs between the outer circumferential surfaces of the drive shaft 5 that are present. This will cause hitting noise and wear and damage of the contact surface.

In other words, due to the difference between the inner circumferential surface curvature of the shaft seating portion 4 and the outer circumferential surface curvature of the drive shaft 5, for example, in the state where the sizes of the clearances G1 and G2 are differently formed in the V1 and V2 directions, Contact with the drive shaft 5 occurs in the vicinity of the clearance G2 where the spacing is relatively small in the inner peripheral surface of the shaft seating portion 4 of the eccentric bush 1, which is rotated a little further. Will cause.

The present invention has been made to solve the problems in the related art as described above, an object of the present invention is to form the same curvature between the outer peripheral surface of the drive shaft and the inner peripheral surface of the shaft seating portion of the eccentric bush, the play movement direction of the eccentric bush The present invention provides a motor-driven compressor including an eccentric bush for preventing collision noise, wear and damage of the drive shaft and eccentric off-time when the motor-driven compressor is stopped.

The present invention for achieving the above object relates to an electric compressor comprising an eccentric bush, casing; A motor disposed inside the casing and generating a driving force; A drive shaft rotated by the motor; A compression mechanism for compressing a refrigerant by driving between a swing scroll associated with the drive shaft and a fixed scroll engaged with the swing scroll; And an eccentric bush formed at one side of the shaft seating portion connected to the driving shaft, and at the other side of the eccentric bush formed at the scroll coupling portion connected to the swinging scroll. The eccentric bush may have a play in one direction.

In addition, in the embodiment of the present invention, the clearance formation direction of the eccentric bush is the first direction (V1), the eccentric bush may be configured to move in the first direction (V1) when the operation of the drive shaft is stopped.

In another embodiment of the present invention, the pinhole is disposed in the eccentric bush; And a connecting pin inserted into the pin hole and connecting the driving shaft and the eccentric bush, wherein the first pin D1 and the second direction V2 correspond to a first direction V1 in the pin hole. The second intervals D2 corresponding to the second gaps D2 may have different lengths.

In addition, in the embodiment of the present invention, the first interval D1 may be longer than the second interval D2.

In addition, in the embodiment of the present invention, the connecting pin may be formed in a circular cross section, and the outer circumferential surface of the connecting pin may be the same as the round shape formed at both sides of the pinhole with respect to the first direction V1.

In addition, in the embodiment of the present invention, the connecting pin is formed in a rectangular cross section, the length (H2) corresponding to the second direction (V2) of the connecting pin is the same as the second interval (D2), The length H1 corresponding to the first direction V1 may be smaller than the first interval D1.

In addition, in the embodiment of the present invention, the shape of both sides of the pinhole may be different from each other based on the first direction V1.

In addition, in the embodiment of the present invention, the clearance formation direction of the eccentric bush is formed in the third direction V3 between the first direction V1 and the second direction V2, and the eccentric bush when the driving shaft is stopped. May be freely moved in the third direction V3.

In another embodiment of the present invention, the pinhole is disposed in the eccentric bush; And a connection pin inserted into the pin hole and connecting the driving shaft and the eccentric bush, wherein the third gap D3 and the fourth direction V4 corresponding to the third direction V3 in the pin hole are further included. The fourth intervals D4 corresponding to the second intervals D4 may have different lengths.

In addition, in the embodiment of the present invention, the third interval D3 may be longer than the fourth interval D4.

In addition, in the embodiment of the present invention, the connecting pin may have a circular cross section, and the outer circumferential surface of the connecting pin may be the same as the round shape formed at both sides of the pinhole with respect to the third direction V3.

In addition, in the embodiment of the present invention, the connecting pin is formed in a rectangular cross section, the length (H4) corresponding to the fourth direction (V4) of the connecting pin is the same as the fourth interval (D4), The length H3 corresponding to the third direction V3 may be smaller than the third interval D3.

In addition, in the embodiment of the present invention, the shapes of both sides of the pinhole may be different from each other based on the third direction V3.

In addition, in the embodiment of the present invention, the shaft seating portion may have a shape corresponding to the outside of the driving shaft.

In addition, in the embodiment of the present invention, the outer circumferential surface curvature of the drive shaft and the inner circumferential surface curvature of the shaft seating portion may be the same.

According to the present invention, by forming the same curvature between the outer circumferential surface of the drive shaft and the inner circumferential surface of the shaft seating portion of the eccentric bush and by setting the play movement direction of the eccentric bush, There is an effect of preventing noise, abrasion and damage caused by.

1A shows a conventional eccentric bush.

Figure 1b is a side cross-sectional view showing a coupling structure of the eccentric bush in the conventional electric compressor.

Figure 2a is a view showing the play state of the drive shaft and the eccentric minor time during operation of the conventional electric compressor.

Figure 2b is a view showing the impact state of the drive shaft and the eccentric minor time when the operation of the conventional electric compressor stopped.

3 is a side sectional view showing a structure of an electric compressor (scroll compressor).

Figure 4 shows a first embodiment of an eccentric bush of the electric compressor of the present invention.

Figure 5a is a view showing the play state of the drive shaft and the eccentric part time during the operation of the electric compressor in the first embodiment of the present invention as shown in FIG.

Figure 5b is a view showing a state of movement along the play direction of the drive shaft and the eccentric secondary time when the operation of the electric compressor in the first embodiment of the present invention posted in FIG.

Fig. 6 shows a second embodiment of the eccentric bush of the electric compressor of the present invention.

Figure 7 shows a third embodiment of the eccentric bush of the electric compressor of the present invention.

8 shows a fourth embodiment of the eccentric bush of the electric compressor of the present invention;

Fig. 9 shows a fifth embodiment of the eccentric bush of the electric compressor of the present invention.

10 shows a sixth embodiment of an eccentric bush of the electric compressor of the present invention;

Hereinafter, exemplary embodiments of the eccentric bush of the electric compressor according to the present invention will be described in detail with reference to the accompanying drawings.

First, referring to FIG. 3, the structure of an electric compressor or a scroll compressor to which the present invention is applied will be described.

Referring to FIG. 3, a motor-driven compressor or a scroll compressor to which the present invention is applied includes a casing 10, a motor 20 generating a driving force inside the casing 10, and a drive rotated by the motor 20. The shaft 30 may include a compression mechanism 40 driven by the driving shaft 30 to compress the refrigerant.

The casing 10 includes a first housing 11 for accommodating the motor 20, a second housing 12 for accommodating an inverter 50 for controlling the motor 20, and the compression mechanism 40. It may include a third housing 13 for receiving the.

The first housing 11 includes an annular wall 11a, a first partition 11b for covering one end of the annular wall 11a, and a second partition 11c for covering the other end of the annular wall 11a. ), And the annular wall 11a, the first partition 11b, and the second partition 11c may form a motor accommodating space in which the motor 20 is accommodated.

The second housing 12 may be coupled to the first partition 11b to form an inverter accommodation space in which the inverter 50 is accommodated.

The third housing 13 may be coupled to the second partition wall 11c to form a compression space in which the compression mechanism 40 is accommodated.

Here, the second partition 11c partitions the motor accommodating space and the compression space, and serves as a main frame for supporting the compression mechanism 40, and the motor on the center side of the second partition 11c. A bearing hole 14a through which the drive shaft 30 for interlocking the 20 and the compression mechanism 40 may be formed.

Meanwhile, the fixed scroll 41 of the compression mechanism 40 may be fastened to the second partition 11c, and the third housing 13 may be fastened to the fixed scroll 41. However, the present invention is not limited thereto, and the third housing 13 may receive the compression mechanism 40 and may be fastened to the second partition 11c.

The motor 20 may include a stator 21 fixed to the first housing 11 and a rotor 22 rotated in interaction with the stator 21 inside the stator 21. .

The drive shaft 30 penetrates through the center of the rotor 22, and one end of the drive shaft 30 protrudes toward the first partition 11b based on the rotor 22, and the drive thereof. The other end of the shaft 30 may protrude toward the second partition 11c with respect to the rotor 22.

One end portion 30a of the driving shaft 30 may be rotatably supported by a first bearing 71 provided at the center side of the first partition wall 11b.

Here, a first support groove 11d into which one end of the first bearing 71 and the driving shaft 30 is inserted is formed at the center side of the first partition wall 11b, and the first bearing 71 is It may be interposed between the first support groove (11d) and one end of the drive shaft (30).

The other end 30b of the driving shaft 30 may be connected to the compression mechanism 40 through the bearing hole 14a of the second partition 11c.

In addition, the other end portion 30b of the rotation shaft 30 is connected to the eccentric bush 100 by a connecting pin 90. The eccentric bush 100 may be rotatably supported by a third bearing 73 provided in the compression mechanism 40. In addition, the rotational force is transmitted to the revolving scroll 42 in association with the third bearing 73. The eccentric bush 100 of the present invention will be described later.

Here, a second support groove 14b in which the second bearing 72 is disposed is formed in the water storage hole 14a of the second partition wall 11c, and the second bearing 72 is the second support groove. It may be interposed between the 14b and the rotating shaft 30.

In addition, a boss portion 42a into which the third bearing 73 and the eccentric bush 100 are inserted is formed in the turning scroll 42 of the compression mechanism 40, and the third bearing 73 is It may be interposed between the boss portion 42a and the eccentric bush 100.

The compression mechanism 40 is fixed scroll 41 and the second partition 11c fixedly coupled to the second partition 11c on the opposite side of the motor 20 based on the second partition 11c. And a rotating scroll 42 provided between the fixed scroll 41 and the fixed scroll 41 to form a pair of compression chambers and pivoting by the driving shaft 30. have.

The fixed scroll 41 may include a disc-shaped fixed hard plate portion 41a and a fixed wrap 41c protruding from the compression surface 41b of the fixed hard plate portion 41a to be engaged with the pivoting scroll 42. Can be.

A discharge port 41d may be formed at the center side of the fixed light plate portion 41a to penetrate the fixed light plate portion 41a and discharge the refrigerant compressed in the compression chamber. Here, the discharge port 41d may be in communication with a discharge space formed between the fixed scroll 41 and the third housing 13.

In the scroll compressor according to this configuration, when power is applied to the motor 20, the driving shaft 30 may transmit rotational force to the pivoting scroll 42 while rotating with the rotor 22. Then, the pivoting scroll 42 is pivoted by the drive shaft 30, so that the compression chamber is continuously moved toward the center side, thereby reducing the volume. Then, the coolant may be introduced into the motor accommodating space through a coolant inlet (not shown) formed in the annular wall 11a of the first housing 11. The refrigerant in the motor accommodating space may be sucked into the compression chamber through a refrigerant passage hole (not shown) formed in the second partition 11c of the first housing 11. Then, the refrigerant sucked into the compression chamber may be compressed while being moved to the center side along the movement path of the compression chamber and discharged to the discharge space through the discharge port 41d. A series of processes in which the refrigerant discharged into the discharge space is discharged to the outside of the scroll compressor through the refrigerant discharge port formed in the third housing 13 is repeated.

In this process, the drive shaft 30 is rotatably supported by the first bearing 71 and the second bearing 72, and the pivoting scroll 42 is driven by the third bearing 73. The third bearing 73 is rotatably supported relative to the drive shaft 30, which reduces the weight and size of the assembly of the third bearing 73 and the swinging scroll 42 (hereinafter, the swinging body). To this end, the first bearing 71 and the second bearing 72 may be formed of a different bearing 73.

Specifically, the first bearing 71 and the second bearing 72 fixed to the casing 10 may be formed as ball bearings to minimize friction loss.

On the other hand, the third bearing 73 which is proportional to the weight and size of the swinging body as it is pivoted together with the swinging scroll 42 has a smaller weight and size than the ball bearings and a lower cost needle roller bearing. It may be formed as a roller bearing or a slide bush bearing. In addition, the third bearing 73 may be press-fitted to the boss 423 by a predetermined pressing input.

Hereinafter, the eccentric bush of the electric compressor of the present invention will be described with reference to FIGS. 4 to 10.

Figure 4 is a view showing a first embodiment of the eccentric bush of the electric compressor of the present invention, Figure 5a is a view showing the play state of the drive shaft and the eccentric minor time during operation of the electric compressor of the present invention, Figure 5b is the present invention A diagram showing a state of movement along the play direction of the drive shaft and the eccentric sub time when the compressor is stopped.

The V1 direction described below may be referred to as a direction indicating a first length D1 having a relatively long length in the pinhole 120, or may be referred to as a vertical direction or a vertical direction. The V1 direction may be a direction in which the eccentric bush 100 of the present invention is freely moved. Therefore, the -V1 direction may also be included in the V1 direction.

The V2 direction may be referred to as a direction indicating a second gap D2 having a relatively small length in the pinhole 120, or may be referred to as a horizontal direction. The -V2 direction may also be included in the V2 direction. However, since it may be selected in other directions according to the design and mounting state of the electric compressor, it is not necessarily limited to the above-described direction.

First, referring to FIG. 4, in the first embodiment of the eccentric bush 100 of the present invention, the electric compressor may include a body 103 and a pinhole 120.

The shaft seating unit 110 may have a container shape having a circular cross section as the driving shaft 30 is configured in a cylindrical shape. The scroll coupling portion 105 may have a protrusion shape having a circular cross section as shown in FIG. 4, and may be a portion connected to the turning scroll 42 as shown in FIG. 3.

In the present invention, the inner circumferential surface curvature of the shaft seating portion 110 may be the same as the outer circumferential surface curvature of the driving shaft 30, and the size of the inner circumferential surface of the shaft seating portion 110 is larger than the outer circumferential surface size of the drive shaft 30. It can be configured large.

Accordingly, as shown in FIG. 5A, a relatively uniform gap may be formed between the inner circumferential surface of the shaft seating unit 110 and the outer circumferential surface of the driving shaft 30.

In the related art, as illustrated in FIG. 2A, the curvature of the shaft seating portion 4 is formed differently between the V1 and V2 directions, and thus the clearance formed with the driving shaft 5 is formed in the first direction G1 and the second direction. Different gaps were formed between (G2).

According to the present invention, since the curvature between the shaft seating unit 110 and the driving shaft 30 is the same and differs only in size, the clearance between the V1 and V2 directions may be relatively uniform.

Here, the pinhole 120 is disposed on the scroll coupling portion 105 of the eccentric bush 100, the connecting pin for connecting the drive shaft 30 and the body portion 103 of the eccentric bush 100 ( 90) may be the site of insertion.

In the embodiment of the present invention, the pinhole 120 may have a first length D1 corresponding to the first direction V1 and a second gap D2 corresponding to the second direction V2 to have different lengths. Can be. Here, the diameter (C) of the second spacing (D2) and the connecting pin 90 may be matched.

This is because the eccentric bush 100 in which the pinhole 120 is formed is in the first direction V1 in which the pinhole 120 is inserted into the pinhole 120. This is to move only in the direction of 1 interval D1.

In other words, unlike the conventional eccentric bush (1), the eccentric bush 100 of the present invention is to prevent the movement of the play in the second direction (V2) when the operation of the electric compressor is stopped, and to the centrifugal force generated when a little more rotation It is configured to move the play only in the first direction (V1) by force. By such a structure, a collision between the inner surface of the shaft seating portion 110 of the eccentric bush 100 and the outer surface of the drive shaft 30 can be prevented.

In the first embodiment of the present invention, the connecting pin 90 is formed in a circular (diameter C) cross section, and the outer surface shape of the connecting pin 90 is rounded at both sides 121. 123 of the pinhole 120. It may be the same as the shape.

That is, when the connecting pin 90 moves from one end of the pinhole 120 to the other by the play of the play, the inner surface shape of the both

sides

121 and 123 of the pinhole 120 and the connecting pin 90 Since the outer surface shape of the same), the inner surface of the pinhole 120 and the outer surface of the connecting pin 90 is completely in contact with.

Next, referring to Figure 5a, the drive shaft 30 and the eccentric bush 100 is connected by the connecting pin 90 during the operation of the electric compressor, it is possible to transmit a stable torque without a collision.

By the way, when the operation of the electric compressor is stopped, the drive shaft 30 immediately stops, but the eccentric bush 100 rotates a little more by inertia.

At this time, referring to Figure 5b, the centrifugal force generated by the rotation in the eccentric bush 100 is generated, the present invention is set the play movement direction in the first direction (V1), that is, the first spacing (D1) direction, Figure 5b As shown in the eccentric bush 100 formed with the pinhole 120 is moved only in the first direction (V1) in a state in which the connecting pin 90 is inserted inside.

In FIG. 5B, the positions of the connecting pin 90 and the driving shaft 30 are fixed, and the positions of the pinhole 120 and the eccentric bush 100 are moved up and down, that is, in the first direction V1. do.

That is, the rotational force due to the inertia generated in the eccentric bush 100 when the operation is stopped acts as a centrifugal force, so that the eccentric bush 100 is moved only in the first direction V1 which is the set play movement direction by the centrifugal force.

The present invention forcibly sets the play movement direction in only one specific direction, that is, in the first direction V1, thereby suppressing the eccentric bush 100 from performing additional rotational motion by inertia when the operation is stopped, and thereby It was converted to a linear movement. In this way, the centrifugal force in the rotational direction is converted into a linear movement force in one specified direction, that is, the first direction V1, thereby preventing collision between the eccentric bush 100 and the drive shaft 30.

This is due to the collision caused by the rotation of the stationary drive shaft 30 and the eccentric bush 100 a little more at a time difference due to inertia, which was a problem of the conventional structure when the electric compressor disclosed in FIGS. 2A and 2B is stopped. Noise and contact surface wear and damage caused by the problem will be solved.

Next, referring to FIG. 6, in the second embodiment of the present invention, the connecting pin 90 is formed in a rectangular cross section and has a length H2 corresponding to the second direction V2 of the connecting pin 90. Is the same as the second interval D2, and the length H1 corresponding to the first direction V1 of the connection pin 90 may be smaller than the first interval D1.

In addition, as the clearance movement space is formed in the first direction V1, the eccentric bush 100 having the pinhole 120 having a rectangular cross-sectional shape has a first direction V1 in a state where the connecting pin 90 is inserted. Only), the collision between the drive shaft 30 and the inner surface of the shaft mounting portion 110 of the eccentric bush 100 does not occur.

That is, even if the connecting pin 90 has a square cross-sectional shape, the rotational force generated by the inertia generated in the eccentric bush 100 when the operation is stopped acts as a centrifugal force, so that the eccentric bush 100 is set by the centrifugal force in the first play direction. It can only be moved in the direction V1. The centrifugal force in the rotational direction is also converted to a moving force in a specific one direction to prevent the impact between the eccentric bush 100 and the drive shaft 30.

In addition, when the connecting pin 90 and the pinhole 120 have a rectangular cross-sectional shape, even when the eccentric bush 100 is stopped by the rotational inertia when the driving shaft 30 stops, the connecting pin 90 and the pinhole ( Slip is relatively reduced between the outer surface of the connecting pin 90 and the inner surface of the pinhole 120 compared to the circular cross-sectional shape of 120, so that the amount of additional rotation can be further reduced.

Next, referring to FIG. 7, in the third embodiment of the present invention, the connecting pin 90 is formed in a circular cross section, and the curvature of the connecting pin 90 is one side 121 of the pinhole 120. It may be configured to be the same as the curvature of the round shape formed in.

In this case, the shape of one side 121 of the pinhole 120 and the other side 123 of the pinhole 120 may be different. For example, one side 121 may have a semicircular shape, and the other side 123 may have a rectangular shape. Although not shown in the drawings, in this case, one end of the connecting pin 90 may be semi-circular, and the other end may be rectangular. When the shape of the connecting pin 90 differs depending on the end of the pinhole 120, when the driving shaft 30 stops, the inertia rotation of the eccentric bush 100 may be further suppressed. In addition to connecting the eccentric bush 100 and the drive shaft 30 by the connection pin 90 is eccentric, the connection pin 90 itself is not a simple circular shape, so that the connection pin 90 In comparison, the sliding between the outer surface of the connection pin 90 and the inner surface of the pinhole 120 is relatively reduced, thereby helping to suppress the rotational force by the shape itself when the rotation is stopped.

In addition, the pinhole 120 may be configured such that the first gap D1 formed in the first direction V1 is larger than the second gap D2 formed in the second direction V2. This is to form the play movement space of the drive shaft 30 in the first direction V1.

In the third embodiment of the present invention, the clearance movement space is formed in the first direction V1, and the one side 121 of the pinhole 120 has a semicircular shape, and the other side 123 has a eccentric bush 100. ) Is moved only in the first direction (V1) in the state that the connecting pin 90 is inserted, the collision between the drive shaft 30 and the inner surface of the shaft mounting portion 110 of the eccentric bush 100 is shown in FIG. As shown in 5a and 5b, it does not occur.

That is, the rotational force generated by the inertia generated in the eccentric bush 100 when the operation is stopped may act as the centrifugal force, and the eccentric bush 100 may be moved only in the first direction V1 which is the set play movement direction by the centrifugal force. The centrifugal force in the rotational direction is also converted to a moving force in a specific one direction to prevent the impact between the eccentric bush 100 and the drive shaft 30.

The cross-sectional shape of the connection pin 90 may be other shapes in addition to the shape shown in the embodiment of the present invention, and correspondingly, the internal shape of the pinhole 120 may be changed.

Next, referring to FIG. 8, a fourth embodiment of the present invention is shown.

Prior to the description, in the fourth embodiment of the present invention, the third direction V3 may be an inclined direction between the first direction V1 and the second direction V2, which is the first and second directions V1 and V2. It can include any angle between). In the present invention, since the first and second directions may include all of the V1, -V1, V2, and -V2 directions, the third direction includes the inclination directions formed by V1 and -V2, -V1 and -V2, V1 and -V2. Can be. That is, since the inclination direction disclosed in FIG. 8 is only one example, the inclination direction is not limited thereto and may also include the inclination direction on another slope.

The fourth direction V4 may be an inclination direction between the first direction -V1 and the second direction V2 within a range substantially perpendicular to the third direction V3, which is the first and second directions. It can include any angle between (-V1, V2). Of course, since the first and second directions include all of the V1, -V1, V2, and -V2 directions, the fourth direction may be an inclination direction formed by V1 and -V2, -V1 and -V2, V1 and -V2. Since the inclination direction disclosed in FIG. 8 is only an example, the inclination direction is not limited thereto and may also include the inclination direction on another slope. The same applies to FIGS. 9 and 10 below.

In the fourth embodiment of the present invention, in the embodiment of the present invention, the pinhole 120 has a third gap D3 corresponding to the third direction V3 and a fourth gap D4 corresponding to the fourth direction V4. ) May be formed in different lengths. Herein, the fourth gap D4 and the diameter C of the connection pin 90 may coincide with each other.

This means that the eccentric bush 100 in which the pinhole 120 is formed is the third direction V3 in one direction, that is, the relatively long length of the pinhole 120 is inserted into the pinhole 120. This is to move only in the direction of 3 intervals D3.

That is, unlike the conventional eccentric bush (1), the eccentric bush (100) of the present invention by the play movement occurs in the third direction (V3) when the operation of the electric compressor is stopped, the first and second directions (V1, V2) Avoid excessive play of clearance in either direction. That is, the movement of the play occurs in the inclined direction between the first and second directions V1 and V2 by the centrifugal force generated when the rotation is a little further. By such a structure, a collision between the inner surface of the shaft seating portion 110 of the eccentric bush 100 and the outer surface of the drive shaft 30 can be prevented.

In the fourth embodiment of the present invention, the connecting pin 90 is formed in a circular (diameter C) cross section, and the outer surface shape of the connecting pin 90 is rounded at both side portions 121. 123 of the pinhole 120. It may be the same as the shape.

sides

Next, referring to FIG. 9, in the fifth embodiment of the present invention, the connecting pin 90 has a square cross section and has a length H4 corresponding to the fourth direction V4 of the connecting pin 90. Is the same as the fourth interval D4, and the length H3 corresponding to the third direction V3 of the connection pin 90 may be smaller than the third interval D3.

In addition, as the clearance movement space is formed in the third direction V3, the eccentric bush 100 having the pinhole 120 having a rectangular cross-sectional shape has a third direction V3 in a state where the connecting pin 90 is inserted. The inner surface of the shaft mounting portion 110 of the drive shaft 30 and the eccentric bush 100 by preventing movement of the play in only one of the first and second directions V1 and V2. No collision with the card will occur.

That is, even when the connecting pin 90 has a square cross-sectional shape, the rotational force generated by the inertia generated in the eccentric bush 100 when the operation stops is acted as a centrifugal force, and the third movement is the direction in which the eccentric bush 100 is set by the centrifugal force. It can only be moved in the direction V3. The centrifugal force in the rotational direction is also converted to a moving force in a specific one direction to prevent the impact between the eccentric bush 100 and the drive shaft 30.

In addition, when the connecting pin 90 and the pinhole 120 have a rectangular cross-sectional shape, even if the eccentric bush 100 is further rotated due to rotational inertia when the driving shaft 30 stops, the connecting pin 90 and the pinhole ( Slip is relatively reduced between the outer surface of the connecting pin 90 and the inner surface of the pinhole 120 compared to the circular cross-sectional shape of 120, so that the amount of additional rotation can be further reduced.

Next, referring to FIG. 10, in the sixth embodiment of the present invention, the connecting pin 90 is formed in a circular cross section, and the curvature of the connecting pin 90 is one side 121 of the pinhole 120. It may be configured to be the same as the curvature of the round shape formed in.

In addition, the pinhole 120 may have a third gap D3 formed in the third direction V3 to be larger than a fourth gap D4 formed in the fourth direction V4. This is to form the play movement space of the drive shaft 30 in the third direction V3.

In the sixth embodiment of the present invention, the clearance movement space is formed in the third direction (V3), one side 121 of the pinhole 120 is a semi-circular shape, the other side 123 is an eccentric bush 100 formed in a square shape ) Moves only in the third direction (V3) in the state that the connecting pin 90 is inserted, the collision between the drive shaft 30 and the inner surface of the shaft mounting portion 110 of the eccentric bush 100 occurs You will not. Also, the collision is suppressed by preventing excessive play movement in only a specific direction among the first and second directions V1 and V2.

That is, the rotational force generated by the inertia generated in the eccentric bush 100 when the operation is stopped may act as a centrifugal force, so that the eccentric bush 100 may be moved only in the third direction V3 which is the set play movement direction by the centrifugal force. The centrifugal force in the rotational direction is also converted to a moving force in a specific one direction to prevent the impact between the eccentric bush 100 and the drive shaft 30.

The foregoing merely shows a specific embodiment of the eccentric bush of the electric compressor.

Therefore, it will be apparent to those skilled in the art that the present invention may be substituted and modified in various forms without departing from the spirit of the present invention as set forth in the claims below. do.

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a motor-driven compressor comprising an eccentric bush and has industrial applicability.

Claims

Casing;

A motor disposed inside the casing and generating a driving force;

A drive shaft rotated by the motor;

A compression mechanism for compressing a refrigerant by driving between a swing scroll associated with the drive shaft and a fixed scroll engaged with the swing scroll; And

Includes an eccentric bush formed in one side portion is a shaft seating portion connected to the drive shaft, the other side is formed with a scroll coupling portion connected to the swing scroll,

The eccentric bush is an electric compressor, characterized in that the play is formed in one direction
The method of claim 1,

The eccentric bush forming direction of the eccentric bush is a first direction (V1), the eccentric bush is moved in the first direction (V1) when the operation of the drive shaft is stopped.
The method of claim 2,

A pinhole disposed in the eccentric bush; And

A connection pin inserted into the pin hole and connecting the driving shaft and the eccentric bush;

The eccentric bush, characterized in that the first interval (D1) corresponding to the first direction (V1) and the second interval (D2) corresponding to the second direction (V2) in the pinhole are formed with different lengths.
The method of claim 3,

The first interval (D1) is eccentric bush, characterized in that formed longer than the second interval (D2).
The method of claim 4,

The connecting pin is formed in a circular cross-section, the outer peripheral surface of the connecting pin is an eccentric bush, characterized in that the same as the round shape formed on both sides of the pin hole with respect to the first direction (V1).
The method of claim 4,

The connecting pin has a rectangular cross section, and a length H2 corresponding to the second direction V2 of the connecting pin is the same as the second gap D2, and is connected to the first direction V1 of the connecting pin. Equivalent length (H1) is eccentric bush, characterized in that less than the first interval (D1).
The method of claim 4,

The eccentric bush, characterized in that the shape of both sides of the pinhole relative to the first direction (V1).
The method of claim 1,

The clearance formation direction of the eccentric bush is formed in the third direction V3 between the first direction V1 and the second direction V2, and the eccentric bush is the third direction V3 when the driving shaft is stopped. Electric compressor characterized in that it is moved to play.
The method of claim 8,

A pinhole disposed in the eccentric bush; And

A connection pin inserted into the pin hole and connecting the driving shaft and the eccentric bush;

The eccentric bush, wherein the third gap D3 corresponding to the third direction V3 and the fourth gap D4 corresponding to the fourth direction V4 are formed in different lengths in the pinhole.
The method of claim 9,

The third spacing D3 is longer than the fourth spacing D4.
The method of claim 10,

The connecting pin is formed in a circular cross section, the outer circumferential surface of the connecting pin is an eccentric bush, characterized in that the same as the round shape formed on both sides of the pin hole with respect to the third direction (V3).
The method of claim 10,

The connecting pin is formed in a rectangular cross section, the length (H4) corresponding to the fourth direction (V4) of the connecting pin is the same as the fourth interval (D4), and in the third direction (V3) of the connecting pin Equivalent length (H3) is eccentric bush, characterized in that less than the third interval (D3).
The method of claim 10,

The eccentric bush, characterized in that the shape of both sides of the pinhole with respect to the third direction (V3).
The method of claim 1,

The shaft seating portion is an eccentric bush, characterized in that the shape corresponding to the outside of the drive shaft.
The method of claim 14,

And an outer circumferential surface curvature of the drive shaft and an inner circumferential surface curvature of the shaft seating portion.