KR102538615B1 - Rotor assembly structure of electric compressor - Google Patents

Abstract

The present invention relates to a rotor assembly structure of an electric compressor. More specifically, the present invention relates to a rotor assembly structure of an electric compressor, which is able to reduce the number of rotor assembly parts of the electric compressor, simplify an assembly process, and increase product productivity. According to the present invention, the rotor assembly structure of an electric compressor comprises: a rotor iron core having a hollow hole formed inside; a driveshaft pressed into the hollow hole of the rotor iron core; and a balance weight having the outer diameter surface corresponding to the outer diameter of the rotor iron core, and the inner diameter surface corresponding to the outer diameter of the driveshaft, and engaged with an end unit of the rotor iron core. A chamfering groove is formed on the outer diameter surface of the driveshaft. An engagement surface is formed on the inner diameter surface of the balance weight, having a shape corresponding to the chamfering groove. With the driveshaft pressed into the hollow hole of the rotor iron core, the chamfering groove and the engagement surface are engaged with each other, and prevent the idling between the rotor iron core and the driveshaft.

Description

Rotor assembly structure of electric compressor {Rotor assembly structure of electric compressor}

The present invention relates to a rotor structure of an electric compressor, and more particularly, to a rotor assembly structure of an electric compressor capable of increasing product productivity by reducing the number of rotor assembly parts of the electric compressor and simplifying the assembly process.

An air conditioner is installed inside the vehicle to maintain the proper temperature inside the vehicle, secure air cleanliness, and remove fog or frost from the vehicle window. Such an air conditioner generally converts low-temperature, low-pressure gaseous refrigerant introduced from the evaporator to high-temperature, high-pressure of the gaseous refrigerant is compressed and sent to the condenser.

Compressors are largely classified into a reciprocating compressor that compresses refrigerant according to the reciprocating motion of a piston and a rotary compressor that compresses refrigerant by rotational motion. It is classified into crank type compressor, swash plate type compressor using a rotating shaft installed with a swash plate, etc. Rotary type compressor is a vane rotary type compressor using a rotating rotary shaft and vanes, and a scroll type compressor using an orbiting scroll and a fixed scroll. classified, etc.

Among these various types of compressors, scroll-type electric compressors using orbiting scrolls and fixed scrolls perform suction, compression, and discharge continuously, so compared to other compressors, vibration and noise generated during operation are small and relatively high. It is widely used as a refrigerant compressor for air conditioners because it has the advantage of obtaining a compression ratio.

The scroll type electric compressor includes a fixed scroll with a fixed wrap and an orbiting scroll with an orbiting wrap engaged with the fixed wrap. As a result, the refrigerant introduced into the compression chamber is compressed while the volume of the compression chamber formed between the fixed wrap of the fixed scroll and the orbiting wrap of the orbiting scroll continuously changes.

On the other hand, Figure 1 shows the rotor assembly structure of the electric motor for rotating the orbiting scroll in the conventional scroll type electric compressor.

As shown in FIG. 1, the rotor of the electric motor installed in the conventional scroll type electric compressor includes a rotor core 10 and a drive shaft 20 coupled to the inside of the rotor core 10.

Here, the drive shaft 20 is press-fitted into the hollow hole 12 of the rotor core 10 and assembled. 20) is coupled between the driving shaft 20 and the rotor iron core 10 to prevent idling.

That is, key grooves 24 and 14 into which a portion of the shaft key 50 can be inserted are formed on the outer surface of the drive shaft 20 and the inner surface of the hollow hole 12 of the rotor core 10, respectively, so that the drive shaft 20 Rotation of the drive shaft 20 inside the rotor core 10 is prevented by rotating the shaft key 50 while being engaged with the key groove 24 and the key groove 14 of the rotor core 10, respectively.

In this case, since vibration durability is required due to the nature of the electric compressor mounted on the vehicle, it is important to design the shaft key 50 not to move when the drive shaft 20 is press-fitted into the rotor iron core 10. However, in the conventional rotor assembly structure in which the rotor core 10 and the drive shaft 20 are assembled using the shaft key 50, the rotor core 10 is press-fitted with the drive shaft 20 inside the rotor core 10. (10) and the key grooves 14 and 24 formed on the drive shaft 20 and the axis keys 50 engaged with each key groove 14 and 24 do not have dimensions that do not match, causing the axis keys 50 to move.

In addition, since the shaft key 50 must be used for assembling the rotor core 10 and the drive shaft 20, the number of assembly parts increases, and the hollow shaft of the rotor core 10 engages the shaft key 50. Since an additional process of forming the key grooves 14 and 24 on the outer surface of the hole 112 and the drive shaft 20 is required, the manufacturing process is increased, which increases the manufacturing cost of the electric compressor.

Korean Patent Publication No. 2010-0058821 (2010.06.04)

The present invention has been made to solve the above conventional problems, and the technical problem to be solved in the present invention is to replace the existing rotor assembly method using a shaft key and a keyway with an assembly method using a drive shaft and a counterweight, An object of the present invention is to provide a rotor assembly structure of an electric compressor capable of reducing the number of parts and simplifying the assembly process to reduce manufacturing costs.

A rotor assembly structure of an electric compressor according to the present invention for solving the above technical problems includes a rotor iron core having a hollow hole therein; a drive shaft press-fitted into the hollow hole of the rotor core; A balance weight having an outer diameter surface corresponding to the outer diameter of the rotor core and an inner diameter surface corresponding to the outer diameter of the drive shaft, and coupled to an end of the rotor core, a chamfered groove is formed on the outer diameter surface of the drive shaft, and the inner diameter of the counterweight is A coupling surface having a shape corresponding to the chamfered groove is formed on the surface, and the chamfered groove and the coupling surface are engaged with each other in a state where the drive shaft is press-fitted into the hollow hole of the rotor core, thereby preventing idle rotation between the rotor core and the drive shaft. do.

In this case, the chamfering groove and the coupling surface may be machined into a flat shape.

And, the drive shaft includes a first drive shaft portion having a larger diameter than the hollow hole of the rotor iron core; It may include a second drive shaft having a diameter smaller than that of the first drive shaft and being press-fitted into the hollow hole of the rotor core.

In addition, the balance weight, a first balance weight coupled to one end of the rotor core adjacent to the first drive shaft portion; It may be configured to include; a second balance weight coupled to the other end of the rotor core adjacent to the end of the second driving shaft.

At this time, the chamfering groove may be formed on an outer surface of the first driving shaft, and the coupling surface may be formed on an inner diameter surface of the first balance weight.

Alternatively, the chamfering groove may be formed on the outer surface of the end of the second drive shaft, and the coupling surface may be formed on the inner diameter surface of the second balance weight.

According to the rotor assembly structure of the electric compressor of the present invention having the above configuration, it is possible to prevent idle rotation between the rotor core and the drive shaft through a simple shape change of the drive shaft and the balance weight coupled to the rotor core. The number of assembly parts and the assembly process can be simplified because the use of shaft keys and keyways used in the rotor assembly structure of the existing electric compressor can be eliminated. Since it is not necessary, there is an advantage in reducing the manufacturing cost of the electric compressor and improving the productivity of the product.

1 is a perspective view showing the rotor structure of an electric motor installed in a conventional electric compressor.
2 is a perspective view showing a rotor structure of an electric compressor according to the present invention.
3 is a perspective view of FIG. 2 viewed from another direction;
Figure 4 is an exploded perspective view of Figure 2;
5 is a perspective view showing an assembly structure of a rotor iron core and a drive shaft according to a first embodiment of the present invention;
Figure 6 is a perspective view showing a combined state of Figure 5;
7 is a perspective view showing an assembly structure of a rotor iron core and a drive shaft according to a second embodiment of the present invention;
Figure 8 is a perspective view showing the combined appearance of Figure 7;

Hereinafter, with reference to the accompanying drawings, embodiments of the present invention will be described in detail so that those skilled in the art can easily carry out the present invention.

However, the present invention may be implemented in many different forms and is not limited to the embodiments described herein. In addition, parts marked with the same reference numerals throughout the detailed description indicate the same components.

Hereinafter, a rotor assembly structure of an electric compressor according to an embodiment of the present invention will be described in detail.

Figure 2 is a perspective view showing the main configuration around the rotor of the internal electric motor in the electric compressor of the present invention, Figure 3 is a perspective view of Figure 2 viewed from another direction. And, FIG. 4 is an exploded perspective view of FIG. 2 .

2 to 4, the electric compressor according to the present invention performs an eccentric turning motion by a fixed scroll (not shown) fixed inside the housing and a rotational force transmitted from the drive shaft 120 of the electric motor engaged with the fixed scroll. It is configured to include a orbiting scroll 180 to.

That is, the fixed scroll and the orbiting scroll 180 performing an eccentric turning motion are engaged to form a compression chamber, and the orbiting scroll 180 moves into the compression chamber while performing an eccentric turning motion by the rotational force transmitted through the drive shaft 120 of the electric motor. It operates by compressing the introduced refrigerant.

In this case, in the process of compressing the refrigerant in the compression chamber by the eccentric pivoting motion of the orbiting scroll 180, the rotational imbalance caused by the eccentric pivoting motion of the orbiting scroll 180 is compensated through the eccentric weight 150 and the balance weights 130 and 140. can do.

In addition, the rotor of the electric motor enabling the eccentric rotational movement of the orbiting scroll 180 includes a rotor iron core 110 having a hollow hole 112 formed therein, and an inner hollow hole 112 of the rotor iron core 110. It includes a driving shaft 120 coupled to and balance weights 130 and 140 coupled to both ends of the rotor iron core 110 to compensate for rotational imbalance due to the eccentric rotational movement of the orbiting scroll 180.

In addition, at one end of the driving shaft 120, an eccentric pin 160 is coupled to a position eccentric from the center of the driving shaft 120, and an eccentric weight 150 located on the opposite side of the driving shaft 120 is an eccentric pin ( 160), the eccentric weight 150 may be eccentrically rotated in conjunction with the drive shaft 120. In this case, the eccentric weight 150 serves to enable the eccentric rotational motion of the orbiting scroll 180 and serves as a balance weight to balance the rotational imbalance caused by the eccentric rotational motion.

And, at the center of rotation of the eccentric weight 150 coupled with the eccentric pin 160, the coupling shaft 152 protruding in the direction where the orbiting scroll 180 is located is inserted into the rear surface of the orbiting scroll 180 and coupled thereto, thereby rotating the scroll. (180) can perform an eccentric rotational movement together with the eccentric weight (150). In addition, bearings 172 and 174 for smooth rotation are installed on the outer surface of the drive shaft 120 performing rotational motion and on the outer surface of the coupling shaft 152 of the eccentric weight 150.

On the other hand, the balance weights 130 and 140 coupled to both ends of the rotor iron core 110 are involved in the eccentric turning motion of the orbiting scroll 180 together with the eccentric weight 150 performing the eccentric pivoting motion while being coupled to the orbiting scroll 180. It plays a role in compensating for rotational imbalance.

The balance weights 130 and 140 have a semicircular structure and are assembled at both ends of the rotor core 110 in a state in which they are arranged at positions crossing each other in a diagonal direction with respect to the central axis of the rotor core 110.

In this case, in designing the balance weights 130 and 140, the outer and inner diameters of the balance weights 13 and 140 are designed based on the outer diameter of the rotor core 110 and the outer diameter of the drive shaft 120 as reference values. That is, the outer diameter surfaces of the balance weights 130 and 140 are designed to correspond to the outer diameter of the rotor core 110, and the inner diameter surfaces of the balance weights 130 and 140 are designed to correspond to the outer diameter of the driving shaft 120.

On the other hand, as mentioned in the background art above, in the rotor structure for an electric compressor of the conventional type, in order to prevent the drive shaft from idling due to a decrease in pressing force in the state in which the drive shaft and the rotor core are assembled, there is a gap between the drive shaft and the rotor core. A shaft key is inserted to prevent the drive shaft from idling inside the rotor core (see FIG. 1).

However, in the conventional rotor assembly structure, when the dimensions between the keyway and the shaft key formed on the rotor iron core and the drive shaft do not match, a phenomenon in which the shaft key moves inside the keyway may occur. In addition, since the use of an axis key is necessarily required to prevent the drive shaft from idling inside the rotor core, the number of assembly parts increases, and a keyway for inserting the axis key must be formed inside the hollow hole of the rotor core and outside the drive shaft. Since an additional process is required, there are various problems such as an increase in the manufacturing cost of the product due to an increase in the assembly process.

In order to solve various problems occurring in the existing rotor assembly method using such an axis key, in the present invention, the balance weights 130 and 140 coupled to the rotor iron core 110 and the drive shaft 120 instead of the existing method using an axis key ) is used to prevent idle rotation between the rotor core 110 and the drive shaft 120.

Hereinafter, this will be described in more detail.

5 shows an assembly structure of a rotor iron core and a drive shaft according to a first embodiment of the present invention, and FIG. 6 shows a combined state of FIG. 5 .

5 and 6, the drive shaft 120 according to the first embodiment of the present invention includes a first drive shaft portion 121 having a larger diameter than the hollow hole 112 of the rotor iron core 110, A second drive shaft portion 123 having a smaller diameter than the first drive shaft portion 121 is included.

In this case, since the diameter of the first drive shaft portion 121 is larger than the diameter of the hollow hole 112 of the rotor iron core 110, the first drive shaft portion 121 cannot be inserted into the hollow hole 112 and rotates. It is exposed to the front side of the electron core 110.

In addition, since the second drive shaft portion 123 has a diameter smaller than that of the first drive shaft portion 121 and is formed to have a diameter substantially similar to that of the hollow hole 112 of the rotor core, the second drive shaft portion 123 is a hollow hole. (112) can be press-fitted into the interior. In this case, in a state in which the second drive shaft portion 123 is completely press-fitted into the hollow hole 112, the end portion 124 of the second drive shaft portion 123 is exposed to the outside of the hollow hole 112.

On the other hand, the balance weights 130 and 140 are press-fitted into the first balance weight 130 coupled to one end of the rotor core 110 adjacent to the first drive shaft portion 121 and the hollow hole 112 to form a hollow hole 112. It is configured to include a second balance weight 140 coupled to the opposite end of the rotor iron core 110 adjacent to the end 124 of the second driving shaft 123 partially exposed to the outside.

Here, in the rotor assembly structure according to the first embodiment of the present invention, the outer diameter surface of the first drive shaft portion 121 exposed to the outside of the rotor iron core 110 is chamfered to have a flat shape through chamfer processing. A chamfered groove 122 is formed. That is, the chamfered groove 122 may be formed on the outer diameter surface of the first driving shaft portion 121 coming into contact with the inner diameter surface 132 of the first balance weight 130 .

At the same time, on the inner diameter surface 132 of the first balance weight 130, the coupling surface processed into a plane shape corresponding to the chamfered groove 122 formed in the first drive shaft portion 121 to make surface contact with the chamfered groove 122. (134) may be formed.

Accordingly, as shown in FIG. 6, the chamfered groove 122 formed in the first drive shaft portion 121 and the first balance weight in a state in which the drive shaft 120 is completely press-fitted into the hollow hole 112 of the rotor iron core 110 Since the coupling surfaces 134 formed on the 130 come into surface contact with each other to rotate in an engaged state, idle rotation between the rotor core 110 and the drive shaft 120 can be prevented.

Meanwhile, FIG. 7 shows an assembly structure of a rotor iron core and a driving shaft according to a second embodiment of the present invention, and FIG. 8 shows a combined state of FIG. 7 .

As shown in FIGS. 7 and 8, the rotor assembly structure of the electric compressor according to the second embodiment of the present invention has a flat chamfer on the second drive shaft portion 123, unlike the case of the first embodiment described above. A groove 125 is formed, and a coupling surface 144 having a planar shape corresponding to the chamfered groove 125 is formed on the inner diameter surface 142 of the second balance weight 140.

In this case, the chamfered groove 125 is press-fitted into the outer diameter surface of the second driving shaft part 123 that comes into contact with the inner diameter surface 142 of the second balance weight 140, that is, the rotor core 110, and then moves toward the rear side. It may be formed on the outer diameter surface of the second driving shaft part 123 that is exposed and comes into contact with the inner diameter surface 142 of the second balance weight 140 .

In addition, on the inner diameter surface 142 of the second balance weight 140, the coupling surface processed into a flat shape corresponding to the chamfered groove 125 formed in the second drive shaft portion 123 to make surface contact with the chamfered groove 125. (144) may be formed.

Accordingly, as shown in FIG. 8, the chamfered groove 125 formed in the second drive shaft portion 123 in a state in which the drive shaft 120 is completely press-fitted into the hollow hole 112 of the rotor iron core 110 and Idle rotation between the rotor core 110 and the drive shaft 120 can be prevented as the coupling surfaces 144 formed on the second balance weight 140 come into surface contact with each other to perform rotational movement in an engaged state.

As described above, in the present invention, planar chamfered grooves 122 and 125 are formed on the outer diameter surface of the drive shaft 120 press-fitted into the rotor core 110, and the balance weight coupled to the end of the rotor core 110. Coupling surfaces 134, 144 having a shape corresponding to the chamfered grooves 122, 125 are formed on the inner diameter surfaces of the (130, 140), and the chamfered grooves 122, 125 formed on the drive shaft 120 and the coupling surfaces 134, 144 formed on the balance weights 130, 140 ) is configured to rotate in a state of being engaged with each other while making surface contact, thereby preventing the rotor iron core 110 and the driving shaft 120 from spinning each other.

As such, the present invention can prevent idle rotation between the rotor core 110 and the drive shaft 120 by simply changing the shape of the drive shaft 120 and the balance weights 130 and 140 coupled to the rotor core 110, and There is an advantage in that the number of assembly parts can be reduced and the assembly process can be simplified by excluding the use of the shaft key and the keyway used in the rotor assembly structure of the electric compressor. In addition, since there is no need for a complicated machining process for forming a keyway inside the rotor core as in the conventional method, there is an advantage in reducing product manufacturing costs and improving product productivity.

Although preferred embodiments of the present invention have been described above, the scope of the present invention is not limited to such specific embodiments, and those skilled in the art can make appropriate changes within the scope described in the claims of the present invention. this will be possible

110: rotor iron core 112: hollow hole
120: drive shaft 121: first drive shaft
122,125: chamfering groove 123: second drive shaft
130,140: Counterweight 134,144: Coupling surface
150: eccentric weight 160: eccentric pin
172,174: bearing 180: orbiting scroll

Claims (7)

delete delete delete delete a rotor iron core having a hollow hole therein;
a drive shaft press-fitted into the hollow hole of the rotor core;
A balance weight having an outer diameter surface corresponding to the outer diameter of the rotor core and an inner diameter surface corresponding to the outer diameter of the drive shaft, and coupled to an end portion of the rotor iron core;
A chamfering groove is formed on the outer diameter surface of the drive shaft, and a coupling surface having a shape corresponding to the chamfering groove is formed on the inner diameter surface of the balance weight. The groove and the coupling surface are engaged with each other to prevent idle rotation between the rotor core and the drive shaft,
The drive shaft is
a first driving shaft having a larger diameter than the hollow hole of the rotor iron core;
A second drive shaft having a diameter smaller than that of the first drive shaft and being press-fitted into the hollow hole of the rotor iron core;
the counterweight,
a first balance weight coupled to one end of the rotor core adjacent to the first drive shaft;
A second balance weight coupled to the other end of the rotor core adjacent to the end of the second drive shaft; includes,
The rotor assembly structure of the electric compressor, characterized in that the chamfering groove is formed on the outer surface of the first drive shaft portion, and the coupling surface is formed on the inner diameter surface of the first balance weight.
a rotor iron core having a hollow hole therein;
a drive shaft press-fitted into the hollow hole of the rotor core;
A balance weight having an outer diameter surface corresponding to the outer diameter of the rotor core and an inner diameter surface corresponding to the outer diameter of the drive shaft, and coupled to an end portion of the rotor iron core;
A chamfering groove is formed on the outer diameter surface of the drive shaft, and a coupling surface having a shape corresponding to the chamfering groove is formed on the inner diameter surface of the balance weight. The groove and the coupling surface are engaged with each other to prevent idle rotation between the rotor core and the drive shaft,
The drive shaft is
a first driving shaft having a larger diameter than the hollow hole of the rotor iron core;
A second drive shaft having a diameter smaller than that of the first drive shaft and being press-fitted into the hollow hole of the rotor iron core;
the counterweight,
a first balance weight coupled to one end of the rotor core adjacent to the first driving shaft;
And a second balance weight coupled to the other end of the rotor core adjacent to the end of the second driving shaft,
The rotor assembly structure of the electric compressor, characterized in that the chamfering groove is formed on the outer surface of the end of the second drive shaft, and the coupling surface is formed on the inner diameter surface of the second balance weight.
The rotor assembly structure of an electric compressor according to claim 5 or 6, wherein the chamfered groove and the coupling surface are machined in a flat shape.

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