KR20140098457A - Electric motor-driven compressor - Google Patents

Electric motor-driven compressor Download PDF

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Publication number
KR20140098457A
KR20140098457A KR1020130011123A KR20130011123A KR20140098457A KR 20140098457 A KR20140098457 A KR 20140098457A KR 1020130011123 A KR1020130011123 A KR 1020130011123A KR 20130011123 A KR20130011123 A KR 20130011123A KR 20140098457 A KR20140098457 A KR 20140098457A
Authority
KR
South Korea
Prior art keywords
main bearing
damping member
housing
circumferential surface
bearing
Prior art date
Application number
KR1020130011123A
Other languages
Korean (ko)
Inventor
오성택
정석제
남궁규
Original Assignee
한라비스테온공조 주식회사
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 한라비스테온공조 주식회사 filed Critical 한라비스테온공조 주식회사
Priority to KR1020130011123A priority Critical patent/KR20140098457A/en
Publication of KR20140098457A publication Critical patent/KR20140098457A/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

The present invention relates to a motor-driven compressor. The motor-driven compressor includes a novel structure to prevent the operational malfunction of a bearing and the noise due to the temperature change of the hearing as well as the occurrence of a seizure by improving the coupling structure between the bearing and a housing unit while ensuring the coupling to be smoothly made. Accordingly, the present invention additionally includes a damping member arranged on the coupling area of the bearing and the housing included in the motor-driven compressor to compensate the coupling differences of the bearing and provide a damping force to fix the bearing in the housing regardless of the temperature.

Description

[0001] Electric motor-driven compressor [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electric compressor, and more particularly, to a coupling structure between a compressor housing unit and an inverter assembly constituting an electric compressor.

Generally, a compressor used in an air conditioning system of an automobile performs a function of sucking refrigerant that has been evaporated from an evaporator and converting it into a high-temperature and high-pressure state which is easy to be liquefied and delivering it to a condenser.

The compressor is provided with a driving force from an engine of a vehicle to perform a compression operation, and a method of performing a compression operation by driving an electric motor according to a separate power supply.

In the case of an electric compressor that performs a compressing operation by driving an electric motor, the power of the motor unit 20 and the motor unit 20 is received in the housing unit 10 as shown in FIG. 1 to compress the refrigerant The compression mechanism 30 is provided to adjust the rotational speed of the motor unit 20 by controlling the operation of the inverter assembly 14 so that the cooling efficiency can be variably controlled.

The motor unit 20 includes a stator 21 fixed in the housing unit 10 and a rotor 22 rotatably installed in the stator 21, Is configured to rotate together with the rotor (22) while the drive shaft (60) is inserted through the rotor.

An eccentric bush 61 is provided at the front end of the drive shaft 60 to rotate the scroll (rotary scroll) 32 of the compression mechanism 30.

A main bearing 40 is provided around the front end of the drive shaft 60 and the main bearing 40 supports the rotation of the drive shaft 60.

2, the main bearing 40 includes an inner race 41 rotatably coupled to the drive shaft 60 while press-fitting the circumferential surface of the drive shaft 60 into the housing race 10, And a plurality of balls 43 provided between the inner race 41 and the outer race 42. [

However, due to the difference in thermal expansion coefficient between the material of the drive shaft 60, the material of the housing part 10, and the material of the main bearing 40, the clearance gap value of the main bearing 40 is changed by temperature There is a problem that the determination is not easy.

That is, when the tolerance of the main bearing 40 is selected on the basis of a low temperature, there is a problem that the internal tolerance of the main bearing 40 is increased at a high temperature and noise is generated. In consideration of this, There has been a problem of causing the main bearing 40 to be disengaged.

In addition, in the case of the outer race 42 constituting the main bearing 40, since the tolerance with respect to the housing part 10 is very finely selected in order to prevent the rotation of the outer race 42, ), There were many difficulties.

SUMMARY OF THE INVENTION It is an object of the present invention to improve a coupling structure between a bearing and a housing part to thereby improve noise or noise due to operation failure of the bearing, And to provide an electric compressor according to a new type in which the coupling can be smoothly performed.

According to an aspect of the present invention, there is provided a variable displacement swash plate type compressor, including a motor unit and a compression mechanism unit, the main bearing supporting a drive shaft coupled to a rotor of the motor unit, The main bearing is damped so as to be fixed in the housing part regardless of the temperature change while compensating for the engagement tolerance of the main bearing, between the engagement part of the main bearing and the housing part, And a damping member for supporting and supporting the force.

Here, an accommodating groove for accommodating the damping member is formed on one of the inner circumferential surface of the housing portion facing the outer circumferential surface of the main bearing or the outer circumferential surface of the main bearing, so that the undesired axial movement In order to prevent the problem.

The damping member may include a ring-shaped ring-shaped body surrounding the outer circumferential surface of the main bearing, and elastic protrusions protruding from the outer circumferential surface of the ring-shaped body.

In addition, the elastic protrusions constituting the damping member are provided in a plurality of along the circumferential direction of the ring-shaped body, and are spaced apart from each other with a predetermined distance therebetween.

In addition, each of the elastic protrusions constituting the damping member is formed so as to protrude toward at least one of the outer circumferential surface of the main bearing and the inner circumferential surface of the housing portion, and the spacing distance and the protrusion height between the elastic protrusions And is designed differently depending on the pressing force of the bearing.

Further, the ring-shaped body constituting the damping member is formed by cutting at one end.

In the electric compressor according to the present invention as described above, even if the shape of the coupling portion between the main bearing and the housing portion caused by the temperature change in the housing portion is generated, due to the damping force provided from the damping member, The coupling force between the main bearing and the main bearing can be always kept constant, thereby preventing the occurrence of start-up noise and the disconnection of the main bearing.

Particularly, since the main bearing can be always kept in a stable press-fit state in the housing part, the vertical vibration of the drive shaft due to the swinging of the main bearing can also be prevented originally, Or damage to the compression mechanism, etc.) can be prevented.

1 is a cross-sectional view illustrating an internal structure of a conventional electric compressor
Fig. 2 is an enlarged view of the " A &
3 is a cross-sectional view illustrating an internal structure of an electric compressor according to a preferred embodiment of the present invention
Fig. 4 is an enlarged view of " B &
5 is a perspective view illustrating a damping member of an electric compressor according to a preferred embodiment of the present invention.

Hereinafter, a preferred embodiment of the electric compressor of the present invention will be described in more detail with reference to FIGS. 3 to 5.

Fig. 4 is an enlarged view of the portion " B " in Fig. 2, and Fig. 5 is an enlarged view of the electric compressor according to the embodiment of the present invention. Fig. 3 is a perspective view showing the damping member of Fig.

As can be seen from these drawings, the electric compressor according to the embodiment of the present invention mainly includes a housing part 100, a motor part 200, a compression mechanism part 300, bearings 410 and 420, and a damping member 500 ).

This will be described in more detail below for each configuration.

First, the housing unit 100 includes an intermediate housing 110, a front housing 120, and a rear housing 130, which form an outer appearance of the electric compressor.

The intermediate housing 110 is configured to form a part of a compression chamber 111 for compressing a refrigerant and a motor chamber 112 for accommodating a portion of the motor unit 200. The front housing 120, A discharge chamber 121 through which the refrigerant compressed by the compression chamber compression mechanism 300 of the intermediate housing 110 is discharged is formed while being coupled to the front of the intermediate housing 110, Is configured to form another portion of the motor chamber 132 for receiving the remaining portion of the motor unit 200 together with the intermediate housing 110 while being coupled to the rear of the intermediate housing 110. [

At the rear of the rear housing 130, an inverter assembly 140 for controlling the amount of compression of the refrigerant is provided.

Of course, although not shown, the housing part 100 is not formed separately from the intermediate housing 110, the front housing 120, and the rear housing 130, but the front housing 120, And the rear housing 130, as well as the entire structure may be formed as a single body, or may be formed as four or more separate structures.

Next, the motor unit 200 generates a driving force for the compression operation of the compression mechanism unit 300.

The motor unit 200 includes a stator 210 for generating a magnetic field in a fixed state within the housing unit 100 and a stator 210 rotatably installed in the stator 210 and rotated by a magnetic field of the stator 210 And a rotor (220).

Here, the stator 210 has a plurality of ring-shaped core pieces passing through the center thereof, and is formed into a cylindrical shape. A coil (not shown) is wound around the stator 210.

The rotor 220 is formed into a cylindrical shape passing through the center of the rotor 220. The driving shaft 600 passes through the center of the rotor 220 and is inserted into the inner circumferential surface of the rotor 220, Is configured to rotate with the rotor (220).

An eccentric bushing 610 provided to rotate the rotary scroll 320 of the compression mechanism 300 is coupled to the tip of the drive shaft 600. The tip of the eccentric bushing 610 rotates eccentrically while drawing a circular locus, and functions to revolve the orbiting scroll 320 constituting the compression mechanism unit 300.

Next, the compression mechanism 300 includes a fixed scroll 310 and a orbiting scroll 320 as a portion for sucking and compressing the refrigerant.

The fixed scroll 310 is fixed to the inner end of the intermediate housing 110 constituting the housing part 100 and the orbiting scroll 320 is coupled to the driving shaft 310 through the eccentric bushing 610. [ 600 to compress the refrigerant in the compression space 330 formed between the fixed scroll 310 and the orbiting scroll 320 while revolving the fixed scroll 310.

The bearings 410 and 420 support various rotatably driven parts and include a main bearing 410 for supporting the tip of the drive shaft 600 and auxiliary bearings 420 for supporting the rear end of the drive shaft 600 ).

The main bearing 410 includes an inner race 411 that is rotated together with the driving shaft 600 while press-fitting the distal end side surface of the driving shaft 600 and an outer race 411 which is press-fitted into the housing portion 100 412) and a plurality of balls 413 provided between the inner race 411 and the outer race 412.

The damping member 500 is provided between the coupling part between the housing part 100 and the main bearing 410 to provide a damping force to compensate for the coupling tolerance of the main bearing 410 .

That is, the coupling allowance of the main bearing 410 can be compensated by providing the damping member 500, and the main bearing 410 can be stably stored in the housing part 100 regardless of the temperature change. So as to provide a damping force for achieving a fixed state.

In the embodiment of the present invention, the damping member 500 is press-fitted between the outer circumferential surface of the main bearing 410 and the inner circumferential surface of the intermediate housing 110 corresponding thereto.

5, the damping member 500 includes a ring-shaped body 510 having a ring shape surrounding the outer peripheral surface of the outer race 412 constituting the main bearing 410, And an elastic protrusion 520 protruding from the outer circumferential surface of the protrusion 510.

At this time, since the ring-shaped body 510 is formed so as to be cut at one end, the damping member 500 is installed between the main bearing 410 and the intermediate housing 110, .

When the main bearing 410 is coupled to the intermediate housing 110, the elastic protrusions 520 provide elastic restoring force between the main bearing 410 and the intermediate housing 110, And provides a damping force toward the radial direction while forming the press-fitted state. That is, regardless of the deformation force of the main bearing 410 or the intermediate housing 110 due to the temperature change due to the damping force of the elastic protrusion 520, the main bearing 410 is inserted into the intermediate housing 110 So that it is possible to maintain the press-fit state with a constant pressure input.

The elastic protrusions 520 are provided in a plurality of along the circumferential direction of the ring-shaped body 510 and spaced apart from each other with a predetermined gap therebetween, Resilience should be provided.

In particular, each of the elastic protrusions 520 protrudes toward at least one of an outer circumferential surface of the main bearing 410 and an inner circumferential surface of the intermediate housing 110, and the spacing between the elastic protrusions 520 And the protrusion height may be designed differently according to the shape change amount of the main bearing 410 and the intermediate housing 110 according to the temperature reference. That is, in consideration of the temperature change of the main bearing 410 on the low temperature basis or the shape change amount of the main bearing 410 on the high temperature basis according to the temperature change, the spacing between the elastic protrusions 520, So that the main bearing 410 can be stably fixed at all times.

4, a receiving groove 414 in which the damping member 500 is received is formed on the circumferential surface of the outer race 412 constituting the main bearing 410, To prevent undesired axial flow of the fluid (500). That is, the damping member 500 can be accommodated in the receiving groove 414 of a predetermined width, so that the damping member 500 can be moved in the process of installing the main bearing 410 on the intermediate housing 110 So that it is prevented from being seated between the main bearing 410 and the intermediate housing 110 by moving in the axial direction.

Of course, the receiving groove 414 may be formed on the inner circumferential surface of the step where the main bearing 410 of the intermediate housing 110 is accommodated.

The damping member 500 may be formed of any one of a synthetic resin material, a metal material, and a ceramic material. However, in order to provide a smooth damping force by the elastic protrusions, for example, stainless steel (SUS) It is more preferable to be formed of a steel material such as carbon steel.

Hereinafter, the operation state of the electric compressor according to the embodiment of the present invention and the action of the damping member 500 will be described in more detail.

First, when power is externally applied to the motor-driven compressor, electric power is supplied from the inverter assembly 140 to the stator 210 constituting the motor unit 200, so that the rotor 220 constituting the motor unit 200 .

When the rotor 220 is rotated as described above, the driving shaft 600 coupled to the rotor 220 is rotated together to rotate the orbiting scroll 320. By the rotation of the orbiting scroll 320, The volume for the compression space 330 between the scroll 320 and the fixed scroll 310 gradually changes.

When the above process is performed, the refrigerant flows into the compression space 330 between the orbiting scroll 320 and the fixed scroll 310 through a suction port (not shown) And then gradually compressed in accordance with the volume change of the compression space 330 due to revolution of the orbiting scroll 320 described above and then discharged to the outside of the housing part 100 through the discharge port (not shown) .

Meanwhile, during the compression operation of the electric compressor described above, a temperature change occurs in the housing part 100, and the shape of the main bearing 410 and the shape of the intermediate housing 110 Deformation occurs.

A damping member 500 is provided between the main bearing 410 and the intermediate housing 110. The elastic protrusions 520 of the damping member 500 are connected to the main bearing 410, Since the damping force is constantly provided toward the opposite direction between the damping member 500 and the intermediate housing 110, the shape deformation of the main bearing 410 and the intermediate housing 110 can be reduced, So that the pressure input between the main bearing 410 and the intermediate housing 110 is always kept constant, thereby preventing the generation of noise and the occurrence of the occurrence of the noise.

As a result, the electric compressor according to the embodiment of the present invention is capable of preventing the start noise or the seizing of the main bearing 410 caused by the temperature change in the housing part 100 by the additional provision of the damping member 500 And vibration of the drive shaft 600 in the vertical direction can also be prevented, so that it is possible to prevent damage (e.g., damage to the eccentric bush, compression mechanism, etc.) of the related internal components.

Meanwhile, the damping member 500 of the electric compressor according to the present invention is not limited to being provided only at the joint portion between the main bearing 410 and the housing portion 100 as in the above-described embodiment.

Although not shown, the damping member 500 may be provided between the coupling portion between the auxiliary bearing 420 and the rear housing 120, as well as another bearing 430 supporting the eccentric bushing 620, Eccentric bushes 620. [0064] As shown in Fig.

As described above, the damping member 500 of the electric compressor according to the present invention is a useful invention that can be applied to bearings 410, 420, and 430 and any portion between the bearings 410, 420, and 430.

100. Housing part 110. Middle housing
111. Compression chambers 112, 132. Motor room
120. Front housing 130. Rear housing
140. Inverter assembly 200. Motor section
210. Stator 220. Rotor
300. Compression mechanism section 310. Fixed scroll
320. Turning scroll 330. Compression space
410. Main Bearings 411. Inner Lace
412. Outer Race 413. Ball
414. Receiving groove 420. Auxiliary bearing
430. Bearing 500. Damping element
510. Ring-shaped body 520. Elastic projection
600. Drive shaft 610. Eccentric Bush

Claims (6)

A main bearing 410 including a motor unit 200 and a compression mechanism 300 in the housing unit 100 and supporting a drive shaft 600 coupled to the rotator 220 of the motor unit 200, Is press-fitted into the housing part (100), the electric compressor
The main bearing 410 is fixed within the housing part 100 regardless of the temperature change while compensating for the engagement tolerance of the main bearing 410 between the coupling part between the main bearing 410 and the housing part 100. [ Further comprising a damping member (500) for supporting and supporting the damping force so as to form the damping force. The method according to claim 1,
The inner circumferential surface of the housing part 100 facing the outer circumferential surface of the main bearing 410 or the outer circumferential surface of the main bearing 410 is provided with a receiving groove 414 for receiving the damping member 500 Is configured to prevent undesired axial movement of the damping member (500). The method according to claim 1 or 2,
The damping member (500)
A ring-shaped ring-shaped body 510 surrounding the outer circumferential surface of the bearing 410,
And an elastic protrusion (520) protruding from an outer circumferential surface of the ring-shaped body (510). The method of claim 3,
Wherein the elastic protrusions (520) of the damping member (500) are provided in a plurality of along the circumferential direction of the ring-shaped body (510) and spaced apart from each other with a predetermined distance therebetween. 5. The method of claim 4,
The elastic protrusions 520 of the damping member 500 are formed to protrude toward at least one of the outer circumferential surface of the main bearing 410 and the inner circumferential surface of the housing portion 100,
Wherein the spacing distance and the protrusion height between the elastic protrusions (520) are designed differently according to the pressing force of the main bearing (410) according to the temperature change. The method of claim 3,
Wherein the ring-shaped body (510) constituting the damping member (500) is formed by cutting one end of the ring-shaped body (510).
KR1020130011123A 2013-01-31 2013-01-31 Electric motor-driven compressor KR20140098457A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020130011123A KR20140098457A (en) 2013-01-31 2013-01-31 Electric motor-driven compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020130011123A KR20140098457A (en) 2013-01-31 2013-01-31 Electric motor-driven compressor

Publications (1)

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KR20140098457A true KR20140098457A (en) 2014-08-08

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Application Number Title Priority Date Filing Date
KR1020130011123A KR20140098457A (en) 2013-01-31 2013-01-31 Electric motor-driven compressor

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