JP2009091986A - Motor-driven compressor for vehicular air conditioning - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vehicular air conditioning motor-driven compressor for securing sufficient air tightness under corrosive conditions. <P>SOLUTION: The compressor comprises a plurality of casings 13, 15, 67 constituting a container storing a compression part for compressing refrigerant, a first shield part 101 having annular grooves 111A, 111B formed on one mating face out of those of the plurality of casings 13, 15, 67 and annular elastic members 112A, 112B arranged inside the grooves 111A, 111B, and a second shield part 102 annularly arranged on one mating face or the other mating face in a region outside the first shield part 101. <P>COPYRIGHT: (C)2009,JPO&amp;INPIT

Description

  The present invention relates to an electric compressor for vehicle air conditioning.

  2. Description of the Related Art Conventionally, in an inverter-integrated electric compressor for vehicle air conditioning (electric compressor for vehicle air conditioning), a type in which a scroll compressor using a fixed scroll and a turning scroll is driven by an electric motor is often used (for example, Patent Documents). 1 to 3).

Such an inverter-integrated electric compressor for vehicle air conditioning is integrally formed by tightening a housing and an upper bearing that form a space in which a fixed scroll, a turning scroll, and the like are accommodated, and a motor case having a space in which the electric motor is accommodated with a bolt. It is often configured to. As a result, in order to form a sealed container by the housing, the upper bearing and the motor case, the mating surfaces of the housing and the upper bearing and the mating surfaces of the upper bearing and the motor case are in surface contact with each other. The seal structure using the seal and one O-ring was used.
Japanese Unexamined Patent Publication No. 7-19185 JP-A-8-74769 No. 4-10390

  However, with the above-described seal structure alone, under severe corrosion resistance test conditions such as salt water spray, the housing and the like corrode, resulting in incomplete sealing due to surface contact. There is a problem that it may become complete, and it is difficult to ensure sufficient sealing performance.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a vehicle air-conditioning electric compressor capable of ensuring sufficient airtightness even under corrosive conditions.

In order to achieve the above object, the present invention provides the following means.
An electric compressor for vehicle air conditioning according to the present invention includes a plurality of casings that form a container that houses a compression unit that compresses a refrigerant therein, and an annular groove formed on one mating surface of the plurality of casings. And a first shielding part having an annular elastic member arranged inside the groove, and a second shielding part arranged annularly in a region outside the first shielding part in the one mating surface or the other mating surface. And a shielding part.

  According to the present invention, the first shielding portion prevents leakage of the refrigerant from the inside to the outside of the container constituted by a plurality of housings, and the second shielding portion corrodes from the outside toward the first shielding portion. Progress is prevented.

  In the above invention, the second shielding portion includes an outer groove formed in a region outside the groove on the one or other mating surfaces, and an outer annular elastic member disposed inside the outer groove. It is desirable to have

  According to the present invention, the outer annular elastic member disposed inside the outer groove prevents the progress of corrosion from the outside toward the first shielding portion.

  In the above invention, the second shielding portion is disposed in a region further outside the outer groove in the one or other mating surface, and contacts the one or other mating surfaces facing each other, and the contact It is desirable to have the inclined surface which leaves | separates from the said one or other mating surface which faces outward from a surface.

  In the above invention, the second shielding portion is disposed in a region outside the groove on the one or other mating surface and is in contact with the one or other mating surface facing each other, and the outside from the contact surface It is desirable to have the inclined surface which leaves | separates from the said one or other mating surface which opposes.

  According to the present invention, since the inclined surface is formed, the contact surface and the one or other mating surface come into reliable contact. That is, the contact surface and the one or other mating surface are annularly contacted outside the first shielding portion, thereby preventing the progress of corrosion from the outside toward the first shielding portion.

  In the above invention, it is desirable that the second shielding portion is a gasket disposed between the one and another mating surfaces and in a region outside the groove.

  According to the present invention, the progress of corrosion from the outside toward the first shielding portion is prevented by the gasket disposed between one and the other mating surfaces.

  In the above invention, the plurality of casings include at least a compression section casing and an intermediate casing that form a space in which the compression section is housed, and the compression sections are fixed to the compression section casing. A fixed scroll and a orbiting scroll that revolves around the fixed scroll and compresses the refrigerant to ensure slidability between the orbiting scroll and the intermediate housing; and It is desirable that a plate portion for adjusting the interval between the scroll and the orbiting scroll is provided.

According to the present invention, the number of parts to be used can be reduced as compared with the case of separately using parts that ensure slidability and parts that adjust the interval.
Furthermore, when assembling the electric compressor for vehicle air conditioning, the number of parts to be stacked can be reduced, and the parallelism of the scroll tooth tips after assembly is improved.

  According to the electric compressor for vehicle air conditioning of the present invention, the first shielding portion prevents leakage of the refrigerant from the inside of the container constituted by the plurality of housings to the outside, and the second shielding portion from the outside. Since the progress of corrosion toward the first shielding portion is prevented, there is an effect that sufficient airtightness can be ensured even under corrosion conditions where it is difficult to ensure airtightness.

[First Embodiment]
An electric compressor according to a first embodiment of the present invention will be described with reference to FIGS.
FIG. 1 is a cross-sectional view illustrating the outline of the configuration of the electric compressor according to the present embodiment.
In the present embodiment, the electric compressor (electric compressor for vehicle air conditioning) 1 is a compressor used in a vehicle air conditioner, and is applied to an electric compressor whose drive rotation speed is controlled by an inverter. explain.
As shown in FIG. 1, the electric compressor 1 includes a scroll compression unit (compression unit) 3 that compresses a refrigerant used in the vehicle air conditioner, and an electric unit 5 that drives the scroll compression unit 3. It has been.

  The scroll compression unit 3 includes a fixed scroll 7 and a orbiting scroll 9 that compress refrigerant, a main shaft 11 that transmits the rotational driving force of the electric unit 5 to the orbiting scroll 9, and a housing that houses the fixed scroll 7 and the orbiting scroll 9. A (housing, compression housing) 13 and an upper bearing case (housing, intermediate housing) 15 that supports a main shaft 11 to be described later are provided.

The fixed scroll 7 is provided with a fixed end plate 19 and a spiral fixed wall body 21 extending from the fixed end plate 19 toward the orbiting scroll 9.
On the other hand, the orbiting scroll 9 is supported by the main shaft 11 and the rotation prevention unit 23 so as to be revolved. The turning scroll 9 is provided with a turning end plate 25 and a spiral turning wall plate 27 extending from the turning end plate 25 toward the fixed scroll 7.
The fixed scroll 7 and the orbiting scroll 9 are arranged so as to engage the fixed wall body 21 and the orbiting wall plate 27 to form a compression chamber C therebetween.

A discharge hole 29 is provided at the center of the fixed end plate 19, and the refrigerant compressed in the compression chamber C is formed between the housing 13 and the fixed scroll 7 through the discharge hole 29 (see FIG. (Not shown).
A boss portion 33 extending toward the main shaft 11 is provided on a surface of the turning end plate 25 facing the main shaft 11. The boss portion 33 is provided with a swivel portion bearing that rotatably supports the bush 45 to which the revolution driving force by the main shaft 11 is transmitted.

  The main shaft 11 is a columnar member extending from the electric part 5 toward the orbiting scroll 9. The main shaft 11 is arranged at a position eccentric from the central axis of the disc portion 39, a cylindrical crankshaft fixed to the rotor of the electric portion 5, a disc portion 39 having a diameter larger than the crankshaft. And a crankpin 41.

  The crankpin 41 is provided with a bush 45 and a counterweight 47. The bush 45 is a cylindrical member disposed between the crankpin 41 and the boss portion 33, and transmits the driving force of the main shaft 11 to the orbiting scroll 9. The counterweight 47 balances the turning motion of the turning scroll 9.

The housing 13 is a cylindrical member having a bottom surface, and the fixed scroll 7 is fixed to the above-described bottom surface. A discharge chamber into which the refrigerant compressed by the fixed scroll 7 and the orbiting scroll 9 flows is formed between the fixed scroll 7 and the housing 13.
A first flange portion 51 is provided in the housing 13.

  The first flange portion 51 is used when the housing 13, the upper bearing case 15, and the motor case 67 are fixed integrally, and is a member that extends outward in the radial direction at an end portion on the opening side of the housing 13. is there. The first flange portion 51 is formed with a through hole through which a housing bolt 53 that integrally fixes the housing 13, the upper bearing case 15, and the motor case 67 is inserted.

  The upper bearing case 15 is a member provided with a side wall portion 55 formed in a cylindrical shape and a flange portion 57 extending radially outward from an end portion on the housing 13 side. The upper bearing case 15 is disposed so that the flange portion 57 is sandwiched between the housing 13 and the motor case 67.

A radial bearing 43 that rotatably supports the main shaft 11 is provided in the side wall portion 55 of the upper bearing case 15, and a suction passage 59 that extends along the central axis of the main shaft 11 is provided in the wall surface of the side wall portion 55. Is provided.
The flange portion 57 of the upper bearing case 15 is provided with a second flange portion 61 that is used when the housing 13, the upper bearing case 15, and the motor case 67 are fixed together. The second flange portion 61 is a member extending radially outward from the flange portion 57, and has a through hole through which the housing bolt 53 that integrally fixes the housing 13, the upper bearing case 15, and the motor case 67 is inserted. ing.

FIG. 2 is a schematic diagram illustrating the configuration of the thrust plate of FIG.
Between the upper bearing case 15 and the orbiting scroll 9, a thrust plate (plate part) that prevents the upper bearing case 15 and the orbiting scroll 9 from being worn or adhered and adjusts the distance between the orbiting scroll 9 and the fixed scroll 7. ) 141 is provided.

  Specifically, the surface of the thrust plate 141 that contacts the orbiting scroll 9 is provided with a lubricating material that ensures slidability. Examples of the lubricating material include polytetrafluoroethylene (Teflon (registered trademark)).

  The thickness of the thrust plate 141 is the distance between the fixed end plate 19 of the fixed scroll 7 and the rotating wall plate 27 of the orbiting scroll 9 when incorporated in the electric compressor 1 together with the orbiting scroll 9 and the fixed scroll 7. And the space | interval between the turning end plate 25 of the turning scroll 9 and the fixed wall body 21 of the fixed scroll 7 is selected so that it may become a predetermined space | interval.

  Here, the predetermined interval is an interval that prevents contact between the fixed end plate 19 and the swivel wall plate 27 and between the swivel end plate 25 and the fixed wall body 21, and is compressed through a gap related to the interval. This is the interval at which the leakage of the refrigerant can be suppressed.

  As shown in FIGS. 1 and 2, the thrust plate 141 is a substantially disk-shaped member in which a central hole 142 in which the boss portion 33 of the orbiting scroll 9 is disposed is formed at a substantially central position. A suction hole 143 is formed at a position surrounding the suction flow path 59. Further, the thrust plate 141 is formed with an insertion hole 144 through which the non-rotating pin 151 is inserted.

  As shown in FIG. 2, the insertion hole 144 is formed at a position asymmetric with respect to the center of the thrust plate 141. By forming the insertion hole 144 at such a position, the thrust plate 141 can be disposed between the upper bearing case 15 and the orbiting scroll 9 without making a mistake in the front and back sides.

FIG. 3 is a schematic diagram for explaining a state in which a pin used to prevent rotation of the thrust plate of FIG. 2 is press-fitted into the upper bearing case.
As shown in FIG. 3, the pin 151 is press-fitted into a press-fitting hole 152 formed in the upper bearing case 15. A curved surface portion 153 is formed at the opening end of the press-fitting hole 152.
In this way, by forming the curved surface portion 153, the occurrence of stuffiness is prevented even if the pin 151 is press-fitted into the press-fitting hole 152.

  As shown in FIG. 1, the electric unit 5 is supplied to a stator and a rotor (not shown) that drive the orbiting scroll 9, a motor case (housing) 67 that houses the stator and the rotor, and an electric unit 5. And a box 83 for accommodating an inverter unit (not shown) for controlling the alternating current.

  Box 83 houses the inverter part inside. The box 83 opens outward in the radial direction of the motor case 67, and a plurality of screw holes (not shown) are provided on the outer peripheral surface of the motor case 67, which is the bottom surface of the box 83, for fixing the inverter part. Yes.

  The case flange portion 87 is used when the housing 13, the upper bearing case 15, and the motor case 67 are fixed integrally, and is a member that extends radially outward from the opening side end portion of the motor case 67. is there. The case flange portion 87 is formed with a screw hole into which a housing bolt 53 that integrally fixes the housing 13, the upper bearing case 15, and the motor case 67 is screwed.

Next, the configuration of the mating surface between the housing 13 and the upper bearing case 15 and the mating surface between the upper bearing case 15 and the motor case 67, which are features of the present embodiment, will be described.
FIG. 4 is a schematic diagram illustrating the configuration of the mating surface between the housing and the upper bearing case and the mating surface between the upper bearing and the motor case in FIG. 1.
On the mating surface of the housing 13 and the upper bearing case 15 and on the mating surface of the upper bearing case 15 and the motor case 67, a first shielding portion 101 and a second shielding disposed outside the first shielding portion 101 are provided. Part 102 is provided.

The first shielding unit 101 prevents the refrigerant from leaking from the inside to the outside.
The first shielding portion 101 includes an inner O-ring groove (groove) 111 </ b> A and an inner O-ring (annular elastic member) 112 </ b> A formed on a surface of the upper bearing case 15 facing the housing 13, and an upper bearing case in the motor case 67. 15 is provided with an inner O-ring groove (groove) 111B and an inner O-ring (annular elastic member) 112B formed on the surface opposite to the surface 15.

The inner O-ring grooves 111A and 111B are annular grooves, and the inner O-rings 112A and 112B are disposed therein.
The inner O-rings 112A and 112B are elastic members such as rubber formed in an annular shape, and are formed using, for example, hydrogenated nitrile butadiene rubber (HNBR) that is compatible with the lubricating oil used in the electric compressor 1. It is.

The inner O-rings 112A and 112B have a cross-sectional diameter selected so as to protrude from the inner O-ring grooves 111A and 111B when disposed in the inner O-ring grooves 111A and 111B.
Alternatively, the groove depth of the inner O-ring grooves 111A and 111B is selected so as to protrude from the inner O-ring grooves 111A and 111B when the inner O-ring grooves 112A and 112B are disposed inside.

  By doing so, when the housing 13, the upper bearing case 15 and the motor case 67 are combined together, they are pressed against the housing 13 and the upper bearing case 15, respectively, and elastically deformed. Thereby, prevention of the refrigerant | coolant leakage by the 1st shielding part 101 is achieved.

The second shielding portion 102 prevents the progress of corrosion from the outside to the inside.
The second shielding portion 102 includes an outer O-ring groove (outer groove) 121A and an outer O-ring (outer annular elastic member) 122A formed on a surface of the upper bearing case 15 facing the housing 13, and an upper in the motor case 67. An outer O-ring groove (outer groove) 121B and an outer O-ring (outer annular elastic member) 122B formed on the surface facing the bearing case 15 are provided.

  Further, the second shielding portion 102 includes a contact surface 131A and an inclined surface 132A formed on the surface of the upper bearing case 15 facing the housing 13, and a contact surface formed on the surface of the upper bearing case 15 facing the housing 13. 131B and an inclined surface 132B are provided.

The outer O-ring grooves 121A and 121B are annular grooves formed outside the inner O-ring grooves 111A and 111B, and the outer O-rings 122A and 122B are disposed inside.
The outer O-rings 122A and 122B are elastic members such as rubber formed in an annular shape like the inner O-rings 112A and 112B. For example, the outer O-rings 122A and 122B use HNBR that is compatible with the lubricating oil used in the electric compressor 1. Is formed.

  When the outer O-rings 122A and 122B are arranged in the outer O-ring grooves 121A and 121B, the cross-sectional diameter is selected so as to protrude from the outer O-ring grooves 121A and 121B. Alternatively, the groove depth of the outer O-ring grooves 121A and 121B is selected so as to protrude from the outer O-ring grooves 121A and 121B when the outer O-rings 122A and 122B are disposed inside.

  By doing so, when the housing 13, the upper bearing case 15 and the motor case 67 are combined together, they are pressed against the housing 13 and the upper bearing case 15, respectively, and elastically deformed. Thereby, the progress of corrosion toward the first shielding part 101 by the second shielding part 102 is prevented.

The contact surfaces 131 </ b> A and 131 </ b> B are flat surfaces formed outside the outer O-ring grooves 121 </ b> A and 121 </ b> B, in other words, flat surfaces parallel to the mating surfaces of the housing 13 and the motor case 67.
The inclined surfaces 132A and 132B are inclined surfaces that are formed on the outer sides of the contact surfaces 131A and 131B and have an inclination away from the inclined surfaces that face outward. Specifically, the inclined surface 132A is an inclined surface having an inclination away from the mating surface of the housing 13 facing outward, and the inclined surface 132B is separated from the mating surface of the motor case 67 facing outward. A slope having an inclination.

  As an inclination angle in the inclined surfaces 132A and 132B, for example, the distance d between the inner end and the outer end of the inclined surfaces 132A and 132B in the direction perpendicular to the mating surface (left and right direction in FIG. 4) is from about 30 μm to about 50 μm. An inclination angle falling within the range can be given.

    Thus, when the housing 13, the upper bearing case 15, and the motor case 67 are combined together, the contact surfaces 131A and 131B are annular with the mating surface of the housing 13 and the mating surface of the motor case 67, respectively. To touch.

Next, refrigerant compression in the electric compressor 1 in the present embodiment will be described.
As shown in FIG. 1, the direct current supplied from the outside of the inverter is controlled in frequency by an electronic element such as a power transistor of the inverter unit, and is supplied to the electric unit 5.
In the electric motor 5, the rotational driving force is generated based on the alternating current whose frequency is controlled. The rotational driving force generated by the electric unit 5 is transmitted to the main shaft 11.

  The rotational driving force is transmitted to the disc portion 39 of the main shaft 11, and the crank pin 41 is driven to rotate by the rotation of the disc portion 39. The orbiting motion of the crank pin 41 is transmitted to the orbiting scroll 9 through the bush 45 and the boss portion 33. The orbiting scroll 9 is driven to revolve in a state in which the rotation motion is restricted by the rotation prevention unit 23.

When the orbiting scroll 9 is driven to revolve, the compression chamber C formed between the fixed scroll 7 takes in and compresses the refrigerant flowing from the motor case 67 to the scroll compressor 3.
The refrigerant compressed in the compression chamber C is discharged to the discharge chamber through the discharge hole 29 of the fixed scroll 7 and discharged from the discharge chamber to the outside of the housing 13.

  According to the above configuration, the first shielding portion 101 prevents the refrigerant from leaking from the inside to the outside of the container constituted by the plurality of housings, and the second shielding portion 102 from the outside to the first shielding portion. The progress of corrosion toward 101 is prevented. As a result, the electric compressor 1 of the present embodiment can ensure sufficient airtightness by the first shielding part 101 even under corrosive conditions.

Specifically, the outer O-rings 122A and 122B disposed inside the outer O-ring grooves 121A and 121B as the second shielding part 102 can prevent the progress of corrosion from the outside toward the first shielding part 101. it can.
Further, since the inclined surfaces 132A and 132B are formed outside the outer O-ring grooves 121A and 121B, the contact surfaces 131A and 131B and the mating surface of the housing 13 or the mating surface of the motor case 67 are in reliable contact. become. That is, the contact surfaces 131A and 131B and the above-described mating surfaces are in annular contact outside the first shielding portion 101, so that the progress of corrosion toward the first shielding portion 101 from the outside can be prevented.

The thrust plate 141 ensures the slidability between the upper bearing case 15 and the orbiting scroll 9 and adjusts the interval between the orbiting scroll 9 and the fixed scroll 7, so The number of parts used can be reduced as compared with the case where the parts for adjusting the frequency are used separately.
Furthermore, when assembling the electric compressor 1, the number of parts to be stacked can be reduced, and the parallelism of the scroll tooth tips after assembly is improved.

FIG. 5 is a schematic diagram for explaining another embodiment of the second shielding part in FIG. 4. FIG. 6 is a schematic view for explaining still another embodiment of the second shielding part of FIG.
In addition, the 2nd shielding part 102 may have outer O ring groove 121A, 121B and outer O ring 122A, 122B, contact surface 131A, 131B, and inclined surface 132A, 132B like the above-mentioned embodiment. As shown in FIG. 5, the second shielding part 102 may have only the outer O-ring grooves 121A and 121B and the outer O-rings 122A and 122B, or as shown in FIG. 102 may have only the contact surfaces 131A and 131B and the inclined surfaces 132A and 132B, and is not particularly limited.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG.
The basic configuration of the electric compressor of the present embodiment is the same as that of the first embodiment, but the configuration of the second shielding portion is different from that of the first embodiment. Therefore, in the present embodiment, only the configuration of the second shielding part will be described using FIG. 7, and the description of the other configurations will be omitted.
FIG. 7 is a schematic diagram illustrating the configuration of the second shielding unit according to the present embodiment.
In addition, the same code | symbol is attached | subjected about the component same as 1st Embodiment, and the description is abbreviate | omitted.

  On the mating surface of the housing 13 and the upper bearing case 15 and the mating surface of the upper bearing case 15 and the motor case 67 in the electric compressor (electric compressor for vehicle air conditioning) 201, A second shielding part 202 disposed outside the first shielding part 101 is provided.

The second shielding part 202 prevents the progress of corrosion from the outside to the inside.
The second shielding portion 202 is provided with a gasket 221 disposed in an outer region of the inner O-ring grooves 111A and 111B.

  The gasket 221 is a liquid member and is a region outside the inner O-ring groove 111A, a mating surface of the housing 13 or the upper bearing case 15, and a region outside the inner O-ring groove 111B. Thus, the one applied to the mating surface of the upper bearing case 15 or the motor case 67 can be exemplified.

  The gasket 221 may be a liquid member as described above, or may be one in which an elastic member such as rubber is provided on both surfaces of a plate member formed in a ring plate shape, and is particularly limited. Not what you want.

  As described above, by disposing the gasket 221 outside the first shielding part 101, it is possible to prevent the progress of corrosion from the outside to the inside.

  According to the above configuration, the first shielding portion is externally provided by the gasket disposed on the mating surface between the housing 13 and the upper bearing case 15 and the mating surface between the upper bearing case 15 and the motor case 67. It is possible to prevent the progress of corrosion toward the surface.

It is sectional drawing explaining the outline of a structure of the electric compressor which concerns on the 1st Embodiment of this invention. It is a schematic diagram explaining the structure of the thrust plate of FIG. It is a schematic diagram explaining the state by which the pin used for the rotation stop of the thrust plate of FIG. 2 was press-fit in the upper bearing case. FIG. 2 is a schematic diagram illustrating a configuration of a mating surface between a housing and an upper bearing case and a mating surface between an upper bearing and a motor case in FIG. 1. It is a schematic diagram explaining another embodiment of the 2nd shielding part of FIG. It is a schematic diagram explaining another embodiment of the 2nd shielding part of FIG. It is a schematic diagram explaining the structure of the 2nd shielding part which concerns on the 2nd Embodiment of this invention.

Explanation of symbols

1,201 Electric compressor (electric compressor for vehicle air conditioning)
3 Scroll compression part (compression part)
7 Fixed scroll 9 Orbiting scroll 13 Housing (housing, compression housing)
15 Upper bearing case (housing, intermediate housing)
141 Thrust plate (plate part)
67 Motor case (housing)
101 1st shielding part 102,202 2nd shielding part 111A, 111B Inner side O-ring groove (groove)
112A, 112B Inner O-ring (annular elastic member)
121A, 121B Outer O-ring groove (outer groove)
122A, 122B Outer O-ring (outer annular elastic member)
131A, 131B Contact surface 132A, 132B Inclined surface 221 Gasket

Claims (6)

A plurality of housings constituting a container that houses a compression unit that compresses the refrigerant therein;
A first shielding portion having an annular groove formed on one mating surface of the plurality of housings, and an annular elastic member disposed inside the groove;
A second shielding portion annularly disposed in a region outside the first shielding portion on the one mating surface or the other mating surface;
An electric compressor for vehicle air conditioning is provided.   The second shielding portion includes an outer groove formed in a region outside the groove on the one or other mating surfaces, and an outer annular elastic member disposed inside the outer groove. The electric compressor for vehicle air conditioning according to claim 1 characterized by the above-mentioned.   The second shielding portion is disposed in a region further outside the outer groove on the one or other mating surfaces, and contacts a surface that contacts the one or other mating surfaces facing each other, and faces outward from the contact surface. The vehicle air conditioning electric compressor according to claim 2, further comprising an inclined surface that is separated from the facing one or other mating surfaces.   The second shielding portion is disposed in a region outside the groove on the one or other mating surfaces, and contacts the one or other mating surfaces facing each other, and outward from the contact surfaces, The vehicular air-conditioning electric compressor according to claim 1, further comprising an inclined surface separated from one or the other facing surfaces.   2. The electric compressor for vehicle air conditioning according to claim 1, wherein the second shielding portion is a gasket disposed between the one and another mating surfaces and in an area outside the groove. The plurality of housings include at least a compression unit housing and an intermediate housing that form a space in which the compression unit is housed.
The compression unit includes a fixed scroll fixed to the compression unit housing, and a turning scroll that compresses the refrigerant by revolving around the fixed scroll.
The plate part which adjusts the space | interval between the said fixed scroll and the said turning scroll while ensuring the slidability between the said turning scroll and the said intermediate | middle housing | casing is provided. To 5. The electric compressor for vehicle air conditioning according to any one of 5 to 5.

Images