JP4606272B2 - Cooling system electric compressor - Google Patents

Description

  The present invention relates to an electric compressor of a cooling system for air conditioning of a vehicle, for example, and more particularly to an electric compressor suitable for a cooling system using carbon dioxide gas as a refrigerant.

  In view of the recent environmental situation, when the cooling system is used for air conditioning of a vehicle, the refrigerant is preferably a natural refrigerant such as carbon dioxide gas as compared with the refrigerant such as R134a. However, since the thermal insulation index of carbon dioxide gas is higher than that of R134a, when the refrigerant compressed in the compressor, that is, the compression unit is discharged into the discharge chamber, the discharge temperature and discharge pressure of the compressed refrigerant are Also, carbon dioxide gas is higher than R134a.

With respect to a reciprocating compressor in which the refrigerant suction chamber is disposed adjacent to the discharge chamber, a heat insulating space is secured between the discharge chamber and the suction chamber, and cooling fins are provided on the outer surface of the wall defining the discharge chamber. A compressor provided is known (for example, Patent Document 1). The compressor of Patent Document 1 is considered to be able to achieve a decrease in the discharge temperature by the cooling fins while suppressing the increase in the temperature of the suction refrigerant due to the increase in the discharge temperature by the heat insulating space.
JP 2004-183534 A

However, since the cooling fin of patent document 1 exhibits only the function of only radiating heat toward the periphery of the compressor, the discharge temperature of the refrigerant cannot be lowered sufficiently. For this reason, it is conceivable that the sealing member for ensuring the airtightness of the discharge chamber and the lubricating oil contained in the refrigerant and used for lubricating the compression unit are deteriorated at an early stage.
Further, when an electric motor is used as a drive source for the compressor, an increase in the discharge pressure of the refrigerant increases a load applied to the output shaft of the electric motor, so that the amount of heat generated from the electric motor also increases.

However, the cooling fin of Patent Document 1 does not function at all for suppressing the heat generation of the electric motor, and deteriorates the insulating material and insulating correlation paper of the stator winding included in the electric motor at an early stage. In addition, those having excellent heat resistance are required.
On the other hand, it is also conceivable to introduce a part of the suction refrigerant into the casing of the electric motor to suppress the heat generation of the electric motor. However, since the inside of the casing is occupied by the core of the electric motor, the stator, the stator winding, and the like, it is difficult to secure a sufficient flow path for the suction refrigerant in the casing.

Furthermore, since the increase in the discharge pressure also increases the noise from the compression unit, a noise countermeasure is also desired for a compressor that uses carbon dioxide gas as the refrigerant.
The present invention has been made on the basis of the above-mentioned circumstances, and its object is to suppress the discharge temperature rise of the compressed discharge refrigerant and the heat generation of the electric motor, and further reduce the noise from the compression unit. An object of the present invention is to provide an electric compressor for a cooling system.

  In order to achieve the above object, an electric compressor of a cooling system of the present invention includes a hermetically sealed housing, an electric motor that is accommodated in the hermetic housing leaving a surrounding space, and has a rotor and a stator, and an electric motor in the hermetic housing. Adjacent, driven by an electric motor, sucks and compresses the recirculated refrigerant from the cooling system, compresses this compressed refrigerant to the cooling system via the discharge chamber, and is secured in the sealed housing and compressed A suction space for allowing the unit to suck the refrigerant, an adjacent space that is secured in the hermetic housing and is disposed adjacent to at least a part of the wall defining the discharge chamber of the compression unit from the outside, and the suction space, the adjacent space, and the surrounding space. The spaces are connected to each other, provided in a sealed pipe and a connecting pipe line having a smaller channel cross-sectional area than the representative channel cross-sectional area of each space, ON space, and a introduction port for guiding a reflux coolant to one of the adjacent space and enclosed space (Claim 1).

According to the electric compressor of claim 1 described above, the reflux refrigerant from the cooling system is introduced into any one of the suction space, the adjacent space, and the surrounding space through the introduction port, and thereafter, the other space is introduced into the other space from the introduction space. Two flows into the space. Therefore, the reflux refrigerant is supplied to the suction space, the adjacent space, and the surrounding space, respectively.
Since the adjacent space is adjacent to the discharge chamber, the recirculation refrigerant in the adjacent space exchanges heat with the compressed refrigerant in the discharge chamber, that is, the discharge refrigerant, so that the temperature of the discharge refrigerant decreases.

Since the adjacent space is fluidly connected to the suction space, the temperature of the reflux refrigerant sucked into the compression unit from the suction space, that is, the temperature of the suction refrigerant rises. Therefore, the recirculation refrigerant supplied to the surrounding space cools the electric motor.
Each connecting pipe has a flow passage cross-sectional area smaller than the representative cross-sectional area of each of the above-described spaces, and fluidly connects the adjacent space, the surrounding space and the suction space to each other. It functions and reduces the noise transmitted from the suction chamber with the suction of the compression unit, specifically the reflux refrigerant.

Specifically, the connection pipe line connects the suction space, the adjacent space, and the surrounding space in series, and the introduction port is connected to the adjacent space (Claim 2). In this case, since the recirculation refrigerant from the cooling system is first introduced into the adjacent space through the introduction port, the recirculation refrigerant in the adjacent space can effectively cool the discharge refrigerant in the discharge chamber.
Further, the suction space is disposed downstream of the surrounding space (Claim 3), or is disposed between the adjacent space and the surrounding space (Claim 4).

Further, it is preferable that at least one of the adjacent space and the suction space is formed as a resonance silencer.
The compression unit is a scroll-type compression unit having fixed and movable scrolls (Claim 6) or a piston-type compression unit (Claim 7).
In any type of compression unit, carbon dioxide gas can be used as the refrigerant (claim 8).

  The electric compressor of the cooling system according to any one of claims 1 to 6 performs heat exchange between the reflux refrigerant in the adjacent space and the discharge refrigerant in the discharge chamber, and between the reflux refrigerant and the electric motor in the surrounding space. Since this is done, the discharge temperature of the compressed refrigerant decreases. As a result, the deterioration of the lubricating oil in the discharge chamber sealing member and the compressed refrigerant is suppressed, and the reliability of the electric compressor is improved. Furthermore, since the stator windings and the like of the electric motor are cooled by the reflux refrigerant in the surrounding space, the heat generation of the electric motor can be effectively suppressed, which greatly contributes to the improvement of the reliability of the electric compressor. In addition, the connection pipe line that connects the three spaces of the adjacent space, the suction space, and the surrounding space functions as a silencer, so that noise transmitted from the suction chamber can be effectively reduced. Can do.

In the electric compressor according to claim 2, since the reflux refrigerant from the cooling system is first introduced into the adjacent space, heat exchange is performed between the discharge refrigerant having the highest temperature and the reflux refrigerant having the lowest temperature. The temperature of the refrigerant can be reduced more effectively.
In the electric compressor according to claim 3, since the suction space is arranged downstream of the surrounding space, the recirculation refrigerant in the surrounding space exchanges heat with the stator winding of the electric motor while the temperature is relatively low. Therefore, the temperature of the electric motor can be further reduced.

In the electric compressor according to the fourth aspect, since the suction chamber is disposed between the adjacent space and the surrounding space, the adjacent space and the suction space can be disposed adjacent to each other, and the sound deadening function can be further enhanced. .
In the electric compressor according to the fifth aspect, since one of the adjacent space and the surrounding space forms a resonance silencer, noise having a specific frequency among noises of the compression unit can be effectively reduced.

Referring to FIG. 1, the electric compressor of the cooling system according to the first embodiment includes a cylindrical hermetic housing 10. The hermetic housing 10 has a partition wall 12 inside, and the partition wall 12 partitions the inside of the hermetic housing 10 into an electric motor chamber 14 and a compression unit chamber 16.
An electric motor 18 is accommodated in the electric motor chamber 14, and the electric motor 18 has a rotor 22 attached to the drive shaft 20 and a stator 24 surrounding the rotor 22. The stator 24 has a stator winding 26 and insulating correlation paper. (Not shown).

In the illustrated embodiment, the stator 24 is supported on the inner peripheral wall of the hermetic housing 10 via a disk-shaped stator holder 28, and the stator holder 28 has a plurality of through holes 30 at intervals in the circumferential direction.
The drive shaft 20 of the electric motor 18 has a large-diameter end 32 at one end on the partition wall 12 side, and the large-diameter end 32 is rotatably supported by the partition wall 12 via a bearing 34. A crankpin 36 protrudes from the large diameter end portion 32 into the compression unit chamber 16, and the crankpin 36 is connected to the compression unit 38.

  In the case of this embodiment, the compression unit 38 is a scroll type compression unit having a movable scroll 40 and a fixed scroll 42 that mesh with each other. (Not shown). The movable and fixed scrolls 40 and 42 have spiral walls that mesh with each other, and a compression chamber is formed between the spiral walls. The spiral wall is formed integrally with the end plate of the corresponding scroll.

  When the rotor 22 of the electric motor 18, that is, the drive shaft 20 thereof is rotated, the crankpin 36 imparts a rotational motion to the movable scroll 40, whereby the movable scroll 40 is prevented from rotating and the fixed scroll. Rotate with respect to 42. The orbiting motion of the movable scroll 40 moves the compression chamber formed on the outer peripheral side of the movable scroll 40 toward the center, and the volume of the compression chamber decreases with this movement. The turning radius of the movable scroll 40 is determined by the distance between the axes between the axis of the drive shaft 20 and the axis of the crankpin 36.

  A cylindrical discharge head 44 having pressure resistance is disposed between the end plate of the fixed scroll 42 and the end wall 16 a of the compression unit chamber 16. The discharge head 44 fixes the fixed scroll 42 to the hermetic housing 10. It is used to A discharge chamber 46 is formed in the discharge head 44, and the discharge chamber 46 is hermetically sealed through a seal member 48. That is, the seal member 48 is disposed between the discharge head 44 and the fixed scroll 42 and between the discharge head 44 and the end wall 16 a of the compression unit chamber 16.

A discharge hole (not shown) is formed in the center of the end plate of the fixed scroll 42, and this discharge hole is opened and closed by a discharge valve (not shown). The discharge valve has a reed valve body and is disposed on the outer surface of the end plate of the fixed scroll 42 on the discharge chamber 46 side.
On the other hand, the discharge chamber 46 is connected to the cooling system, that is, the refrigerant circulation path via the discharge port 50, and the discharge port 50 is formed through the discharge head 44 and the end wall 16 a of the compression unit chamber 16.

In this embodiment, the cooling system is used for air conditioning of a vehicle, and the refrigerant circulation path is filled with a carbon dioxide gas refrigerant, while the refrigerant circulation path includes a gas cooler, an expansion valve, and an evaporator. Various devices such as these are inserted, and these devices constitute a cooling system together with the electric compressor.
In this embodiment, the refrigerant contains lubricating oil, and this lubricating oil is used for lubricating various sliding surfaces in the electric motor 18 and the compression unit 38 and for sealing the compression chamber in the compression unit 38. The

On the other hand, an introduction port 52 made of a pipe is provided through the end wall 16a of the compression unit chamber 16, and the outer end of the introduction port 52 is connected to the refrigerant circulation path of the cooling system. Thus, the inlet port 52 can receive the reflux refrigerant returning from the evaporator of the cooling system.
An introduction hood 56 is connected to the inner end of the introduction port 52. The introduction hood 56 is disposed in the compression unit chamber 16 so as to cover a part or the whole of the outer peripheral surface of the discharge head 44, and the inside thereof is formed as an adjacent space 58 adjacent to the discharge chamber 46. Specifically, the introduction hood 56 has a shape that covers a part of the outer peripheral surface of the discharge head 44 as viewed in the circumferential direction of the discharge head 44, and the adjacent space 58 is in contact with only the outer peripheral surface of the discharge head 44. ing. When viewed in the axial direction of the ejection head 44, the introduction hood 56 extends over the entire axial length of the ejection head 44.

A connecting pipe 60 extends from the introduction hood 56 toward the partition wall 12, and a tip of the connecting pipe 60 penetrates the partition wall 12 and faces the motor chamber 14.
On the other hand, a connecting pipe 62 different from the connecting pipe 60 is provided through the partition wall 12, and the connecting pipe 62 is disposed away from the connecting pipe 60 in the diameter direction of the electric motor 18. A suction hood 64 is connected to the end of the connection pipe 62 located in the compression unit chamber 16, and the suction hood 64 is disposed outside the compression unit 38.

  More specifically, the suction hood 64 covers a part of the outer peripheral surface of the compression unit 38 when viewed in the circumferential direction of the compression unit 38, and the suction hood 64 is viewed in the axial direction of the compression unit 38 when viewed in the axial direction of the compression unit 38. It extends over the entire length. The inside of the suction hood 64 forms a suction space 66 for the compression unit 38, and a compression chamber formed on the outer peripheral side of the compression unit 38 is opened, that is, connected to the suction space 66.

As apparent from FIG. 1, the flow passage cross-sectional areas of the connecting pipes 60 and 62 are smaller than the representative cross-sectional areas of the adjacent space 58, the motor chamber 14 (that is, the surrounding space surrounding the motor 18), and the suction space 66. Here, the representative cross-sectional area represents an effective average flow path cross-sectional area when the space is viewed in a cross section transverse to the axial direction of the sealed housing 10.
As described above, if the introduction hood 56 and the connecting pipe 60 are sequentially connected to the introduction port 52, the reflux refrigerant from the cooling system passes through the adjacent space 58 in the introduction hood 56 as shown by the arrow in FIG. It flows into the motor chamber 14 and then flows into the suction hood 64, that is, into the suction space 66 from the motor chamber 14 through the connection pipe 62.

  According to the electric compressor of the first embodiment described above, when the motor 18 is driven and the movable scroll 40 of the compression unit 38 rotates, the compression unit 38 sucks the recirculated refrigerant in the suction space 66 into the compression chamber. Thereafter, the compression chamber moves toward the discharge port of the fixed scroll 42. In this moving process, the volume of the compression chamber is gradually reduced, so that the refrigerant in the compression chamber is compressed.

  When the compression chamber reaches the discharge port and the pressure of the compressed refrigerant overcomes the shutoff pressure of the discharge valve, the discharge valve is opened. At the time of this valve opening, the compressed refrigerant is discharged from the compression chamber to the discharge chamber 46 through the discharge port, and is sent from the discharge chamber 46 to the cooling system through the discharge port 50. The discharged refrigerant sent to the cooling system is used for cooling the ambient air in the evaporator, and then returned to the introduction port 52 of the compressor. That is, the refrigerant circulates in the cooling system, that is, the refrigerant circulation path through the compressor.

  Since the refrigerant compressed by the compressor is carbon dioxide gas as described above, the temperature and pressure of the compressed refrigerant discharged into the discharge chamber 46 are both higher than when the refrigerant is R134a. However, since the reflux refrigerant introduced from the introduction port 52 is first introduced into the introduction hood 56, that is, the adjacent space 58 adjacent to the discharge chamber 46, the reflux refrigerant in the adjacent space 58 passes through the discharge head 44 through the discharge chamber 44. Heat is received from the discharged refrigerant in 46. Such heat exchange with the discharged refrigerant lowers the temperature of the discharged refrigerant.

  Thereafter, the reflux refrigerant in the adjacent space 58 flows into the motor chamber 14, but the temperature of the reflux refrigerant is lower than the heat generation temperature of the electric motor 18 in the steady drive state even if the temperature of the reflux refrigerant rises due to the heat exchange described above. Therefore, the reflux refrigerant in the motor chamber 14 functions sufficiently as a refrigerant for the motor 18, that is, heat exchange is performed with the motor 18, and the winding insulation material of the motor 18, insulation correlation paper, etc. are effective. Cool. As a result, deterioration of the winding insulating material, the insulating correlation paper, etc. can be suppressed, and the operational reliability of the electric motor 18 can be improved.

Moreover, as a result of guaranteeing effective cooling of the electric motor 18, it becomes possible to lower the heat resistance grade of the stator winding, and an inexpensive stator winding can be used for the electric motor 18, which greatly contributes to the cost reduction of the electric motor 18. To do.
The reflux refrigerant used for cooling the motor 18 in the motor chamber 14 then flows into the suction hood 64, that is, the suction space 66 through the connection pipe 62, and, as described above, from the suction space 66 to the compression unit 38. Inhaled into the compression chamber.

As described above, the refrigerant sucked into the compression chamber exchanges heat not only in the adjacent space 58 but also in the electric motor chamber 14, so that the discharge temperature of the compressed refrigerant can be lowered.
As a result, both the seal member 48 that ensures the airtightness of the discharge chamber 46 and the deterioration of the lubricating oil contained in the refrigerant are suppressed, which also improves the operational reliability of the compressor.
Further, the connecting pipe 60 that connects the adjacent space 58 and the motor chamber 14 and the connecting pipe 62 that connects the motor chamber 14 and the suction space 66 have the flow path cross-sectional area of the adjacent space 58, the motor chamber 14, and Since it is smaller than the representative sectional area of the suction space 66, these connection pipes 60 and 62 constitute a silencer together with the adjacent space 58, the motor chamber 14, and the suction space 66.

Therefore, the noise propagating from the compression unit 38 toward the suction space 66 is silenced step by step in the process of being propagated from the suction space 66 to the adjacent space 58 through the motor chamber 14, greatly reducing the noise of the compression unit 38. it can.
Further, since the adjacent space 58, the motor chamber 14, the suction space 66, and the connecting pipes 60 and 62 are all disposed in the sealed housing 10, even if the refrigerant leaks from the adjacent space 58 or the suction space 66, the refrigerant Is not discharged outside the sealed housing 10, that is, outside the cooling system, and the above-described spaces and connecting pipes can be easily arranged.

  The present invention is not limited to the first embodiment described above, and various modifications are possible. The electric compressors according to the second to fourth embodiments will be described below. In the description of the electric compressors of the second to fourth embodiments, in order to avoid duplication of explanation, the members and parts that exhibit the same functions as the members and parts of the electric compressor of the first embodiment are the same. The description is omitted.

FIG. 2 shows an electric compressor of the second embodiment.
In the case of the electric compressor of FIG. 2, the suction hood 64 is disposed adjacent to the introduction hood 56, and these hoods 56, 64 are connected to each other by a connecting pipe 68. The suction hood 64 and the motor chamber 14 are connected via a connection pipe 70. Specifically, the introduction hood 56, the suction hood 64, and the electric motor chamber 14 are arranged on a straight line along the axis of the hermetic housing 10. Needless to say, the cross-sectional areas of the connecting pipes 68 and 70 are smaller than the representative cross-sectional areas of the adjacent space 58, the motor chamber 14, and the suction space 66.

According to the electric compressor of the second embodiment described above, the reflux refrigerant introduced into the adjacent space 58 of the introduction hood 56 exchanges heat with the discharge refrigerant, and then enters the suction hood 64 via the connection pipe 68. That is, it flows into the suction space 66. A part of the reflux refrigerant in the suction space 66 is sucked into the compression chamber of the compression unit 38 and flows into the motor chamber 14 through the connection pipe 70.
Also in the case of the electric compressor of the second embodiment, the reflux refrigerant in the suction space 66, that is, the suction refrigerant exchanges heat with the discharge refrigerant in the adjacent space 58, so that the temperature of the discharge refrigerant decreases. Also in this case, it goes without saying that the reflux refrigerant in the motor chamber 14 can sufficiently cool the motor 18.

Therefore, the electric compressor of the second embodiment exhibits the same advantages as those of the first embodiment. Further, in the case of the second embodiment, the adjacent space 58, the suction space 66, and the motor chamber 14 are arranged adjacent to each other as compared with the case of the first embodiment, so that the function as a silencer is more effective. The noise from the compression unit 38 can be further reduced.
FIG. 2 also shows the electric compressor of the third embodiment.

In the case of the third embodiment, at least one of the adjacent space 58 and the motor chamber 14 is formed as a resonance silencer.
In addition to the advantages of the first and second embodiments, the electric compressor of the third embodiment can effectively attenuate noise of a predetermined wavelength among noises generated from the compression unit 38. Low noise can be achieved.

In the electric compressor of the third embodiment, the motor chamber 14 may be formed as a resonance chamber, or both the motor chamber 14 and the adjacent space 58 are formed as resonance chambers. In the space 58, noises having different wavelengths can be selectively attenuated.
FIG. 3 shows an electric compressor of the fourth embodiment.
The electric compressor of FIG. 3 includes a piston-type compression unit 72 instead of the scroll-type compression unit 38, and the compression unit 72 includes a cylinder block 74, a valve plate 76, and a cylinder head 78. A plurality of cylinder bores 80 are formed in the cylinder block 74, and pistons 82 are fitted in the cylinder bores 80. The tail 84 of the piston 82 is connected to a swash plate 86 via a pair of shoes (not shown), and the swash plate 86 is rotated by the drive shaft 20 of the electric motor 18. The rotational movement of the swash plate 86 is converted into the reciprocating movement of the piston 82, whereby the volume of the compression chamber in the cylinder bore 80 is increased or decreased.

On the other hand, the cylinder head 78 is formed with a suction chamber 88 as a suction space at the center thereof, and an annular discharge chamber 90 is formed so as to surround the suction chamber 88.
The valve plate 76 is formed with a suction hole 92 and a discharge hole 94 for each compression chamber. The suction hole 92 and the discharge valve 94 can be connected to the suction chamber 88 and the discharge chamber 90 via a suction valve and a discharge valve (both not shown).

An introduction hood 56 is disposed on the outer peripheral surface of the cylinder head 78, and a connection pipe 60 extending from the introduction hood 56 is connected to the motor chamber 14. On the other hand, the connecting pipe 62 extending from the motor chamber 14 is connected to the suction chamber 88 through the cylinder head 78.
Therefore, as in the case of the electric compressor of the first embodiment, the reflux refrigerant from the cooling system is once introduced into the adjacent space 56 from the introduction port 52 and then from the adjacent space 56 through the connecting pipe 60 to the electric motor chamber 14. And can flow into the suction chamber 88 from the motor chamber 14 through the connecting pipe 62.

Therefore, when the compression unit 72 is driven, the reflux refrigerant is sucked into each compression chamber from the suction chamber 88 through the suction hole 92 and the suction valve, and the suction refrigerant is compressed after being compressed in the compression chamber. The ink is discharged from the chamber into the discharge chamber 90 through the discharge hole 94 and the discharge valve.
Even in the piston-type compression unit 72 described above, since the adjacent space 56 is disposed adjacent to the discharge chamber 90, the reflux refrigerant in the adjacent space 56 is heated between the discharge refrigerant in the discharge chamber 90. Exchange can be performed, and the reflux refrigerant flowing into the motor chamber 14 can be used to cool the motor 18. Furthermore, since the adjacent space 56, the electric motor chamber 14, and the suction chamber 88 are connected via the connecting pipes 60 and 62, they also function as a silencer. Therefore, the electric compressor of the fourth embodiment also has the same advantages as those of the first and second embodiments.

  Further, in the case of the second to fourth embodiments described above, the adjacent space, the motor room (enclosed space), and the suction space are all connected in series via a connecting pipe. The other two spaces may be connected in parallel to the space connected to the introduction port. Moreover, the connection pipe can be replaced with a connection passage, and the space connected to the introduction port is not limited to the adjacent space, but may be an enclosed space or a suction space.

  Needless to say, the present invention can be similarly applied to other types of electric compressors such as a swing type and a vane type.

It is the schematic sectional drawing which showed the electric compressor of 1st Example. It is the schematic sectional drawing which showed collectively the electric compressor of 2nd and 3rd Example. It is the schematic sectional drawing which showed the electric compressor of 4th Example.

Explanation of symbols

10 Sealed housing 14 Motor room (go space)
18 Electric motor 22 Rotor 24 Stator 38, 72 Compression unit 46, 90 Discharge chamber 52 Introduction port 58 Adjacent space 60, 62 Connection pipe (connection pipe)
66 Suction space 68, 70 Connection pipe (connection pipe)
88 Suction chamber (suction space)

Claims (8)

A sealed housing;
An electric motor housed in the sealed housing leaving a surrounding space and having a rotor and a stator;
A compression unit that is disposed adjacent to the electric motor in the hermetic housing, is driven by the electric motor, sucks and compresses the recirculated refrigerant from the cooling system, and sends the compressed refrigerant to the cooling system through the discharge chamber. When,
A suction space secured in the sealed housing and allowing the compression unit to suck refrigerant;
An adjacent space that is secured in the hermetic housing and is disposed adjacent to at least a part of a wall defining the discharge chamber of the compression unit from the outside;
A connecting pipe line that connects the suction space, the adjacent space, and the surrounding space with each other, and has a channel cross-sectional area smaller than a representative channel cross-sectional area of each space;
An electric compressor for a cooling system, comprising: an inlet port that is provided in the hermetic housing and guides the reflux refrigerant to one of the suction space, the adjacent space, and the surrounding space.   2. The cooling system according to claim 1, wherein the connection pipe connects the suction space, the adjacent space, and the surrounding space in series, and the introduction port is connected to the adjacent space. Compressor.   The electric compressor of the cooling system according to claim 2, wherein the suction space is disposed downstream of the surrounding space.   The electric compressor of the cooling system according to claim 2, wherein the suction space is disposed between the adjacent space and the surrounding space.   5. The electric compressor for a cooling system according to claim 3, wherein at least one of the adjacent space and the surrounding space is formed as a resonance silencer. 6.   The electric compressor of the cooling system according to claim 2, wherein the compression unit is a scroll type compression unit including a fixed and a movable scroll.   The electric compressor of the cooling system according to claim 2, wherein the compression unit is a piston-type compression unit.   The electric compressor of the cooling system according to claim 2, wherein the refrigerant is carbon dioxide gas.

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