WO2015005090A1

WO2015005090A1 - Gas-tight terminal fixing structure for gas compressor

Info

Publication number: WO2015005090A1
Application number: PCT/JP2014/066297
Authority: WO
Inventors: 勝義河内
Original assignee: カルソニックカンセイ株式会社
Priority date: 2013-07-08
Filing date: 2014-06-19
Publication date: 2015-01-15
Also published as: JP2015015215A

Abstract

Provided is a gas-tight terminal holding structure for a gas compressor with which a retaining ring for fixing a gas-tight terminal can be assembled with good workability, and with which it is possible to increase the force for holding, by the retaining ring, the vicinity of the central section on the long sides of the gas-tight terminal. A retaining ring (60) comprises: a pair of arm parts (60a, 60b) extending in straight lines so as to oppose one another; and an elastically deformable curved part (60c) that has a narrower width than the width of the arm part (60a, 60b). The outer periphery side of the retaining ring (60) is engaged in an inner periphery groove part (6c) in an attachment opening (6a) in a state where the curved part (60c) of the retaining ring (60) is elastically deformed and the arm parts (60a, 60b) are displaced inwardly; the curved part (60c) of the retaining ring (60) holds a short side part (51b) on one side of the gas-tight terminal (50); and the arm parts (60a, 60b) hold respective straight-line-shaped long side parts (51a) of the gas-tight terminal (50) that oppose one another.

Description

Air compressor terminal fixing structure of gas compressor

The present invention relates to an airtight terminal fixing structure of a gas compressor driven by an electric motor.

For example, a vehicle such as an automobile is provided with an air conditioner for adjusting the temperature in the passenger compartment. Such an air conditioner has a loop-like refrigerant cycle in which refrigerant (cooling medium) is circulated, and this refrigerant cycle is provided with an evaporator, a gas compressor, a condenser, and an expansion valve in this order. ing. The gas compressor of the air conditioner compresses the gaseous refrigerant (refrigerant gas) evaporated by the evaporator into a high-pressure refrigerant gas and sends it to the condenser.

By the way, a gas compressor of a vehicle air conditioner generally obtains a driving force from an internal combustion engine (engine) via an electromagnetic clutch, but is integrated in an EV (electric vehicle), a hybrid vehicle, or the like. The driving force is obtained from the electric motor.

In a gas compressor having an electric motor, a compression mechanism section (compressor section) and an electric motor are provided in a housing. The electric motor has an inverter section for controlling the rotation speed of the electric motor, and an airtight terminal. (See, for example, Patent Document 1).

The airtight terminal is fixed to the inner wall surface of the mounting opening formed in the housing by two C-shaped retaining rings so as not to come off.

JP 2007-128756 A

By the way, in Patent Document 1, since two C-shaped retaining rings are required to fix one airtight terminal, it is necessary to perform assembly work of the retaining rings twice, and workability is poor.

Moreover, the pressure of the refrigerant gas supplied into the housing is applied to the surface of the airtight terminal on the electric motor side. For this reason, as in Patent Document 1, in the structure in which the short side of the curved surface facing the hermetic terminal is fixed with a C-shaped retaining ring, the retaining ring holds the vicinity of the center of the long side of the hermetic terminal. Power is weak.

Therefore, the present invention has been made in view of the above circumstances, can be assembled with a retaining ring for fixing the hermetic terminal with good workability, and holding force near the center of the long side of the hermetic terminal by the retaining ring. An object is to provide an airtight terminal fixing structure of a gas compressor that can be improved.

In order to solve the above problems, the invention according to claim 1 drives a compression mechanism unit that compresses a medium supplied from the outside into a housing and discharges a high-pressure medium to the outside, and drives the compression mechanism unit. A gas compressor comprising: an electric motor; a motor control unit that controls driving of the electric motor; and an airtight terminal that is disposed in the mounting opening and electrically connects the electric motor and the motor control unit. The airtight terminal includes a flat terminal body formed by a pair of opposing linear long sides and curved short sides continuous from both ends of the long sides, and the terminal body And a retaining ring in a concave groove formed on the inner wall surface of the mounting opening with respect to the airtight terminal disposed on the protruding portion formed in the mounting opening. Engaging the outer peripheral side of the A gas compressor hermetic terminal holding structure for holding the hermetic terminal in the mounting opening, wherein the retaining ring connects a pair of linearly extending arm portions and one end of each of the arm portions. And a bending portion that is narrower than the width of the arm portion and elastically deformable, and elastically deforms the bending portion of the retaining ring to displace the arm portions inwardly. In this state, the outer peripheral side of the retaining ring is engaged with the groove portion, the short side portion on one side of the airtight terminal is held by the curved portion, and each length of the airtight terminal is held by each arm portion. It is characterized by holding the sides.

The invention according to claim 2 is characterized in that the curved portion of the retaining ring is formed narrower than the width of the arm portion over the entire outer peripheral surface thereof.

The invention according to claim 3 is characterized in that a jig insertion part into which a jig for displacing each arm part inward is formed in each arm part of the retaining ring. .

According to a fourth aspect of the present invention, the jig insertion portion is located on a side opposite to the curved portion with respect to the intermediate portion of each arm portion, and the outer periphery side of the retaining ring is engaged with the groove portion. It is characterized by being formed at a position where it does not interfere with the terminal.

According to the hermetic terminal holding structure of the gas compressor according to the present invention, the hermetic terminal can be easily held (fixed) in the mounting opening by one assembling operation using one retaining ring. Therefore, the work time is shortened and workability can be improved as compared with the assembly work of fixing the airtight terminal using two C-shaped retaining rings as in the prior art.

In addition, when two C-shaped retaining rings are used as in the prior art, the long side of the hermetic terminal is used to fix the curved short side of the hermetic terminal with the two C-shaped retaining rings. The holding force near the center is weak, and there is a possibility that a sealing failure may occur due to the pressure of the refrigerant supplied (intake) into the housing. The holding force can be improved by securely holding the entire straight long side.

1 is a longitudinal sectional view showing a gas compressor (vane rotary type gas compressor) according to an embodiment of the present invention. FIG. 2 is a sectional view taken along line AA in FIG. 1. The perspective view which shows the retaining ring in embodiment of this invention. The top view which shows the airtight terminal holding structure in embodiment of this invention. The figure which shows the retaining ring in embodiment of this invention.

Hereinafter, the present invention will be described based on the illustrated embodiment. FIG. 1 is a longitudinal sectional view showing a vane rotary type gas compressor (hereinafter referred to as “compressor”) as a gas compressor according to an embodiment of the present invention, and FIG. 2 is taken along line AA in FIG. FIG. In addition, the compressor of this embodiment is an electric compressor incorporating an electric motor.

(Overall configuration and operation of compressor)
The illustrated compressor 1 is configured as a part of an air conditioning system (hereinafter referred to as an “air conditioning system”) that performs cooling by using the heat of vaporization of a cooling medium, for example, and is a condensing component that is another component of the air conditioning system It is provided on the circulation path of the cooling medium together with a condenser, an expansion valve, an evaporator, etc. (all not shown). In addition, as such an air conditioning system, the air conditioning apparatus for adjusting the temperature in the vehicle interior of a vehicle (automobile etc.) is mentioned, for example.

The compressor 1 compresses a refrigerant gas as a gaseous cooling medium taken from the evaporator of the air conditioning system, and supplies the compressed refrigerant gas to the condenser of the air conditioning system. The condenser liquefies the compressed refrigerant gas and sends it to the expansion valve as a high-pressure liquid refrigerant. The high-pressure and liquid refrigerant is reduced in pressure by the expansion valve and sent to the evaporator. The low-pressure liquid refrigerant absorbs heat from ambient air and vaporizes in the evaporator, and cools the air around the evaporator by heat exchange with the heat of vaporization.

As shown in FIG. 1, the compressor 1 includes a housing 4 in which an electric motor 2 and a compression mechanism 3 are housed, and an inverter case 6 in which an inverter unit 5 serving as a motor control unit is housed with a plurality of bolts (not shown). Are joined and integrated. The housing 4 and the inverter case 6 are partitioned by a partition 7 so that the refrigerant gas sucked (supplied) into the housing 4 does not leak into the inverter case 6. The compression mechanism 3 is fixed in the housing 4 by a plurality of bolts 8.

The suction chamber 9 on the side of the electric motor 2 in the housing 4 is formed with a suction port (not shown) for introducing a low-pressure refrigerant gas into the suction chamber 9 from an evaporator (not shown) of the air conditioning system. On the other hand, in the discharge chamber 10 on the compression mechanism section 3 side in the housing 4, a discharge port (not illustrated) that discharges high-pressure refrigerant gas obtained by the compression mechanism section 3 described later to a condenser (not illustrated) of the air conditioning system. ) Is formed.

The electric motor 2 is a drive source that drives the compression mechanism unit 3, and the rotation shaft (shaft) 11 of the electric motor 2 is fitted in the central through hole of the rotor 12 of the compression mechanism unit 3. The electric motor 2 is, for example, a well-known three-phase synchronous motor, and the rotation speed is controlled by the inverter unit 5. The rotating shaft 11 is rotatably supported by the bearing.

The inverter unit 5 converts DC power supplied from an external battery into three-phase AC power and supplies it to the electric motor 2, and changes the number of revolutions of the electric motor 2 in accordance with the operating status of an air conditioning system (not shown). Control. The inverter unit 5 and the electric motor 2 are electrically connected via an airtight terminal 50 (see FIG. 3). The airtight terminal 50 is disposed in a mounting opening 6a formed between the partition plate 7 in the inverter case 6 and the airtight terminal 50 is connected to the inverter case 6 side by the pressure of the refrigerant gas sucked into the housing 4 (see FIG. 1 is held (fixed) by a retaining ring 60 so as not to come off. The details of the airtight terminal holding structure by the retaining ring 60, which is a feature of the present invention, will be described later.

The compression mechanism section 3 has a contour shape surrounding the rotary shaft 11 of the electric motor 2, a substantially cylindrical rotor 12 that rotates integrally with the rotary shaft 11, and the rotor 12 from the outside of the outer peripheral surface 12 a. A cylinder 13 having an inner peripheral surface 13a, five plate-like vanes 14 provided so as to protrude from the outer peripheral surface 12a of the rotor 12 toward the inner peripheral surface 13a of the cylinder 13, and both ends of the rotor 12 and the cylinder 13 2 side blocks (front side block 15 and rear side block 16).

On the outer peripheral surfaces of the front side block 15 and the rear side block 16, seal members such as O-rings are installed over the entire periphery of the outer peripheral surface, and a suction chamber 9 formed in the housing 4 on the front side block 15 side. The discharge chamber 10 formed in the housing 4 on the rear side block 16 side is airtightly partitioned. An oil separator 17 is attached to the outer surface of the rear side block 16 so as to be positioned in the discharge chamber 10.

As shown in FIG. 2, a single cylinder chamber 18 is formed between the inner peripheral surface 13a of the cylinder 13, the outer peripheral surface 12a of the rotor 12, and both side blocks 15 and 16 (see FIG. 1). .

Specifically, the inner peripheral surface 13a of the cylinder 13 and the outer peripheral surface 12a of the rotor 12 are only one place (proximal portion 19 in FIG. 2) within a range of one rotation (angle 360 degrees) around the axis of the rotating shaft 11. The contour shape of the inner peripheral surface 13a of the cylinder 13 is set so as to be in close contact (closest to each other), whereby the cylinder chamber 18 forms a single substantially crescent-shaped space.

Of the contour shape of the inner peripheral surface 13 a of the cylinder 13, the proximity portion 19, which is the region where the inner peripheral surface 13 a of the cylinder 13 and the outer peripheral surface 12 a of the rotor 12 are closest, is the same as the inner peripheral surface 13 a of the cylinder 13. In this embodiment, a position that is separated from the remote portion 20 that is the region farthest from the outer peripheral surface 12a of the rotor 12 downstream by an angle of about 270 degrees along the rotation direction W (clockwise direction in FIG. 2) of the rotor 12. Is set to

The vane 14 is slidably fitted in a vane groove 21 formed in the rotor 12, and protrudes outward from the outer peripheral surface 12 a of the rotor 12 by back pressure due to refrigerating machine oil supplied to the vane groove 21. The vane 14 divides the single cylinder chamber 18 into a plurality of compression chambers 22, and one compression chamber 22 is formed by the two vanes 14 that move back and forth along the rotation direction W of the rotor 12. The Therefore, in the present embodiment in which five vanes 14 are installed around the rotating shaft 11 at an equal angular interval of 72 degrees, five compression chambers 22 are formed.

A suction hole 23 that is formed in the front side block 15 and communicates with the suction chamber 9 faces the portion on the downstream side in the rotation direction of the rotor 12 with respect to the proximity portion 19 of the cylinder chamber 18.

On the other hand, on the inner peripheral surface 13a of the cylinder 13 on the upstream side in the rotation direction of the rotor 12 with respect to the proximity portion 19 of the cylinder chamber 18, the first discharge hole 24a and the first discharge hole 24a are arranged along the circumferential direction of the inner peripheral surface 13a. Two discharge holes 24b are formed. The first discharge hole 24 a is closer to the proximity portion 19 along the rotation direction W of the rotor 12, and is located upstream of the first discharge port 24 a along the rotation direction W of the rotor 12. Two discharge holes 24b are formed.

The first and second discharge holes 24a and 24b communicate with

discharge chambers

25a and 25b as spaces formed between the outer peripheral surface of the cylinder 13 and the inner peripheral surface of the housing 4, respectively. Further, the

discharge passages

26a and 26b communicating with the rear side block 16 between the

discharge chambers

25a and 25b and the oil separation portion 17 attached to the outer surface of the rear side block 16 (surface facing the discharge chamber 10). Is formed.

On the upstream side in the rotational direction of the rotor 12 with respect to the remote portion 20 of the cylinder chamber 18, the cylinder 12 is rapidly increased so that the interval between the inner peripheral surface 13 a of the cylinder 13 and the outer peripheral surface 12 a of the rotor 12 increases from a small state. The contour shape of the inner peripheral surface 12 a is set, and in the angle range including the remote portion 20, the volume of the compression chamber 22 increases with the rotation of the rotor 12 in the rotation direction W, and the compression chamber 22 passes through the suction hole 23. This is a stroke (suction stroke) in which the low-pressure refrigerant gas G1 is sucked.

Next, the cylinder 13 is arranged such that the distance between the inner peripheral surface 13a of the cylinder 13 and the outer peripheral surface 12a of the rotor 12 gradually decreases toward the downstream side in the rotation direction of the rotor 12 with respect to the remote portion 20 of the cylinder chamber 18. A contour shape of the inner peripheral surface 13a is set, and in this range, the volume of the compression chamber 22 decreases with the rotation of the rotor 12, and the stroke in which the refrigerant gas in the compression chamber 22 is compressed (compression stroke) Become.

As the rotor 12 rotates, the gap between the inner peripheral surface 13a of the cylinder 13 and the outer peripheral surface 12a of the rotor 12 is further reduced, so that the compression of the refrigerant gas further proceeds, and the pressure of the refrigerant gas reaches the discharge pressure. The high-pressure refrigerant gas G2 becomes a stroke (discharge stroke) discharged into the first discharge holes 24a (or the first and second discharge holes 24a and 24b).

As described above, in the compressor 1 (compression mechanism unit 3), the refrigerant gas suction stroke, compression stroke, and discharge stroke are performed for one cycle during one rotation of the rotor 12, and the low pressure suctioned from the suction chamber 9 is performed. The refrigerant gas is set to a high pressure and discharged from the first discharge holes 24a (or the first and second discharge holes 24a and 24b).

In addition, a discharge valve 27 and a valve support 28 are installed around the second discharge hole 24b. The discharge valve 27 is elastically deformed so as to warp toward the discharge chamber 25b when the pressure of the refrigerant gas in the compression chamber 22 in the compression stroke becomes equal to or higher than a predetermined discharge pressure, and opens the second discharge hole 24b. When the pressure does not reach the predetermined discharge pressure, the second discharge hole 24b is closed by an elastic force. The valve support 28 prevents the discharge valve 27 from excessively warping toward the discharge chamber 25b. The first discharge hole 24a is not provided with these discharge valves and valve supports, and is always open.

Therefore, when the vane on the front side of the two vanes 14 forming the compression chamber 22 reaches the second discharge hole 24b along the rotor rotation direction, the pressure of the refrigerant gas in the compression chamber 22 is a predetermined discharge. When the pressure has not been reached, the second discharge hole 24b remains closed by the discharge valve 27, and the refrigerant gas that has reached a predetermined discharge pressure by the subsequent compression is discharged from the first discharge hole 24a.

Further, when the front vane of the two vanes 14 forming the compression chamber 22 reaches the second discharge hole 24b along the rotor rotation direction, the pressure of the refrigerant gas in the compression chamber 22 is set at a predetermined discharge rate. When the pressure is reached, the discharge valve 27 is warped and the second discharge hole 24b is opened. Therefore, in this case, the refrigerant gas is discharged from the first and second discharge holes 24a and 24b.

The oil separator 17 separates the refrigeration oil mixed with the refrigerant gas (the vane back pressure oil leaked from the vane groove 21 formed in the rotor 12 into the cylinder chamber 18 (compression chamber 22)) from the refrigerant gas. The high-pressure refrigerant gas discharged through the first and second discharge holes 24a and 24b and introduced through the

discharge chambers

25a and 25b and the

discharge passages

26a and 26b is spirally swirled to refrigerating machine oil. It is configured to centrifuge.

And the refrigerating machine oil R (refer FIG. 1) isolate | separated from the refrigerant gas in the oil separation part 17 accumulates in the bottom part of the discharge chamber 10, and the high-pressure refrigerant gas after the refrigerating machine oil R is separated is the discharge chamber 10 It is discharged to a condenser (not shown) through a discharge port (not shown).

The refrigerating machine oil accumulated at the bottom of the discharge chamber 10 is supplied through the oil passage 16a formed in the rear side block 16 and the

Sarai grooves

30 and 31 which are recesses for supplying back pressure, and the rear side block due to the high pressure atmosphere in the discharge chamber 10. The

oil passages

16 a and 16 b formed in 16, the oil passage 32 formed in the cylinder 13, the oil passage 33 formed in the front side block 15, and a salai that is a back pressure supply recess formed in the front side block 15. The grooves are supplied to the vane grooves 21 of the rotor 12 through the

grooves

34 and 35, respectively, and become back pressure that causes the vanes 14 to protrude outward.

(Configuration of airtight terminal 50)
As shown in FIGS. 1 and 3, an airtight terminal 50 for electrically connecting the inverter unit 5 and the electric motor 2 is provided in the attachment opening 6 a having an oval hole formed in the inverter case 6. It has been. In FIG. 3, the electric motor is located below the attachment opening 6a.

As shown in FIG. 3, the airtight terminal 50 includes a flat terminal body 51 and three

electrode terminals

52 a, 52 b, and 52 c made of a conductive member fitted through the terminal body 51. The outer peripheral portion of the electric motor (lower side in FIG. 3) is disposed in a protruding portion 6b formed in the mounting opening 6a. The terminal body 51 is formed in an oval shape, and has a pair of linear long side portions 51a facing each other and a pair of curved short side portions 51b continuous from both ends of the long side portion 51a. Yes.

An O-ring 53 is interposed between the protrusion 6b of the mounting opening 6a and the outer periphery of the terminal body 51 in order to maintain airtightness. The three

electrode terminals

52a, 52b, and 52c correspond to the three-phase electric motor 2, and the terminal section (not shown) on the inverter section 5 side and the electric motor 2 are connected to the

electrode terminals

52a, 52b, and 52c. The

side terminal portions

2a, 2b, 2c are electrically connected.

Further, the outer peripheral portion of the terminal body 51 on the inverter portion 5 side (upper side in FIG. 3) is connected to the inverter portion 5 side (FIG. 3) by a retaining ring 60 engaged with a concave inner peripheral groove portion 6c formed in the mounting opening 6a. It is locked (fixed) so as not to come off.

(Configuration of retaining ring 60)
As shown in FIGS. 4 and 5, a flat retaining ring 60 made of a metal material connects a pair of

arm portions

60a and 60b extending linearly and one end of the

arm portions

60a and 60b. And an arc-shaped curved portion 60c that is elastically deformable and formed integrally therewith. Note that the retaining ring 60 shown in FIG. 4 is in a state of being engaged with the inner peripheral groove 6c of the attachment opening 6a, and the pair of

arms

60a and 60b are in a substantially parallel state. FIG. 5 shows the retaining ring 60 before engaging with the inner circumferential groove 6c, and the pair of

arm portions

60a and 60b are opened outward.

The intermediate portions along the longitudinal direction of the

arm portions

60a and 60b have projecting

portions

60d and 60e projecting inward, and

jig holes

60f and 60g are formed in the projecting

portions

60d and 60e. Also, the ends of the

arm portions

60a, 60b opposite to the curved portion 60c (the lower side in FIGS. 4 and 5) are slightly inwardly aligned with the curved shape of the inner wall surface of the mounting opening 6a (inner circumferential groove portion 6c). It is curved.

The jig holes 60f and 60g are opposite to the curved portion 60c with respect to the intermediate portions of the

arm portions

60a and 60b, and when the retaining ring 60 is attached to the attachment opening 6a (inner peripheral groove portion 6c), the electrode terminal 52a. , 52b, 52c are formed at positions that do not interfere with each other. In the present embodiment, the jig holes 60f and 60g are positioned between the electrode terminal 52b and the electrode terminal 52c.

The curved portion 60c is curved corresponding to the curved shape of the inner wall surface of the mounting opening 6a (inner circumferential groove 6c). Further, the outer peripheral surface side of the bending portion 60c is formed so as to have a step in the vicinity of the ends of the integrally formed

arm portions

60a and 60b so that the radial width is reduced, and the bending portion 60c is small. It is designed to be easily elastically deformed by force.

That is, as shown in FIG. 5, by providing a stepped portion 60h from the vicinity of the ends of the

arm portions

60a and 60b and reducing the thickness of the entire outer peripheral surface side of the bending portion 60c, the radial direction of the bending portion 60c is reduced. The width t1 is smaller than the width t2 of the

arm portions

60a and 60b. For example, the width t1 of the curved portion 60c is about 60% of the width t2 of the

arm portions

60a and 60b. The retaining ring 60 shown by the solid line in FIG. 5 is in a state before being engaged with the inner circumferential groove 6c of the mounting opening 6a, and the bending portion 60c is not elastically deformed in the inner direction, and the

arm portion

60a and 60b are open at a predetermined angle.

And in order to hold | maintain (fix) this airtight terminal 50 with the retaining ring 60 with respect to the airtight terminal 50 arrange | positioned at the protrusion part 6b of the attachment opening part 6a, the jig hole 60f of the retaining ring 60 shown in FIG. , 60g, by inserting a tip protrusion of an attachment jig (not shown) and applying a force so that the bending portion 60c is elastically deformed inward, thereby displacing the

arm portions

60a, 60b inward (two-dot chain line). The state shown in). At this time, since the radial width of the curved portion 60c is made smaller than the width of the

arm portions

60a and 60b, the tip protrusions of the mounting jig (not shown) are inserted into the jig holes 60f and 60g, and the arm portion 60a. , 60b can be reduced in force when displaced inward.

In this state, the retaining ring 60 is placed on the airtight terminal 50 (terminal body 51), and the curved portion 60c side of the retaining ring 60 is pushed into one curved side of the inner circumferential groove portion 6c of the mounting opening 6a. Then, by removing the attachment jig (not shown) from the jig holes 60f and 60g, the curved portion 60c is elastically deformed outward as shown in FIGS. 3 and 4, and the outer surface side of the

arm portions

60a and 60b is attached. Engaged with the inner peripheral groove 6c of the opening 6a in a biased state.

As a result, the airtight terminal 50 (terminal body 51) is held against the projecting portion 6b of the mounting opening 6a by the

arms

60a, 60b and the curved portion 60c of the retaining ring 60 engaged with the inner circumferential groove 6c. (Fixed). Since the O-ring 53 is interposed between the airtight terminal 50 (terminal body 51) and the protruding portion 6b, the airtight terminal 50 (terminal body 51) is held in the mounting opening 6a with good airtightness. .

Thus, according to the airtight terminal holding structure by the retaining ring 60, the airtight terminal 50 can be easily retained (fixed) in the mounting opening 6a by one assembling operation using one retaining ring 60. it can. Therefore, the work time is shortened and workability can be improved as compared with the assembly work of fixing the airtight terminal using two C-shaped retaining rings as in the prior art.

Further, since the radial width of the curved portion 60c of the retaining ring 60 is smaller than the width of the

arm portions

60a and 60b, the tip protrusions of the mounting jig (not shown) are inserted into the jig holes 60f and 60g. Thus, the force when displacing the

arms

60a and 60b in the inner direction can be reduced, and the workability during the assembly work can be further improved.

In addition, when two C-shaped retaining rings are used as in the prior art, the long side of the hermetic terminal is used to fix the curved short side of the hermetic terminal with the two C-shaped retaining rings. The holding force in the vicinity of the center becomes weak, and a seal failure may occur due to the pressure of the refrigerant gas supplied (sucked) into the housing. On the other hand, in the present embodiment, the entire linear long side of the airtight terminal 50 is securely held by the

linear arms

60a and 60b opposed to the retaining ring 60, thereby causing a sealing failure. There is no.

In addition, although the said embodiment was provided with the vane rotary type compression mechanism part, if it is an electric compressor provided with the electric motor of the structure which fixes an airtight terminal with a retaining ring, it can also be set as the compression mechanism part of another system. Is possible.

Cross-reference of related applications

This application claims priority based on Japanese Patent Application No. 2013-142656 filed with the Japan Patent Office on July 8, 2013, the entire disclosure of which is fully incorporated herein by reference.

Claims

A compression mechanism that compresses a medium supplied from the outside into the housing and discharges a high-pressure medium to the outside; an electric motor that drives the compression mechanism; and a motor controller that controls the driving of the electric motor; In the gas compressor that is disposed in the mounting opening and includes an airtight terminal for electrically connecting the electric motor and the motor control unit,
The hermetic terminal includes a flat terminal body formed by a pair of opposing linear long sides and a curved short side continuous from both ends of the long sides, and both sides of the terminal body An electrode terminal provided so as to protrude to
An outer peripheral side of a retaining ring is engaged with a concave groove formed on an inner wall surface of the mounting opening with respect to the hermetic terminal disposed on the projecting portion formed in the mounting opening, and the airtight terminal is engaged with the retaining ring. An airtight terminal holding structure of a gas compressor for holding the inside of the mounting opening,
The retaining ring includes a pair of arm portions extending linearly;
The arm portions are integrally formed so as to connect one end of each arm portion, and have a bending portion that is narrower than the width of the arm portion and elastically deformable,
With the curved part of the retaining ring elastically deformed and the arms being displaced inward, the outer peripheral side of the retaining ring is engaged with the groove part,
An airtight terminal holding structure for a gas compressor, wherein the curved portion holds the short side portion on one side of the airtight terminal, and each arm portion holds each long side portion of the airtight terminal.
2. The airtight terminal holding structure for a gas compressor according to claim 1, wherein the curved portion of the retaining ring is formed to be narrower than the width of the arm portion over the entire outer peripheral surface thereof.
3. The gas according to claim 1, wherein a jig insertion portion into which a jig for displacing each arm portion in an inward direction is inserted is formed in each arm portion of the retaining ring. 4. Airtight terminal holding structure of the compressor.
The jig insertion portion is formed at a position opposite to the bending portion with respect to the intermediate portion of each arm portion, and at a position that does not interfere with the electrode terminal when the outer peripheral side of the retaining ring is engaged with the groove portion. The airtight terminal holding structure for a gas compressor according to claim 3, wherein the airtight terminal holding structure is provided.