阅读说明：本技术 涡旋式压缩机 (Scroll compressor having a discharge port ) 是由 今井哲也 佐藤泰造 于 2020-03-16 设计创作，主要内容包括：提供一种涡旋式压缩机,能有效地减轻从排出空间至排出端口的通路中的压力损失。包括：排出空间(27),所述排出空间(27)形成于外壳(11)的压缩机构罩(9)内；排出孔(26),所述排出孔(26)形成于定涡盘(21),并将压缩后的制冷剂排出到排出空间；排出端口(51),所述排出端口(51)将制冷剂排出到外壳外；泄压通路(71),所述泄压通路(71)使排出空间与排出端口连通；以及压差阀(74),所述压差阀(74)设置于泄压通路,并根据排出空间与排出端口的压力差打开,泄压通路在比排出孔靠上侧的位置处朝排出空间开口。(Provided is a scroll compressor capable of effectively reducing pressure loss in a passage from a discharge space to a discharge port. The method comprises the following steps: a discharge space (27), the discharge space (27) being formed in a compression mechanism cover (9) of a housing (11); a discharge hole (26), wherein the discharge hole (26) is formed in the fixed scroll (21) and discharges the compressed refrigerant to a discharge space; a discharge port (51), the discharge port (51) discharging refrigerant out of the housing; a pressure relief passage (71), the pressure relief passage (71) communicating the discharge space with the discharge port; and a differential pressure valve (74), wherein the differential pressure valve (74) is arranged on the pressure relief channel and opens according to the pressure difference between the discharge space and the discharge port, and the pressure relief channel is opened towards the discharge space at the position above the discharge hole.)

1. A scroll compressor includes a compression mechanism composed of a fixed scroll and an orbiting scroll in a casing, each of orbiting members of the fixed scroll and the orbiting scroll being formed opposite to each front surface of each mirror plate, compressing a working fluid by a compression chamber formed between the respective orbiting members of the two scrolls by orbiting and orbiting the orbiting scroll with respect to the fixed scroll,

it is characterized by comprising:

a discharge space formed within the housing;

a discharge hole formed at the fixed scroll and discharging the compressed working fluid to the discharge space;

a discharge port that discharges the working fluid out of the housing;

a pressure relief passage communicating the discharge space with the discharge port; and

a differential pressure valve disposed in the pressure relief passage and opened according to a pressure difference between the discharge space and the discharge port,

the pressure relief passage opens to the discharge space at a position above the discharge hole.

2. The scroll compressor of claim 1,

includes a sound-deadening chamber formed in the housing so as to be located between the discharge space and the discharge port and to communicate the discharge space with the discharge port,

the pressure relief passage communicates the discharge space with the discharge port without passing through the sound-deadening chamber.

3. The scroll compressor of claim 2,

comprising an oil separator formed in the discharge space,

the working fluid discharged from the discharge hole flows into the muffling chamber after passing through the oil separator,

and the pressure relief passage communicates the discharge space with the discharge port without passing through the oil separator and the muffling chamber.

4. The scroll compressor of claim 2,

comprising an oil separator formed in the discharge space,

the working fluid discharged from the discharge hole flows into the muffling chamber after passing through the oil separator,

and the pressure relief passage communicates the working fluid outlet of the oil separator with the discharge port without passing through the muffling chamber.

5. The scroll compressor of any one of claims 1 to 4,

the differential pressure valve opens when the pressure of the discharge space is greater than the pressure of the discharge port and the difference between the pressure of the discharge space and the pressure of the discharge port reaches a prescribed value (PD 1).

6. The scroll compressor of claim 5,

includes a discharge valve provided to the discharge hole and opened when a pressure difference between the compression chamber and the discharge space reaches a prescribed value (PD2),

the prescribed value (PD1) is greater than the prescribed value (PD 2).

Technical Field

The present invention relates to a scroll compressor for compressing a working fluid in a compression chamber formed between surrounding members of two scrolls by orbiting and orbiting a movable scroll with respect to a fixed scroll.

Background

Conventionally, such a scroll compressor includes a compression mechanism including a fixed scroll including a spiral wrap on a front surface of a mirror plate and an orbiting scroll including a spiral wrap on a front surface of a mirror plate, wherein the wraps of the scrolls are opposed to each other to form a compression chamber between the wraps, and the orbiting scroll revolves and revolves around the fixed scroll to compress a working fluid (refrigerant) in the compression chamber (see, for example, patent document 1).

Further, in patent document 1, a relief valve is provided in a relief passage that communicates a discharge space (a discharge chamber of document 1) with a discharge passage, and the relief passage is opened by a pressure difference. The pressure release passage discharges the liquid accumulated in the discharge space (discharge chamber) to the discharge passage so as to open to the discharge space (discharge chamber) at a position lower than the discharge port (discharge port of the document).

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open No. 2010-151060

Disclosure of Invention

Technical problem to be solved by the invention

In this scroll compressor, a sound deadening chamber for reducing pulsation, an oil separator described in patent document 1, and the like are generally disposed between the discharge space and the discharge port. The working fluid discharged from the discharge port of the fixed scroll to the discharge space reaches the discharge port after passing through the oil separator and the muffler chamber.

Therefore, there is a problem that, particularly under a high volume flow rate condition of the working fluid (exhaust gas) discharged from the discharge hole, pressure loss occurs and efficiency is reduced by passing through the oil separator and the muffler chamber. In this regard, in patent document 1, the pressure relief passage is opened at a position lower than the discharge port, and the liquid accumulated in the discharge space is discharged to the discharge passage, and therefore, the effect of reducing the pressure loss as described above cannot be expected.

The present invention has been made to solve the above-described conventional problems, and an object of the present invention is to provide a scroll compressor capable of effectively reducing a pressure loss in a path from a discharge space to a discharge port.

Technical scheme for solving technical problem

The present invention provides a scroll compressor, which comprises a compression mechanism composed of a fixed scroll and a movable scroll in a housing, wherein the fixed scroll and the movable scroll are respectively provided with a spiral surrounding piece and a front surface of each mirror plate, and the movable scroll revolves and revolves relative to the fixed scroll to compress working fluid through a compression chamber formed between the surrounding pieces of the two scrolls, the scroll compressor is characterized by comprising: a discharge space formed within the housing; a discharge hole formed at the fixed scroll and discharging the compressed working fluid to a discharge space; a discharge port that discharges the working fluid outside the housing; a pressure relief passage communicating the discharge space with the discharge port; and a differential pressure valve provided in the pressure release passage and opened according to a pressure difference between the discharge space and the discharge port, the pressure release passage opening toward the discharge space at a position above the discharge hole.

The scroll compressor according to the invention of claim 2 is characterized by including a sound-deadening chamber formed in the casing so as to be located between the discharge space and the discharge port and communicate the discharge space with the discharge port, and the pressure-releasing passage communicating the discharge space with the discharge port without passing through the sound-deadening chamber.

The scroll compressor according to claim 3 of the present invention is characterized in that the scroll compressor includes an oil separator formed in the discharge space, the working fluid discharged from the discharge port flows into the muffling chamber after passing through the oil separator, and the relief passage communicates the discharge space with the discharge port without passing through the oil separator and the muffling chamber.

The scroll compressor according to claim 4 of the present invention is the scroll compressor according to claim 2, further comprising an oil separator formed in the discharge space, wherein the working fluid discharged from the discharge port flows into the muffling chamber after passing through the oil separator, and the relief passage communicates the working fluid outlet and the discharge port of the oil separator without passing through the muffling chamber.

The scroll compressor according to the invention of claim 5 is characterized in that, in addition to the above-described inventions, the differential pressure valve opens when the pressure in the discharge space is higher than the pressure at the discharge port and the difference between the pressure in the discharge space and the pressure at the discharge port reaches a predetermined value PD 1.

The scroll compressor according to the invention of claim 6 is characterized by including a discharge valve provided in the discharge hole and opened when the pressure difference between the compression chamber and the discharge space reaches a predetermined value PD2, wherein the predetermined value PD1 is greater than the predetermined value PD 2.

Effects of the invention

According to the present invention, since the relief passage that communicates the discharge space from which the working fluid is discharged from the discharge port of the fixed scroll and the discharge port from which the working fluid is discharged to the outside of the casing is formed, and the pressure difference valve that opens according to the pressure difference between the discharge space and the discharge port is provided in the relief passage, and the relief passage is opened to the discharge space at the position above the discharge port, it is possible to effectively reduce the pressure loss in the noise reduction chamber provided between the discharge space and the discharge port and the oil separator configured in the discharge space, as in claims 2 to 4, and to improve the efficiency, under the condition of a high volume flow rate of the working fluid.

Further, since the degree of freedom in designing the muffling chamber increases, the discharge pulsation in a low speed condition can be effectively reduced. Further, since the conditions for opening the differential pressure valve are set as in claim 5 and claim 6, the pressure loss can be smoothly reduced.

Drawings

Fig. 1 is a sectional view of a scroll compressor to which an embodiment of the present invention is applied.

Fig. 2 is a front view of a compression mechanism cover of the scroll compressor of fig. 1.

Fig. 3 is a diagram illustrating a flow of a refrigerant (working fluid) from a compression mechanism of the scroll compressor of fig. 1 to a refrigerant circuit.

Detailed Description

Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.

Example 1

Fig. 1 is a sectional view of a scroll compressor 1 to which an embodiment of the present invention is applied. The scroll compressor 1 of the present embodiment is used in, for example, a refrigerant circuit R (fig. 3) of a vehicle air conditioner, and is a so-called inverter-integrated scroll compressor that sucks, compresses, and discharges a refrigerant as a working fluid of the vehicle air conditioner, and includes a motor 2, an inverter 3 for operating the motor 2, and a compression mechanism 4 driven by the motor 2.

The scroll compressor 1 of the embodiment includes: a main housing 6, the main housing 6 accommodating the motor 2 and the inverter 3 therein; a compression mechanism housing 7, the compression mechanism housing 7 accommodating the compression mechanism 4 therein; an inverter cover 8; and a compression mechanism cover 9. The main casing 6, the compression mechanism casing 7, the inverter cover 8, and the compression mechanism cover 9 are made of metal (aluminum in the embodiment), and are integrally joined to constitute a casing 11 of the scroll compressor 1. That is, the compression mechanism cover 9 constitutes a part of the housing 11.

The main casing 6 is composed of a cylindrical peripheral wall portion 6A and a partition wall portion 6B. The partition wall 6B is a partition wall that partitions the interior of the main casing 6 into a motor housing 12 that houses the motor 2 and an inverter housing 13 that houses the inverter 3. One end surface of the inverter housing portion 13 is open, and the opening is closed by the inverter cover 8 after housing the inverter 3.

The other end surface of the motor housing 12 is also open, and the opening is closed by the compression mechanism case 7 after housing the motor 2. A support portion 16 is provided to protrude from the partition wall portion 6B, and the support portion 16 supports one end portion (an end portion on the opposite side from the compression mechanism 4) of the rotating shaft 14 of the motor 2.

The compression mechanism housing 7 is open on the side opposite to the main housing 6, and the opening is closed by the compression mechanism cover 9 after the compression mechanism 4 is housed. The compression mechanism casing 7 is composed of a cylindrical peripheral wall portion 7A and a frame portion 7B on one end side (main casing 6 side) of the peripheral wall portion 7A, and the compression mechanism 4 is accommodated in a space defined by the peripheral wall portion 7A and the frame portion 7B. The frame 7B is a partition wall that partitions the inside of the main casing 6 and the inside of the compression mechanism casing 7.

The frame portion 7B is opened with a through hole 17 through which the other end portion (end portion on the compression mechanism 4 side) of the rotating shaft 14 of the electric motor 2 is inserted, and a front bearing 18 as a bearing member that supports the other end portion of the rotating shaft 14 is fitted to the compression mechanism 4 side of the through hole 17. Further, reference numeral 19 denotes a seal member for sealing the outer peripheral surface of the counter shaft 14 and the inside of the compression mechanism case 7 at the through hole 17 portion.

The motor 2 is composed of a stator 25 around which a coil 35 is wound and a rotor 30. Further, for example, a direct current from a battery (not shown) of the vehicle is converted into a three-phase alternating current by the inverter 3, and the rotor 30 is driven to rotate by supplying power to the coil 35 of the motor 2.

A suction port, not shown, is formed in the main casing 6, and the refrigerant sucked from the suction port is sucked into a suction portion 37, which will be described later, outside the compression mechanism 4 in the compression mechanism casing 7 after passing through the main casing 6. Thereby, the motor 2 is cooled by the sucked refrigerant. The refrigerant compressed by the compression mechanism 4 is discharged into the discharge space 27 as described later, and then finally discharged out of the casing 11, that is, the refrigerant circuit R, from the discharge port 51 formed in the compression mechanism cover 9.

The compression mechanism 4 is constituted by a fixed scroll 21 and a movable scroll 22. The fixed scroll 21 integrally includes a disk-shaped mirror plate 23 and a spiral surround 24, the surround 24 is formed by an involute or a curve close to the involute which is erected on the front surface (one surface) of the mirror plate 23, and the front surface of the mirror plate 23 on which the surround 24 is erected is fixed to the compression mechanism case 7 as the frame portion 7B side. A discharge hole 26 is formed in the center of the mirror plate 23 of the fixed scroll 21, and the discharge hole 26 communicates with a discharge space 27 in the compression mechanism cover 9. Reference numeral 28 denotes an outlet valve provided at an opening on the back surface (the other surface) side of the mirror plate 23 of the outlet 26. The discharge valve 28 opens to communicate the discharge hole 26 with the discharge space 27 when the pressure in the compression chamber 34 is higher than the pressure in the discharge space 27 and the pressure difference between the compression chamber 34 and the discharge space 27 reaches a predetermined value PD 2.

The orbiting scroll 22 is a scroll that orbits and revolves with respect to the fixed scroll 21, and integrally includes a disk-shaped mirror plate 31, a spiral surround 32, and a boss portion 33, the surround 32 is formed by a curve that stands on the front surface (one surface) of the mirror plate 31 and is in a shape of a splash or a curve that is approximately in an involute shape, and the boss portion 33 is formed to protrude from the center of the back surface (the other surface) of the mirror plate 31. The orbiting scroll 22 is disposed so that the protruding direction of the orbiting scroll 32 is set to the fixed scroll 21 side, the orbiting scroll 32 faces the orbiting scroll 24 of the fixed scroll 21 to be engaged with each other while facing each other, and a compression chamber 34 is formed between the respective orbiting scrolls 24 and 32.

That is, the surround 32 of the orbiting scroll 22 is opposed to the surround 24 of the fixed scroll 21, and is engaged in such a manner that the front end of the surround 32 contacts the front surface of the mirror plate 23 and the front end of the surround 24 contacts the front surface of the mirror plate 31. A drive projection 48 is provided at the other end of the rotating shaft 14, i.e., at the end on the orbiting scroll 22 side, and the drive projection 48 projects at a position eccentric from the axial center of the rotating shaft 14. Further, an eccentric bush 36 is attached to the driving projection 48, and is provided eccentrically from the axis of the rotating shaft 14 at the other end portion of the rotating shaft 14.

In this case, a drive projection 48 is attached to a position of the eccentric bush 36 eccentric from the axial center of the eccentric bush 36, and the eccentric bush 36 is fitted to the boss portion 33 of the orbiting scroll 22. When the rotation shaft 14 rotates together with the rotor 30 of the motor 2, the orbiting scroll 22 orbits and revolves around the fixed scroll 21 without rotating. Reference numeral 49 denotes a balance weight attached to the outer peripheral surface of the rotary shaft 14 on the orbiting scroll 22 side of the front bearing 18.

Since the orbiting scroll 22 orbits eccentrically with respect to the fixed scroll 21, the eccentric direction and contact position of the orbiting scroll 24 and 32 move while revolving, and the compression chamber 34, which sucks the refrigerant from the suction portion 37 on the outer side, gradually shrinks while moving to the inner side. Thereby, the refrigerant is compressed and finally discharged from the discharge hole 26 at the center to the discharge space 27 through the discharge valve 28.

In fig. 1, reference numeral 38 denotes an annular thrust plate. The thrust plate 38 is a member for defining a back pressure chamber 39 formed on the back surface side of the mirror plate 31 of the orbiting scroll 22 and a suction portion 37 as a suction pressure region outside the compression mechanism 4 in the compression mechanism casing 7. Reference numeral 41 denotes a seal member attached to the back surface of the mirror plate 31 of the orbiting scroll 22 and abutting against the thrust plate 38, and the back pressure chamber 39 and the suction portion 37 are defined by the seal member 41 and the thrust plate 38.

Reference numeral 42 denotes a seal member which is attached to a surface of the frame portion 7B on the thrust plate 38 side and which abuts against the outer peripheral portion of the thrust plate 38 to seal between the frame portion 7B and the thrust plate 38.

In fig. 1, reference numeral 43 denotes a back pressure passage formed from the compression mechanism cover 9 to the compression mechanism casing 7, and an orifice 44 is installed in the back pressure passage 43. The back pressure passage 43 is configured such that the oil outlet 53A of the oil separator 52 formed in the discharge space 27 of the compression mechanism cover 9 communicates with the back pressure chamber 39, and thereby oil at the discharge pressure depressurized and adjusted by the orifice 44 is supplied to the back pressure chamber 39 as indicated by an arrow in fig. 1.

A back pressure load for pressing the orbiting scroll 22 against the fixed scroll 21 is generated by the pressure (back pressure) in the back pressure chamber 39. The back pressure load presses the orbiting scroll 22 against the fixed scroll 21 against the compression reaction force from the compression chamber 34 of the compression mechanism 4, and the contact between the surrounding members 24 and 32 and the mirror plates 31 and 23 is maintained, so that the refrigerant can be compressed by the compression chamber 34.

On the other hand, an oil passage 46 penetrating in the axial direction is formed in the rotary shaft 14, and a pressure regulating valve 47 is provided in the oil passage 46 so as to be positioned on the support portion 16 side. The oil passage 46 communicates the back pressure chamber 39 with the inside of the main casing 6 (suction pressure region), and the oil that flows into the back pressure chamber 39 from the back pressure passage 43 flows into the oil passage 46 and flows out of the main casing 6, but the pressure regulating valve 47 opens when the pressure (back pressure) in the back pressure chamber 39 becomes maximum, and functions so as not to further increase the back pressure.

Next, the detailed structure of the compression mechanism cover 9 constituting a part of the housing 11 will be described with reference to fig. 1 and 2. As described above, the oil separator 52 is formed in the discharge space 27. The oil separator 52 includes an oil separation portion 54, an oil separation cylinder 56, and two communication holes 57 and 57, wherein the oil separation portion 54 and the compression mechanism cover 9 are integrally formed, an oil separation space 53 is formed inside, the oil separation cylinder 56 is inserted into the oil separation portion 54 from above to close an upper portion of the oil separation space 53, a refrigerant outlet (working fluid outlet) 56A at a lower end opens into the oil separation space 53, the two communication holes 57 and 57 are formed to face a side surface of the oil separation cylinder 56, the discharge space 27 other than the oil separator 52 communicates with the oil separation space 53, and a lower end of the oil separation space 53 is set as the oil outlet 53A.

Further, a plurality of sound-deadening chambers 61, 62, 63 and a discharge port chamber 64 are formed in the compression mechanism cover 9 so as to be positioned around the discharge space 27, the sound-deadening chamber 61 and the sound-deadening chamber 62 communicate with each other through a throttle 66, the sound-deadening chamber 62 and the sound-deadening chamber 63 communicate with each other through a throttle 67, the sound-deadening chamber 63 and the discharge port chamber 64 communicate with each other through a throttle 68, and the first sound-deadening chamber 61 and the upper portion of the oil separation cylinder 56 of the oil separator 52 communicate with each other through a communication passage 69. Further, the discharge port chamber 64 communicates with the discharge port 51 to constitute a part of the above-described discharge port 51.

In the present invention, a relief passage 71 is formed in the compression mechanism cover 9, and a differential pressure valve 74 including a ball valve 72 and a compression spring 73 is provided in the relief passage 71. One end of the pressure relief passage 71 opens into the discharge space 27 at a position above the discharge port 26 of the fixed scroll 21, and the other end opens into the discharge port chamber 64, thereby communicating the discharge space 27 with the discharge port chamber 64 (discharge port 51). In fig. 2, the reference symbol P1 indicates the position of the discharge hole 26 in fig. 1.

The compression spring 73 of the differential pressure valve 74 is configured to always press the ball valve 72 against the valve seat (formed in the pressure relief passage 71) to close the pressure relief passage 71 (the differential pressure valve 74 is closed), but when the pressure in the discharge space 27 is higher than the pressure in the discharge port chamber 64 (the discharge port 51) and the pressure difference between the discharge space 27 and the discharge port 64 reaches a predetermined value PD1, the ball valve 72 is separated from the valve seat against the spring force of the compression spring 73 to open the pressure relief passage 71 (the differential pressure valve 74 is opened).

Here, the spring force of the compression spring 73 is set to be greater than the predetermined value PD1 of the pressure difference between the compression chamber 34 and the discharge space 27, at which the discharge valve 28 opens, and the predetermined value PD2 of the pressure difference between the pressure difference valve 74 and the discharge space 27.

With the above configuration, the flow of the refrigerant flowing from the compression mechanism 4 to the refrigerant circuit R will be described with reference to fig. 3. As described above, when the refrigerant is compressed by the orbiting of the orbiting scroll 22 with respect to the fixed scroll 21 and the pressure difference between the compression chamber 34 and the discharge space 27 reaches the predetermined value PD2, the discharge valve 28 is opened, and the refrigerant is discharged from the discharge hole 26 to the discharge space 27. In a normal operation state in which the volume flow rate of the refrigerant (discharge gas) is relatively low, the differential pressure valve 74 is closed.

Thus, the refrigerant (including oil) flowing into the discharge space 27 flows into the oil separation space 53 of the oil separator 52 from the communication holes 57, and swirls around the oil separation cylinder 56. Oil in the refrigerant is separated by the centrifugal force at this time, and the separated oil is supplied from the oil outlet 53A to the back pressure chamber 39 through the back pressure passage 43 and the orifice 44 as described above.

On the other hand, the refrigerant from which oil has been separated flows into the oil separation cylinder 56 from the refrigerant outlet 56A, and flows into the muffler chamber 61 through the communication passage 69. Then, the refrigerant flows into the discharge port chamber 64 through the throttle portion 66, the muffling chamber 62, the throttle portion 67, the muffling chamber 63, and the throttle portion 68 in this order, and is finally discharged from the discharge port 51 to the refrigerant circuit R (the upper flow in fig. 3) located outside the housing 11.

Although the amount of oil flowing out of the oil separator 52 into the refrigerant circuit R is suppressed and pulsation of the refrigerant discharged into the refrigerant circuit R through the noise reduction chambers 61 to 63 and the throttles 66 to 68 is reduced, pressure loss occurs and efficiency is reduced because the refrigerant (exhaust gas) discharged from the discharge port 26 passes through the oil separator 52 and the noise reduction chambers 61 to 63 under a high volume flow rate condition.

Therefore, in the present invention, the pressure relief passage 71 and the differential pressure valve 74 are provided. That is, under the high volume flow rate condition as described above, when the pressure loss becomes large, the pressure in the discharge space 27 rises to be higher than the pressure in the discharge port chamber 64 (the discharge port 51), and the pressure difference reaches the predetermined value PD1, the differential pressure valve 74 opens to open the pressure relief passage 71, so that the discharge space 27 and the discharge port chamber 64 (the discharge port 51) communicate with each other without passing through the oil separator 52 and the noise canceling chambers 61 to 63, that is, without passing through the oil separator 52 and the noise canceling chambers 61 to 63.

Thus, the refrigerant in the discharge space 27 flows into the discharge port chamber 64 (discharge port 51) while bypassing the oil separator 52 and the noise reduction chambers 61 to 63 without passing through the oil separator 52 and the noise reduction chambers 61 to 63, and therefore, the pressure loss in the oil separator 52 and the noise reduction chambers 61 to 63 can be effectively reduced, and the efficiency can be improved. Further, since the degree of freedom in designing the muffling chambers 61 to 63 is increased, the discharge pulsation under low-speed conditions can be effectively reduced. In the embodiment, the predetermined value PD1 for opening the differential pressure valve 74 is made larger than the predetermined value PD2 for opening the discharge valve 28, and therefore, the pressure loss can be reduced smoothly.

Example 2

Further, in the above-described embodiment, the discharge space 27 and the discharge port chamber 64 (the discharge port 51) are communicated with each other through the relief passage 71 in which the differential pressure valve 74 is provided, but the present invention is not limited to this, and the refrigerant outlet (working fluid outlet) 56A of the oil separation cylinder 56 or the communication path 69 through which the refrigerant flows out from the oil separator 52 may be communicated with the discharge port chamber 64 (the discharge port 51) through the relief passage 71 as shown by the broken line in fig. 3.

Thus, the refrigerant in the discharge space 27 flows into the discharge port chamber 64 (discharge port 51) while bypassing the noise reduction chambers 61 to 63, without passing through the noise reduction chambers 61 to 63, and therefore, the pressure loss in the noise reduction chambers 61 to 63 can be effectively reduced.

In the embodiments, the present invention is applied to the scroll compressor used in the refrigerant circuit of the vehicle air conditioner, but the present invention is not limited to this, and is also effective in the scroll compressor used in the refrigerant circuit of various refrigeration apparatuses. In the embodiment, the present invention is applied to a so-called inverter-integrated scroll compressor, but the present invention is not limited to this, and may be applied to a general scroll compressor which does not integrally include an inverter.

(symbol description)

1 a scroll compressor;

4, a compression mechanism;

6 main housing (part of housing 11);

7 compression mechanism housing (part of housing 11);

9 a compression mechanism cover (a part of the housing 11);

11 a housing;

21 fixed scroll pan;

22 an orbiting scroll;

23. 31 a mirror plate;

24. 32 a surround;

26 discharge holes;

27 a discharge space;

28 a discharge valve;

34 a compression chamber;

51 a discharge port;

52 an oil separator;

61-63 anechoic chambers;

64 discharge port chamber (a part of discharge port);

69 a communication path;

71 a pressure relief passage;

74 differential pressure valve.