DE102017104031A1 - compressor - Google Patents

Abstract

The present invention has a compressor which can be sufficiently lubricated, less prone to exhaust pulsation, and capable of achieving downsizing and reduction of production costs. A compressor according to the present invention has a housing, a compression mechanism, an oil separation mechanism, and an oil supply mechanism. The housing has a housing body, a first partition and a second partition. The oil separation mechanism has an oil separation chamber and an oil drainage path. The oil supply mechanism has an oil supply port. The oil drain path has a first flow path formed by penetrating the second partition wall and configured to open from the oil separation chamber toward the first partition wall and a second flow path formed in at least one of the first partition wall and the second flow path Partition is recessed and is formed by the cooperation of the first partition wall and the second partition wall so as to be connected to the first flow path. An exit of the second flow path is at a higher level in a vertical direction than an inlet of the second flow path, avoiding a direction facing the oil supply port.

Description

TECHNICAL AREA

The present invention relates to a compressor.

TECHNICAL BACKGROUND

A conventional wing compressor is in the Japanese Patent Laid-Open No. 7-12072 disclosed. In the compressor, a cylinder block is housed in a housing, and a front side plate and a rear side plate are tied and fixed on opposite sides of the cylinder block. An oil storage chamber, which is an exhaust chamber, is formed between the rear side plate and the housing. The rear side plate has an oil separator. The oil separator is formed by a housing and an oil separation cylinder, which is fixed to an upper part of an oil separation chamber formed in the housing.

In the oil separation chamber, lubricating oil is separated from a refrigerant. The refrigerant from which the lubricating oil is deposited is discharged from an exhaust chamber to a cooling circuit outside. The lubricating oil in the oil separation chamber is stored in the oil storage chamber via an oil drainage path. The lubricating oil from the oil storage chamber is supplied through a oil feed passage connected to the oil storage passage of a vane groove serving as a back pressure chamber or a sliding portion such as a bearing, the back pressure chamber generating back pressure to press a vane.

However, in the compressor in which the oil drain path linearly connects the oil separation chamber and the oil storage chamber, the flow speed of the lubricating oil is less likely to decrease, and as a result, the lubricating oil in the oil storage chamber tends to be swirled or disturbed by the lubricating oil discharged through the oil drain path when a large amount of lubricating oil is stored in the oil storage chamber. Therefore, the refrigerant in the discharge chamber tends to be mixed again with the lubricating oil in the oil storage chamber, and the lubricating oil mixed with the refrigerant tends to be supplied to the vane groove by the opening of the oil supply passage. In this case, the sliding portion is not lubricated sufficiently, which raises concerns that noise and vibration may be generated, which break the low noise, and that the durability may be deteriorated.

To overcome these concerns, which, for example, in the Japanese Patent Laid-Open No. 2010-31757 can be described, it is conceivable to define a space in the housing of the oil separator in the outlet space to store lubricating oil. In this case, it is considered that lubricating oil sequentially discharged from the oil drain path and the separated refrigerant gas are less likely to be mixed with each other, allowing lubricating oil which is not strongly mixed with refrigerant, the vane groove and to supply the sliding portion and achieve a better low noise and durability.

However, if a space used for storing lubricating oil is provided in the casing of the oil separator as described above, the oil separator becomes larger or expensive to produce. As the oil separator becomes larger, the volume of the discharge chamber decreases, whereby discharge pulsation may occur, and the entire compressor becomes larger, deteriorating mountability on a vehicle or the like. In addition, a complex production results in an increase in production costs.

The present invention has been made in view of the conventional situation described above, and an object of the invention is to provide a compressor which can be lubricated sufficiently, is less susceptible to exhaust pulsation and capable of reducing and reducing the exhaustion To achieve production costs.

SUMMARY OF THE INVENTION

A compressor according to the present invention has: a housing; a compression mechanism accommodated in the housing, which together with the housing forms a suction chamber, an outlet chamber and a compression chamber and is adapted to suck refrigerant from the suction chamber into the compression chamber, to compress the refrigerant and to discharge the refrigerant into the discharge chamber; an oil separation mechanism provided in the discharge chamber and adapted to separate lubricating oil from the refrigerant and to store the lubricating oil in the discharge chamber; and an oil supply mechanism that is adapted to guide the lubricating oil from the discharge chamber to the compression mechanism. The housing has a housing body having a circumferentially extending inner peripheral surface, a first partition wall provided in the housing body and adapted to separate the compression chamber and the outlet chamber, and a second partition wall coupled to the first partition wall and having the oil separation mechanism. The oil separation mechanism has an oil separation chamber formed in the second partition wall and adapted to separate the lubricating oil from the refrigerant discharged from the compression chamber, and an oil drain path adapted to connect the oil separation chamber to the discharge chamber. The oil supply mechanism has an oil supply port formed in the second partition wall and configured to vertically downwardly open to receive the lubricating oil from the discharge chamber. The oil drain path has a first flow path formed by penetrating the second partition wall and configured to open from the oil separation chamber toward the first partition wall and a second flow path formed in at least one of the first partition wall and the second flow path Partition is recessed and is formed by cooperation of the first partition wall and the second partition wall so as to be connected to the first flow path. An exit of the second flow path is located in a vertical direction at a higher level than an entrance of the second flow path, avoiding a direction facing the oil supply port.

In the compressor according to the present invention, the first partition wall and the second partition wall of the housing are coupled together, and the oil drain path is formed by the first flow path and the second flow path. The first flow path is formed by penetrating the second partition wall and is configured to extend from the oil separation chamber in the direction toward the first partition wall. Therefore, lubricating oil discharged from the oil separation chamber first collides with the first partition and its power is weakened.

In addition, the second flow path is recessed in at least one of the first partition wall and the second partition wall, is formed by the cooperation of the first partition wall and the second partition wall, and is connected to the first flow path. The exit of the second flow path is at a higher level in the vertical direction than the inlet of the second flow path. Therefore, the direction in which the lubricating oil is discharged from the exit of the second flow path does not point in the direction toward the oil supply port.

As a result, in the compressor, even if a large amount of lubricating oil is stored in the lubricating oil discharge chamber, lubricating oil discharged from the oil separation chamber in turn tends less to suck the lubricating oil out of the discharge chamber and, in particular, the lubricating oil around the oil supply port. Therefore, the refrigerant in the discharge chamber is less liable to be mixed again with the lubricating oil in the discharge chamber, and the lubricating oil tends to be stored in the discharge chamber almost without being mixed with the refrigerant, the compression mechanism 5 through the oil supply port 75c to be fed. As a result, the compression mechanism in the compressor is sufficiently lubricated. Thus, the compressor is less susceptible to noise and vibration and has a high durability and low noise.

In addition, in the compressor, the second partition is not enlarged and is easy to work with. Thus, the compressor makes it easy to prevent exhaust pulsation by allowing the exhaust chamber to have a large volume and makes it possible to downsize the entire compressor and achieve a high mounting performance on a vehicle or the like. In addition, the compressor, which is easy to handle, reduce production costs.

Thus, according to the present invention, the compressor can be lubricated sufficiently, is less prone to exhaust pulsation, and is capable of achieving downsizing and reduction of production costs.

Preferably, the exit of the second flow path is placed opposite the inner peripheral surface of the housing body. In this case, too, the force of the lubricating oil, which is discharged in order from the second flow path, is weakened by colliding with the inner peripheral surface of the case body. This makes it easy to obtain advantageous effects of the present invention.

If a normal is defined at a position where the exit of the second flow path opposes the inner peripheral surface of the housing body, preferably, the second flow path intersects the normal at an acute angle. In this case, the lubricating oil, which is discharged from the second flow path in order, is guided along the inner peripheral surface of the case body. This makes it easy to obtain advantageous effects of the present invention.

The housing may include a cylinder block in which a cylinder chamber is formed, the housing body configured to surround the cylinder block, a first partition wall configured to form the exhaust chamber between the cylinder block and the housing body, and the second partition wall to have. The compression mechanism can be a rotor which is installed rotatably about an axis of rotation in the cylinder chamber, with a number of vane grooves and vanes formed therein, which are installed in advance / retractable in the respective vane grooves. The compression mechanism may form the compression chamber defined by a surface of the cylinder chamber, an inner peripheral surface of the cylinder chamber, another surface of the cylinder chamber, an outer circumferential surface of the rotor, and the respective vanes. A back pressure chamber may be provided between each of the wings and the corresponding wing groove / wing groove. Then, the oil supply port may be connected by a Gegendruckfließweg with the back pressure chambers. In this case, the present invention may be embodied as a wing compressor.

The first partition may be a side plate configured to form a surface of the cylinder chamber. In addition, the first partition may be a seal.

BRIEF DESCRIPTION OF THE DRAWINGS

1 FIG. 10 is a sectional view of a vane compressor according to Embodiment 1. FIG.

2 is a sectional view of the wing compressor according to embodiment 1 along the line II-II 1 ,

3 is an enlarged sectional view of a main part of the wing compressor 1 according to embodiment 1.

4 is a sectional view of the wing compressor according to embodiment 1 taken along the line IV-IV 3 ,

5 is a sectional view of the wing compressor according to embodiment 1 taken along the line VV 1 ,

6 FIG. 10 is a rear view of a gasket in the wing compressor of Embodiment 1. FIG.

7 FIG. 10 is a rear view of a cover plate in the wing compressor of Embodiment 1. FIG.

8th is a partial sectional view similar to 4 and shows a wing compressor according to Embodiment 2.

9 is a partial sectional view similar to 4 and shows a wing compressor according to Embodiment 3.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Embodiments 1 to 3 embodying the present invention will be described below with reference to the drawings. In the following description, it is assumed that the left side of 1 The front of the compressor is the same as the right side of the compressor 1 the back of the compressor corresponds. It is also believed that the top of 1 the top of the compressor while the bottom of 1 the bottom of the compressor corresponds. In 2 and the following figures are then the front, rear, upper and lower directions with respect to 1 expelled. The front-rear direction and the top-bottom direction in the embodiments 1 to 3 show the directions of a compressor according to the present invention when the compressor is mounted on a vehicle where the top-bottom direction corresponds to a vertical direction, but the installation position of the compressor according to the present invention is appropriately changed depending on the vehicle on which the compressor is mounted, and the front-rear direction and the top-bottom direction in the embodiments 1 to 3 are exemplary and not restrictive.

[Embodiment 1]

An in 1 Shown electric wing compressor (hereinafter simply referred to as a "compressor") according to embodiment 1 is an example of a concrete form of the compressor according to the present invention. The compressor has a housing 1 , a motor mechanism 3 , a compression mechanism 5 , an oil separation mechanism 7 and an oil supply mechanism 9 , The engine mechanism 3 drives the compression mechanism 5 by putting it in the case 1 is housed. Because he is in the case 1 housed forms the compression mechanism 5 together with the housing 1 a suction chamber 11 , an outlet chamber 13 and compression chambers 15 , The compression mechanism 5 then sucks refrigerant from the suction chamber 11 in the compression chambers 15 , compresses the refrigerant and discharges the compressed refrigerant into the discharge chamber 13 , The oil separation mechanism 7 which is in the outlet chamber 13 is installed, lubricating oil separates from the refrigerant and stores the separated lubricating oil in the discharge chamber 13 , The oil supply mechanism 9 directs the lubricating oil from the outlet chamber 13 to the compression mechanism 5 ,

In particular, the housing has 1 a drive housing 17 , a seal 43 , a compressor housing 19 , a first side plate 21 , one cylinder block 23 , a second side plate 25 , a seal 59 and a cover plate 27 , The compressor housing 19 is associated with a housing body according to the present invention, the second side plate 25 and the seal 59 are associated with a first partition according to the present invention and the cover plate 27 is associated with the second partition according to the present invention.

A cylindrical peripheral wall 17a of the drive housing 17 extends in the axial direction from a front end side to a rear end side. The peripheral wall 17a is at the front end side by a front wall 17b closed and has an opening 17c at the rear end side. The also serving as a motor chamber suction chamber 11 is in the drive housing 17 shaped. One with the suction chamber 11 connected inlet connection 17d is in the peripheral wall 17a shaped. A warehouse 29 is on the front wall 17b provided and a rotating shaft 31 is in the warehouse 29 installed rotatable about a rotation axis X1. The inlet connection 17d is connected by an unillustrated tube with an evaporator. The compressor, a condenser, an expansion valve and the evaporator form an air conditioning apparatus of the vehicle. The refrigerant passing through the evaporator passes through the inlet port 17d in the suction chamber 11 sucked.

A stator 33 is on an inner side of the peripheral wall 17a of the drive housing 17 fixed and a motor rotor 35 is on the rotating shaft 31 fixed. The motor rotor 35 is in the stator 33 placed. A connection terminal 37 is on the front wall 17b fixed and the connection terminal 37 has lead wires 39 extending from the outside into the suction chamber 11 to the stator 33 extend. The wires 39 have a cluster block 41 within the peripheral wall 17a , The stator 33 , the motor rotor 35 , the connection terminal 37 , the wires 39 and the accumulation block / cluster block 41 shape the engine mechanism 3 ,

The compressor housing 19 is at a rear end of the drive housing 17 fixed by several screws, not shown. A peripheral wall 19a with a cylindrical shape extending in the axial direction from a front end side to a rear end side of the compressor housing 19 , The peripheral wall 19a is at a rear end side by a rear wall 19b closed and has an opening at the front end side. The peripheral wall 19a has an inner peripheral surface 19d which extends in a circumferential direction. The inner peripheral surface 19d is coaxial with the axis of rotation X1.

An opening 19c of the compressor housing 19 is with the opening 17c of the drive housing 17 coupled and closes both the drive housing 17 as well as the compressor housing 19 , The seal 43 is between the opening 17c of the drive housing 17 and the opening 19c of the compressor housing 19 intended. In addition, the first side plate 21 on the compressor housing 19 together with the drive housing 17 at the side of the opening 19c fixed. The first side plate 21 defines the suction chamber 11 between the drive housing 17 and the cylinder block 23 by extending in a radial direction and separating the compression chamber 15 and the suction chamber 11 from each other. An O-ring 45 is between the first side plate 21 and the compressor housing 19 intended. A shaft hole 21a is in the first side plate 21 coaxial with the bearing 29 shaped. The rotating shaft 31 is through the shaft hole 21a plugged.

The cylinder block 23 , the second side plate 25 and the cover plate 27 are in the compressor housing 19 accommodated. The cylinder block 23 and the second side plate 25 are on a back surface of the first side plate 21 through several screws 47 attached, as in 2 shown. The cylinder block 23 is from the front and from behind through the first side plate 21 and the second side plate 25 trapped, as in 1 shown. The second side plate 25 is in the inner peripheral surface 19d of the compressor housing 19 fitted. An O-ring 48 is between the second side plate 25 and the inner peripheral surface 19d intended. A shaft hole 25a is in the second side plate 25 coaxial with the bearing 29 and the shaft hole 21a shaped. The rotating shaft 31 is also through the shaft hole 25a plugged.

A cylinder chamber 23a is in the cylinder block 23 shaped as in 2 shown. The cylinder chamber 23a is through the back surface of the first side plate 21 and a front surface of the second side plate 25 closed, as in 1 shown. A rotor 49 is integral with the rotating shaft 31 between the first side plate 21 and the second side plate 25 fixed. The rotor 49 is configured to rotate about the axis of rotation X1 in the cylinder chamber 23a to be rotatable. Several wing grooves / wing grooves 49a are in the rotor 49 shaped as in 2 shown. wing 51 are advanceable / retractable in the corresponding wing grooves / wing grooves 49a Installed.

There is also a suction passage 23b and a suction port 23c in the cylinder block 23 shaped. The suction passage 23b extends in the front-rear direction parallel to the rotation axis X1. The suction passage 23b is through the suction port 23c with the cylinder chamber 23a connected. Furthermore, in the cylinder block 23 together with the inner peripheral surface 19d of the compressor housing 19 an outlet space 23d shaped. The outlet space 23d is through an outlet port 23e with the cylinder chamber 23a connected. An outlet membrane valve / outlet flap valve 53 , which is adapted to the outlet port 23e to open and close and an outlet bracket 55 , which is adapted to an opening dimension of the outlet diaphragm valve / outlet flap valve 53 restrict are in the outlet space 23d intended. The outlet diaphragm valve / outlet flap valve 53 and the outlet bracket 55 are by a screw 57 on the cylinder block 23 fixed.

As in 1 shown, becomes a suction passage 21c , which is adapted to the suction chamber 11 and the suction passage 23b to connect with each other, by penetrating the first side plate 21 shaped. The seal 59 is between the second side plate 25 and the cover plate 27 intended. The second side plate 25 , the seal 59 and the cover plate 27 are by several screws 76 assembled and fixed as in 3 to 5 shown. The second side plate 25 , the seal 59 and the cover plate 27 Form the outlet chamber 13 between the cylinder block 23 and the compressor housing 19 by extending in the radial direction and separating the compression chamber 15 and the outlet chamber 13 from each other.

An introductory passage 25b , which is adapted to the outlet space 23d with the oil separation chamber described later 65 To connect is by penetrating the second side plate 25 , the seal 59 and the cover plate 27 shaped. The first side plate 21 , the cylinder block 23 , the second side plate 25 , the rotor 49 , the wings 51 , the outlet diaphragm valve / outlet flap valve 53 , the outlet bracket 55 and the screw 57 shape the compression mechanism 5 , The compression mechanism 5 shapes the compression chamber 15 passing through the front surface of the cylinder chamber 23a an inner circumferential surface of the cylinder chamber 23a , the back surface of the cylinder chamber 23a , the outer circumferential surface of the rotor 49 and the wings 51 is defined. A back pressure chamber 61 is between each wing groove / wing groove 49a and the associated wing 51 intended.

As in 5 shown are the second side plate 25 and the cover plate 27 about the seal 59 in an annular coupling area 73 coupled together. An intermediate pressure chamber 69 is between the second side plate 25 and the cover plate 27 shaped closer to the side of the rotation axis X1 than the coupling portion 73 , As in 3 and 4 shown, the intermediate pressure chamber 69 from a part of the second side plate 25 and a part of the cover plate 27 formed, which are spaced apart in the direction of the rotation axis X1. Viewed in the direction of the rotation axis X1 is the intermediate pressure chamber 69 placed so that it covers at least part of the back surface of the cylinder chamber 23a overlaps.

As in 3 to 5 shown is the oil separation mechanism 7 on the cover plate 27 intended. The oil separation mechanism 7 has a cylinder element 63 , the oil separation chamber 65 and an oil drainage path 71 , As in 3 shown, has the oil separation chamber 65 a columnar hollowed upper chamber 65a and a lower chamber 65b , which with the upper chamber 65a at an underside of the upper chamber 65a connected, coaxial with the upper chamber 65a is columnar hollowed out and configured to have a slightly smaller diameter than the upper chamber 65a to have. As in 5 shown are the upper chamber 65a and the lower chamber 65b formed with an upper part which is slightly inclined inwardly with respect to an up-down direction slightly on the left side of the cover plate 27 in 5 ,

The cylinder element 63 , which has a cylindrical shape, is at an upper end of the upper chamber 65a fixed. As in 3 shown, the cylinder element 63 from a section with a large diameter 63a and a small diameter section 63b shaped, with the section of large diameter 63a configured to have a large diameter and into the upper chamber 65a to be pressed while the section of small diameter 63b integral with and coaxial with the large diameter portion 63a under the large diameter section 63a is shaped and configured to have a slightly smaller diameter than the large diameter portion 63a to have. The refrigerant coming from the outlet space 23d through the introductory passage 25b to the oil separation chamber 65 is circulated in the annular space which flows from the small diameter portion 63b and an inner peripheral surface of the upper chamber 65a is formed. As a result, a centrifugal force acts on the refrigerant and causes the lubricating oil contained in the refrigerant to separate from the inner peripheral surface of the upper chamber 65a drips off and gets to the lower chamber 65b emotional.

As in 1 shown is an outlet port 19e in the peripheral wall 19a of the compressor housing 19 shaped. The outlet connection 19e is connected by a non-illustrated tube with a capacitor. The refrigerant in the oil separation chamber 65 from which the lubricating oil is deposited is through the outlet port 19e discharge to the capacitor.

As in 4 shown becomes a through hole 71a in the cover plate 27 at a lower end of the lower chamber 65b shaped, which is perpendicular to an end face of the seal 59 extends, which is the coupling area 73 is. The through hole 71a extends in the tangential direction from a direction in which the refrigerant in the lower chamber 65b circulated. As in 6 shown has the seal 59 a flat end surface configured to be the through hole 71a the cover plate 27 confront. The through hole 71a is the first flow path. Moreover, as in 4 and 7 shown a linear groove / groove 71c in the cover plate 27 let in, which with the through hole 71a is connected and extends linearly to an outer peripheral surface. The linear groove / groove 71c is a recessed section. The surfaces are joined together so that an end surface of the cover plate 27 with the linear groove / groove formed therein 71c and an end surface of the gasket 59 facing each other and the linear groove / groove 71c forms a second flow path according to the present invention.

One end of the linear groove / groove 71c is one with the through hole 71a connected inlet 71b and another end is an exit 71d , which is to the outlet chamber 13 opens. As in 7 shown is the exit 71d at a higher level in the vertical direction than the inlet 71b , That is, the linear groove / groove 71c extends while being inclined at an angle of θ ° with respect to a horizontal direction when the compressor is mounted on the vehicle. As a result, the linear groove / groove extends 71c , as in 5 shown in a radial direction away from the oil supply port described later 75c , In addition, the exit 71d the linear groove / groove 71c , as in 4 and 5 shown the inner peripheral surface 19d of the compressor housing 19 placed opposite, being spaced only about a few millimeters therefrom. In particular, if a normal L is defined at a position where the exit 71d the inner peripheral surface ( 19d ), the linear groove / groove intersects 71c the normal L at an acute angle, as in 5 shown. The through hole 71a and the linear groove / groove 71c shape the oil drainage path 71 ,

In addition, the first and second oil flow path 75a and 75b in the cover plate 27 shaped. The first oil flow path 75a is through the oil supply port 75c at a lower end with a bottom of the outlet chamber 13 connected and extends upward, wherein it approaches the axis of rotation X1. The second oil flow path 75b extends to the intermediate pressure chamber 69 while at the top end of the first oil flow path 75a is consistent. As a result, the lubricating oil in the outlet chamber 13 through the oil supply port 75c in the first and second oil flow path 75a and 75b taken and to the intermediate pressure chamber 69 directed. The first and second oil flow paths function here 75a and 75b as throttle channels and direct the lubricating oil to the intermediate pressure chamber 69 so that the pressure in the intermediate pressure chamber 69 lower than in the outlet chamber 13 but higher than in the suction chamber 11 is.

As in 1 and 3 shown becomes a connection path 77 , which is adapted to the intermediate pressure chamber 69 and the back pressure chamber 61 connect to each other by penetrating the second side plate 25 shaped. In addition, an oil groove / oil groove 25c , which is annular and coaxial with the axis of rotation X1, in the second side plate 25 shaped. Furthermore, as in 1 shown, an oil groove / oil groove 21b , which is annular and coaxial with the axis of rotation X1, in the first side plate 21 shaped. The oil grooves / oil grooves 21b and 25c are with the bottom of each wing groove / wing groove 49a regardless of the rotation of the rotor 49 , The oil supply connection 75c , the first and second oil flow path 75a and 75b , the intermediate pressure chamber 69 , the connection path 77 , and the oil groove / oil groove 25c form a backpressure flow path. The oil supply connection 75c , the first and second oil flow path 75a and 75b , the intermediate pressure chamber 69 , the connection path 77 , the oil groove / oil groove 25c , the back pressure chamber 61 and the oil groove / oil groove 21b form the oil supply mechanism 9 ,

In the compressor is the engine mechanism 3 in operation, if the in 1 shown stator 33 electrical power is supplied, and causes the rotating shaft 31 rotated about the rotation axis X1. As a result, the compression mechanism is 5 in operation and the rotor 49 rotates in the cylinder chamber 23a , This move / pull in the cylinder chamber 23a the wings 51 along with the rotation of the rotor 49 from the / in the corresponding wing grooves / Flügelnuten 49a next previous. As a result, the refrigerant from the suction chamber 11 in the compression chamber 15 sucked, in the compression chamber 15 compressed and in the outlet chamber 13 discharged.

This will in the oil separation chamber 65 the oil separation mechanism 7 the lubricating oil is separated from the refrigerant. The refrigerant from which the lubricating oil has been deposited, the capacitor outside through the outlet chamber 13 and the exit port 19e fed. The lubricating oil in the oil separation chamber 65 is, by the fact that it through the oil drainage 71 flows through, in the lower area of the outlet chamber 13 saved.

Meanwhile, the second side plate remains in the compressor 25 and the cover plate 27 together in the coupling area 73 coupled and the oil drainage path 71 gets through the through hole 71a and the linear groove / groove 71c shaped. The through hole 71a is by penetrating the cover plate 27 shaped and extends from the lower chamber 65b the oil separation chamber 65 to the end surface of the gasket 59 which the coupling area 73 is. As a result, the lubricating oil, which in turn collides with the lower chamber 65b the oil separation chamber 65 unloading, as the very first with the end face of the seal 59 , whereby its flow direction is changed and its power is weakened.

In addition, the linear groove / groove 71c in the coupling area 73 the cover plate 27 admitted. The exit 71d the linear groove / groove 71c is at a higher level in the vertical direction than the inlet 71b , As a result, the linear groove is groove 71c with the through hole 71a connected and extends so that the exit 71d opens in a direction different from the direction toward the oil supply port 75c is. The lubricating oil, which consists of the linear groove / groove 71c is discharged in turn, is in such a way in the outlet chamber 13 discharge it away from the oil supply port 75c emotional. Especially since the exit 71d the linear groove / groove 71c the inner peripheral surface 19d of the compressor housing 19 is placed opposite, collides in the present compressor, the lubricating oil, which from the linear groove / groove 71c is discharged in turn, even with the inner peripheral surface 19d , That is, the flow of oil through the drainage path 71 flowing lubricating oil is changed by flowing through a curved path before entering the outlet chamber 13 is stored and the flow is weakened by at least two-fold collision with wall surfaces. In addition, since the linear groove / groove 71c the normal L intersects at an acute angle, the lubricating oil coming out of the linear groove / groove 71c in turn, along the inner peripheral surface 19d guided.

As a result, in the present compressor, the lubricating oil discharged from the oil separation chamber tends 65 is discharged in turn, less so, the lubricating oil in the outlet chamber 13 to swirl / blow or disturb, even if a large amount of lubricating oil in the outlet chamber 13 is stored. This causes the refrigerant in the outlet chamber 13 less likely to come back with the lubricating oil in the outlet chamber 13 to mix. Especially since the exit 71d the linear groove / groove 71c not in the direction to the oil supply port 75c is aligned, that is from the exit 71d discharged lubricating oil is prevented, the refrigerant gas and the lubricating oil around the oil supply port 75c to disturb around. As a result, the lubricating oil tends to do so, as it does in the outlet chamber 13 almost without being mixed with the refrigerant, the compression mechanism 5 through the oil supply port 75c to be fed. In particular, this is achieved through the oil supply port 75c absorbed lubricating oil the intermediate pressure chamber 69 through the first and second oil flow path 75a and 75b and becomes the back pressure chamber 61 from the intermediate pressure chamber 69 through the oil groove / oil groove 25c and the connection path 77 fed. The lubricating oil in the back pressure chamber 61 lubricates the sliding portions between the respective vane grooves / vane grooves 49a and wings 51 as well as sliding sections between the respective wings 51 and the cylinder chamber 23a , In addition lubricates the lubricating oil in the back pressure chamber 61 the shaft holes 21a and 25a by passing through the oil grooves / oil grooves 21b and 25c passes. In this way, the present compressor allows the compression mechanism 5 is sufficiently lubricated. Thus, the compressor is less susceptible to noise and vibration and has a high durability and low noise. In addition, every wing can 51 be stably pressed by hydraulic pressure, as compared to when the refrigerant gas is mixed, whereby it is possible to rattle the wing 51 to prevent and to improve the low noise of the compressor.

As an end face of the cover plate 27 which the linear groove / groove 71c has, and an end surface of the seal 59 In addition, in the present compressor, the cover plate is placed facing each other and the second flow path is formed by connecting the end surfaces to each other 27 not bigger and is easy to work with. Thus, the compressor makes it easy to prevent exhaust pulsation by allowing the exhaust chamber 13 has a large volume and makes it possible to downsize the entire compressor and to achieve a good mountability on a vehicle or the like. In addition, the compressor, which is easy to handle, reduce production costs.

Thus, compressor can be sufficiently lubricated, is less prone to exhaust pulsation, and is capable of achieving downsizing and reduction of production cost.

[Embodiment 2]

In the compressor according to Embodiment 2, the cover plate has 27 a flat end surface on an outer peripheral surface of the through hole 71a , as in 8th shown. In addition, a through hole 71e leading to the through hole 71a in the cover plate 27 fits, by penetrating the poetry 59 shaped. A linear groove / groove 71f , which has a linear shape, becomes in the second side plate 25 Shaped by having the through holes 71a and 71e connected is. The surfaces are joined together so that the end face of the seal 59 with the through hole formed therein 71e and an end surface of the second side plate 25 with the linear groove / groove formed therein 71f facing each other. the through hole 71e and the linear groove / groove 71f form the second flow path according to the present invention. The through hole 71a , the through hole 71e and the linear groove / groove 71c form the oil drainage path 71 ,

The rest of the configuration is similar to Embodiment 1. The present compressor achieves similar functions and effects as those of Embodiment 1.

[Embodiment 3]

In the compressor according to Embodiment 2, the cover plate has 27 a flat end surface on an outer peripheral surface of the through hole 71a , as in 9 shown. Next to it also has the second side plate 25 a flat end surface on an outer circumferential surface. A linear notch / groove 71g is in the seal 59 shaped, passing with the through hole 71a in the cover plate 27 connected is. The surfaces are joined together so that an end surface of the cover plate 27 and an end surface of the second side plate 25 two end faces of the seal each 59 in which the notch / groove 71g is shaped, facing. The notch / groove 71g is according to the present invention the second flow path associated. The through hole 71a and the notch / groove 71g form the oil drainage path 71 ,

The rest of the configuration is similar to Embodiment 1. The present compressor also achieves similar functions and effects as those of Embodiment 1.

Of course, although the present invention has been described in accordance with Embodiments 1 to 3, the invention is not limited to the above-described Embodiments 1 to 3, but may be appropriately modified in the application without departing from the gist of the invention.

For example, the second flow path may be formed in a curved or bent shape, whereas in the embodiments 1 through 3, the second flow path may be formed by the linear groove 71c , the linear groove / groove 71f , or the notch / groove 71g linear shape is formed in a linear shape.

In addition, the number of blades is not limited to three and may be, for example, two or four, whereas in the compressor according to the embodiments 1 to 3 three blades are provided.

In addition, the present invention may be embodied as a scroll compressor / scroll compressor or the like, whereas in embodiments 1 through 3, the present invention is embodied as a wing compressor.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• JP 7-12072 [0002]
• JP 2010-31757 [0005]

Claims (6)

Compressor with: a housing ( 1 ); one in the housing ( 1 ) recorded compression mechanism ( 5 ), which together with the housing ( 1 ) a suction chamber ( 11 ), an outlet chamber ( 13 ) and a compression chamber ( 15 ) is adapted and adapted to refrigerant from the suction chamber ( 11 ) into the compression chamber ( 15 ) to compress the refrigerant and the refrigerant in the outlet chamber ( 13 ) to let go; an oil separation mechanism ( 7 ), which in the outlet chamber ( 13 ) is adapted and adapted to separate lubricating oil from the refrigerant and the lubricating oil in the outlet chamber ( 13 ) save; and an oil supply mechanism ( 9 ), which is adapted to the lubricating oil from the outlet chamber ( 13 ) to the compression mechanism ( 5 ), the housing ( 1 ) a housing body ( 19 ) which has an inner peripheral surface extending in a circumferential direction (US Pat. 19d ), a first partition ( 25 . 59 ), which in the housing body ( 19 ) is adapted and adapted to the compression chamber ( 15 ) and the outlet chamber ( 13 ) and a second partition wall ( 27 ), which with the first partition ( 25 . 59 ) and the oil separation mechanism ( 7 ), the oil separation mechanism ( 7 ) an oil separation chamber ( 65 ), which in the second partition ( 27 ) is adapted and adapted to the lubricating oil from that from the compression chamber ( 15 ) separated refrigerant, and an oil drain path ( 71 ), which is adapted to the oil separation chamber ( 65 ) with the outlet chamber ( 13 ), the oil supply mechanism ( 9 ) an oil supply port ( 75c ), which in the second partition ( 27 ) and is configured to open vertically downwards to remove the lubricating oil from the outlet chamber (12). 13 ), the oil drainage path ( 71 ) a first flow path ( 71a ), which by penetrating the second partition ( 27 ) and is configured to move away from the oil separation chamber ( 65 ) towards the first partition ( 25 . 59 ) and a second flow path ( 71c ), which in at least one of the first partition wall ( 25 . 59 ) and the second partition ( 27 ) and by the interaction of the first partition ( 25 . 59 ) and the second partition ( 27 ) is shaped so as to communicate with the first flow path ( 71a ) and an exit ( 71d ) of the second flow path ( 71c ) in a vertical direction at a higher level than an entry ( 71b ) of the second flow path ( 71c ), avoiding a direction which is the oil supply port ( 75c ) is facing. A compressor according to claim 1, wherein the outlet ( 71d ) of the second flow path ( 71c ) of the inner circumferential surface ( 19d ) of the housing body ( 19 ) is placed opposite one another. A compressor according to claim 1 or 2, wherein if a normal (L) is defined at a position where the exit ( 71d ) of the second flow path ( 71c ) of the inner circumferential surface ( 19d ) of the housing body ( 19 ), the second flow path ( 71c ) cuts the normal (L) at an acute angle. A compressor according to any one of claims 1 to 3, wherein: the housing ( 1 ) a cylinder block ( 23 ), in which a cylinder chamber ( 23a ), the housing body ( 19 ) which is configured to block the cylinder block ( 23 ), the first partition wall ( 25 . 59 ), which is configured to the outlet chamber ( 13 ) between the cylinder block ( 23 ) and the housing body ( 19 ), and the second partition wall ( 27 ) Has; the compression mechanism ( 5 ) a rotor ( 49 ) which rotates about an axis of rotation in the cylinder chamber ( 23a ) having a number of vane grooves ( 49a ) and wings ( 51 ) which are installed in the respective wing grooves / flutes advancing / retractable; the compression mechanism ( 5 ) the compression chamber ( 15 ) formed by an area of the cylinder chamber ( 23a ), an inner peripheral surface of the cylinder chamber ( 23a ), another surface of the cylinder chamber ( 23a ), an outer peripheral surface of the rotor ( 49 ) and the corresponding wings ( 51 ) is defined; a back pressure chamber ( 61 ) between each of the wings ( 51 ) and the corresponding wing groove / wing groove ( 49a ) is provided; and the oil supply connection ( 75c ) by a counterpressure flow path ( 75a . 75b . 69 . 77 . 25c ) with the back pressure chambers ( 61 ) connected is. A compressor according to claim 4, wherein the first partition ( 25 . 59 ) a side plate ( 25 ), which is configured to a surface of the cylinder chamber ( 23a ). A compressor according to claim 4, wherein the first partition ( 25 . 59 ) a seal ( 59 ) Has.

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