WO2012039109A1

WO2012039109A1 - Scroll type compressor

Info

Publication number: WO2012039109A1
Application number: PCT/JP2011/005156
Authority: WO
Inventors: 裕司河村; 卿在李
Original assignee: 株式会社ヴァレオジャパン
Priority date: 2010-09-21
Filing date: 2011-09-14
Publication date: 2012-03-29
Also published as: CN103109089B; CN103109089A; EP2631484A1; US20130280115A1; JP2012067602A; JP5612411B2; EP2631484A4

Abstract

While using an Oldham mechanism as a spin prevention unit mechanism, an Oldham ring is positively lubricated by keeping a medium mixed with oil on a back surface of a turning scroll, and a compression mechanism is kept compact. In a scroll type compressor in which an Oldham ring (18) is provided between a turning scroll member (11) and a block member (5) that axially supports a drive shaft, a fixed scroll member (10) and the block member (5) hold an annular thrust race (16) that receives a load in an axial direction from the turning scroll member (11) with the thrust race sandwiched therebetween, an end surface of the turning scroll member (11) is slidably brought into close contact with the thrust race (16) on an entire circumference thereof, the thrust race (16) is brought into close contact with the end surface of the block member (5) to the outer side in a radial direction beyond key groove portions (25b, 25c) which are paired and formed on the block member (5), the turning scroll member (11), the thrust race (16), and the block member (5) define a retention space, and the medium mixed with oil is retained in the retention space.

Description

Scroll compressor

The present invention relates to a scroll compressor used in a refrigeration cycle of a vehicle air conditioner, and more particularly to a scroll compressor capable of ensuring the reliability of an anti-rotation mechanism using an Oldham ring.

A scroll type compressor is fixed in a housing and has an end plate and a scroll member that is erected from the end plate, and a fixed scroll member that is opposed to the fixed scroll member and is erected from the end plate and the end plate. A revolving motion of the orbiting scroll member, and the compression chamber formed between the swirl walls of both scroll members moves to the center while reducing the volume to compress the working fluid. To be done.

In such a compressor, a block member (shaft support member) that supports the drive shaft is fixed to the housing on the opposite side of the orbiting scroll member from the side facing the fixed scroll member. 2, an Oldham ring is provided between the block member and the orbiting scroll member to prevent the orbiting scroll member from rotating.
The Oldham ring includes a key portion that is slidably accommodated in a key groove formed in each of the block member and the orbiting scroll member, and is always in sliding contact with the block member and the orbiting scroll member. Therefore, it is necessary to ensure good lubrication.

For this reason, in Patent Document 1, a through hole in which a main bearing for rotatably holding a drive shaft is mounted on a block member, a support portion extending in the radial center at an end of the through hole, and a drive A bearing swing space in which a swing bearing mounted with a swing shaft mounted eccentrically on the shaft, a main body swing space in which a orbiting scroll member (oscillating scroll body) swings, and a bearing swing space A thrust bearing portion that comes into contact with the orbiting scroll main body toward the radially outer side on a surface extending in the radial direction leading to the main body rocking space, and an Oldham ring storage groove formed radially outward of the thrust bearing portion, A block-side key groove formed in a radial direction from the Oldham ring storage portion to a peripheral wall portion of the main body swinging space, and the orbiting scroll member formed in a radial direction perpendicular to the block-side key groove. Sk A block side claw provided with a rail side key groove, an Oldham ring being arranged in the Oldham ring storage groove, a block side claw slidably inserted in the block side key groove formed in the block member, and a turning scroll member The scroll side claw is formed in a scroll side keyway, and has a scroll side claw that is slidably inserted.

An oil space that is arranged between the drive shaft and the support, is defined by the drive shaft and the block, and communicates with the oil reservoir, and is defined by inserting the swing shaft into the swing bearing. The bearing space and the oil guide hole communicating with the oil space and the bearing space are provided, and the oil space and the oil guide hole → the bearing space → Oscillating bearing → Abutting sliding part between the oscillating shaft and oscillating bearing → Bearing oscillating space → Thrust bearing part → Lubricating oil path for flowing lubricating oil through the main body oscillating space is formed, and the orbiting scroll member Providing an oil guide that extends radially outward from the main body swinging space for housing the orbiting scroll member to the block side key groove into which the block side claw of the Oldham ring is slidably inserted along the swing direction. By A configuration is disclosed in which lubricating oil in the main body swinging space is pushed radially outward along the oil guide by the swinging motion of the orbiting scroll member, and oil is actively supplied to the block side keyway. Yes.

Further, Patent Document 2 suppresses inconveniences that the sliding side of the Oldham ring is not sufficiently filled with the lubricating oil on the back side of the orbiting scroll member, and the Oldham ring's vibration and impact sound are generated. Therefore, a back pressure chamber is provided on the back of the orbiting scroll member, and the pressure of the back pressure chamber is adjusted by a valve device provided between the suction chamber and the orbiting scroll member is pressed toward the fixed scroll side. A configuration is disclosed in which the back pressure chamber is filled with lubricating oil to prevent wear of the Oldham ring disposed therein.

Japanese Patent Application Laid-Open No. 8-219061 JP 2006-266123 A

However, in the scroll compressor of Patent Document 1, the oil supplied from the clearance of the bearing of the orbiting scroll passes through the key groove of the Oldham ring of the orbiting scroll after passing through the thrust sliding surface. Since it is guided to the outside suction area and does not have a structure that holds oil, the oil that has flowed into the main body swinging space does not stay there and is directly sucked into the compression mechanism. It has a configuration. For this reason, there is a concern that the lubrication between the block-side claws and the block-side keyway of the Oldham ring is not sufficiently performed.
In particular, in a vehicular compressor in which the compressor is placed sideways, the suction passage of the compression mechanism may be provided in the lower part, so that the sliding part (the upper Oldham ring claw and keyway etc.) above the compressor is provided. There is a possibility that sufficient oil may not be supplied, and there is a concern about insufficient lubrication.

In this regard, in Patent Document 2, since the orbiting scroll member is completely floated by the pressure in the back pressure chamber and is in close contact with the fixed scroll member, the gap between the block member (main bearing member) and the orbiting scroll, Even if the back pressure leaks to the outside in the radial direction of the end plate of the orbiting scroll member through the key groove of the Oldham ring, the oil in the back pressure chamber can be held. However, in such a system that presses against the fixed scroll member by the back pressure of the orbiting scroll member, the pressure on the back surface of the orbiting scroll member is increased with respect to the suction pressure region of the compression mechanism. It is necessary to cover the compression space including the pressure region with the end plate of the orbiting scroll, and the end plate becomes very large with respect to the wrap of the orbiting scroll member. There is an inconvenience that the outer diameter becomes large.

The present invention has been made in view of such circumstances, and even when an Oldham mechanism is used as an anti-rotation mechanism, oil or oil-mixed working fluid can be retained to some extent on the back surface of the orbiting scroll member. The main object is to provide a scroll type compressor that can form a space, reliably lubricate the Oldham ring, and maintain the compactness of the compression mechanism.
Another object is to suppress fluttering of the Oldham ring disposed between the orbiting scroll member and the block member.

In order to achieve the above object, a scroll compressor according to the present invention includes a fixed scroll member whose movement in the rotational direction and the axial direction is restricted with respect to the inside of the housing, a drive shaft that transmits rotational power, and the fixed compressor. An orbiting scroll member that revolves around the axis of the drive shaft by being connected to the drive shaft via an eccentric shaft that is disposed opposite the scroll member and is eccentric with respect to the axis of the drive shaft; A block member that is provided on the opposite side of the orbiting scroll member from the opposite side of the fixed scroll member (is integrally formed with the housing or fixed to the housing) and supports the drive shaft; It is arranged between the orbiting scroll member and the block member, and can slide in a plurality of key grooves formed on the back surface of the orbiting scroll member. A plurality of key portions engaging with each other, and a plurality of key portions slidably engaged with a plurality of key groove portions formed on an end face of the block member facing the orbiting scroll member; A rotation prevention member that prevents rotation of the orbiting scroll member by engaging with each of the key groove portions, and compression formed by the fixed scroll member and the orbiting scroll member by the revolving motion of the orbiting scroll member In a scroll type compressor that compresses the medium by moving the chamber toward the center while reducing the volume, an annular thrust trace that receives the orbiting scroll member in the axial direction between the fixed scroll member and the block member. Hold the thrust trace across the entire circumference of the end surface of the orbiting scroll member facing it. The thrust trace is brought into close contact with the end surface of the block member to the outside in the radial direction from the key groove portion formed in the block member, and the orbiting scroll member, the thrust trace, and the block A retention space is defined by the members, and the medium (oil or working fluid mixed with oil) after being compressed in the compression chamber is supplied to the retention space to be retained.

Accordingly, the thrust trace is sandwiched between the fixed scroll member and the block member, and the thrust trace is brought into close contact with the thrust trace so as to be slidable over the entire circumference of the end surface of the orbiting scroll member. Since the medium does not leak from between the orbiting scroll member and the thrust trace, and the thrust trace is brought into close contact with the end surface of the block member so as to be radially outward from the key groove formed in the block member. The medium guided to the stationary space through the key groove formed on the medium is not leaked, and the medium after being compressed in the compression chamber in the stationary space defined by the orbiting scroll member, the thrust trace, and the block member ( Oil or oil-mixed working fluid) can be retained and good Oldham ring lubrication is maintained Rukoto is possible. In addition, since the thrust trace is provided between the fixed scroll member and the block member, it is not necessary to cover the compression space including the suction pressure region of the fixed scroll with the end plate of the orbiting scroll, and the outer diameter of the orbiting scroll is reduced. It becomes possible.

Here, as a configuration in which the thrust trace is brought into close contact with the entire circumference of the end surface of the orbiting scroll member facing the thrust trace, a recess is formed on the rear surface of the end plate of the orbiting scroll facing the thrust trace. By doing so, it is preferable to form an annular sliding surface in close contact with the thrust trace so that the sliding surface does not protrude from the thrust trace.
In addition, as a configuration for supplying the medium (oil or working fluid mixed with oil) compressed in the compression chamber to a stationary space defined between the orbiting scroll member, the thrust trace, and the block member, A discharge region for discharging the working fluid compressed in the compression chamber is provided behind the fixed scroll member, and the discharge region and the retention space are communicated with each other via a pressure supply path in which a restriction is formed in the middle. Also good.

Furthermore, the stationary space and the suction path for guiding the working fluid to the compression chamber are communicated via the pressure discharge path, and a pressure regulating valve is provided in the middle of the pressure discharge path, so that the medium in the stationary space is stopped. May be adjusted and the pressure of the stationary space may be maintained at a predetermined pressure set in advance.

As a specific example of the configuration described above, an anti-rotation member is disposed in an Oldham accommodating portion formed in a block portion, and the orbiting scroll is provided so as to project from the ring portion and project from the ring portion through the thrust trace. A pair of key portions slidably engaged with a pair of key grooves formed on the back surface of the member, and a pair of key grooves formed on the block member so as to project from both radial sides of the ring portion And a pair of key portions that are slidably engaged with each other, and the Oldham accommodating portion communicates with the ring portion accommodating portion, the ring portion accommodating portion, and the ring portion accommodating portion. A pair of key grooves projecting on both sides in the radial direction and slidably engaging with each other, and the pressure supply path of the pair of key grooves formed on the block member Communicate with one side and the pressure The discharge path may be other communication with the key groove forming the said pair is formed in the block member.

With such a configuration, the working fluid discharged into the discharge chamber is separated to some extent here, but the separated oil or the working fluid mixed with oil passes through the pressure supply path from the discharge chamber. Is guided to one of the paired key grooves, and then is guided to the other key groove through the ring housing, and then flows out to the suction path through the pressure discharge path. It is possible to supply abundant oil to the sliding part.

As described above, according to the present invention, the annular thrust trace that receives the orbiting scroll member in the axial direction is sandwiched between the fixed scroll member and the block member, and the entire circumference of the end surface of the orbiting scroll member is sandwiched. The thrust traces are brought into close contact with each other and the end face of the block member is brought into close contact with the end surface of the block member radially outside the key groove formed in the block member. Since the retained space is formed and the medium after being compressed in the compression chamber is retained, the Oldham mechanism is adopted as an anti-rotation mechanism, and the back of the orbiting scroll has oil or oil mixed working fluid. The Oldham ring can be reliably lubricated no matter what state the compressor is installed in. Can be performed with it, also, it is possible to maintain the size of the compression mechanism.

In addition, a discharge region for discharging the working fluid compressed in the compression chamber to stop the medium after being compressed in the compression chamber in a space defined between the orbiting scroll member, the thrust trace, and the block member The pressure discharge valve is provided with a pressure regulating valve in the middle of the stationary space and the suction path for guiding the working fluid to the compression chamber. If it is configured to communicate through the path, it is possible to adjust the stationary state of the medium retained in the stationary space by the pressure regulating valve, and it is possible to adjust the stationary space to a desired intermediate pressure.

Further, an anti-rotation member is disposed in the Oldham accommodating portion formed in the block portion, and the anti-rotation member is projected from the ring portion and the ring portion through the thrust trace, and the rear surface of the orbiting scroll member. A pair of key portions that slidably engage with a pair of key grooves formed on the ring portion, and a pair of key grooves formed on the block member that project from both sides in the radial direction of the ring portion so as to be slidable. An Oldham ring having a pair of matching key portions, the Oldham accommodating portion being connected to the ring portion accommodating portion and the ring portion accommodating portion projecting on both sides in the radial direction of the ring portion. In the case where the paired key portions are configured to slidably engage with each other, the pressure supply path communicates with one of the paired key grooves formed on the block member, Discharge route By configuring the lock member to communicate with the other of the pair of key grooves formed in the lock member, the medium (oil or working fluid mixed with oil) compressed in the compression chamber is passed through the sliding portion of the Oldham ring. Since the path is formed, it is possible to supply abundant oil to the sliding portion such as the rotation prevention member regardless of the installation state of the compressor, and it is possible to ensure a good lubrication state. .

FIG. 1 is a cross-sectional view showing an example of the overall configuration of a scroll compressor according to the present invention, including a cut surface taken along the line CC of FIGS. 5 and 6B. FIG. 2 is an exploded perspective view showing components used from the block member to the fixed scroll member of the scroll compressor according to the present invention. FIG. 3A is a cross-sectional view from the fixed scroll member to the block member housed in the housing of the scroll compressor, and is a view cut along the line BB in FIGS. 5 and 6B. is there. FIG. 3B is a diagram of the fixed scroll member of FIG. 3A viewed from the axial direction. FIG. 4 is a view showing the orbiting scroll member, FIG. 4 (a) is a cross-sectional view taken along the line BB in FIGS. 4 (b) and 5, and FIG. It is the figure which looked at the side to do from an axial direction. FIG. 5 is a view of the side of the block member facing the thrust trace as seen from the axial direction. 6A is a cross-sectional view from the orbiting scroll member to the block member in FIG. 3A, and is a view cut along the line BB in FIGS. 5 and 6B. FIG. 6B is a view as seen from the line AA in FIG.

Hereinafter, an embodiment in which an electric compressor in which a compression mechanism and an electric motor are integrated is used as a scroll compressor according to the present invention will be described with reference to the accompanying drawings.

FIG. 1 shows an electric compressor 1 suitable for a refrigeration cycle using a refrigerant as a working fluid. This electric compressor 1 is provided with a compression mechanism 3 on the left side in the figure in a housing 2 made of an aluminum alloy, and an electric motor 4 for driving the compression mechanism on the right side in the figure. Yes. In FIG. 1, the right side in the figure is the front of the compressor, and the left side in the figure is the rear of the compressor.

The housing 2 is provided with a drive shaft 8 that is rotatably supported by

bearings

6 and 7 on a block member (shaft support member) 5 and a front wall portion 2a that are fixed in the middle of the housing.

The compression mechanism 3 is of a scroll type having a fixed scroll member 10 and an orbiting scroll member 11 disposed opposite to the fixed scroll member 10, and the fixed scroll member 10 is a disc-shaped end plate fixed inside the rear portion of the housing 2. 10a, a cylindrical outer peripheral wall 10b provided over the entire periphery along the outer edge of the end plate 10a and erected forward, and from the end plate 10a toward the front inside the outer peripheral wall. It is comprised from the spiral-shaped spiral wall 10c extended in this way.

The orbiting scroll member 11 is composed of a disc-shaped end plate 11a and a spiral spiral wall 11c standing rearward from the end plate 11a, and is formed on the back surface of the end plate 11a. An eccentric shaft 8a provided at the rear end portion of the drive shaft 8 and eccentric with respect to the shaft center of the drive shaft is connected to the boss portion 11b via the bush 12 and the bearing 13, and the shaft center of the drive shaft 8 is centered. It is supported so that it can revolve.

The fixed scroll member 10 and the orbiting scroll member 11 are meshed with each other with their

respective spiral walls

10c and 11c, and the front ends of the respective scroll members are in contact with the

end plates

10a and 11a of the mating scroll member, Therefore, the compression chamber 15 is defined in a space surrounded by the end plate 10 a and the spiral wall 10 c of the fixed scroll member 10 and the end plate 11 a and the spiral wall 11 c of the orbiting scroll member 11.

As shown in FIGS. 2 and 3, a thin plate-shaped annular thrust trace 16 is sandwiched between the outer peripheral wall 10 b of the fixed scroll member 10 and the end surface 5 a of the block member 5. 10 and the block member 5 are abutted via the thrust trace 16.

The thrust trace 16 is formed of a material having excellent wear resistance. The thrust trace 16 is formed in a size having an outer edge shape that matches the outer edge shape of the end surface 5a of the block member 5 to which the thrust trace 16 faces. A central hole 16a through which the boss portion 11b of the scroll member 11 is inserted is formed. The fixed scroll member 10, the thrust trace 16, and the block member 5 are positioned and fixed by positioning pins 9 that are inserted into pin insertion holes 16 c formed in the thrust trace 16.
As shown in FIG. 4, the orbiting scroll member 11 has a slight gap (for example, 0...) From the periphery to the boss portion 11 b so that the periphery is left with a predetermined width (for example, about 2 mm) on the back surface. A recessed portion 11d that is recessed (about 5 mm) is formed (the thickness of the end plate is reduced). The thrust trace 16 is in contact with the entire back surface of the orbiting scroll member 11 by inserting the boss portion 11b of the orbiting scroll member 11 through the central hole 16a. An annular sliding surface 11f having a predetermined width is formed on the rear surface of the end plate 11a so as to surround the recess 11d.
The sliding surface 11f of the orbiting scroll member 11 does not pass the center hole 16a and the notch 16b of the thrust trace 16 due to the revolving motion of the orbiting scroll member 11 (the center hole 16a and the notch 16b are always on the inner side. And is in sliding contact so as not to protrude from the thrust trace 16.
In addition, a key groove portion 11e extending in the radial direction is formed in the recess portion 11d. The key groove portion 11e formed in the recess portion 11d is not formed until it passes the periphery of the end plate 11a (through the sliding surface 11f), and is formed inside the annular sliding surface 11f. .

The block member 5 has a through-hole 5b in the center, and the inner surface thereof is formed in a cylindrical shape having a diameter that increases stepwise. The block member 5 and the block member 5 are separated from the front side farthest from the thrust trace 16. As the drive shaft 8 rotates together with the seal housing portion 22 for housing the seal member 21 that seals between the drive shaft 8, the bearing portion housing portion 23 for housing the bearing 6, and the bush 12. A weight accommodating portion 24 that accommodates the rotating balance weight 19 and an Oldham accommodating portion 25 that is formed from the end surface 5 a of the block member 5 and accommodates an Oldham ring 18 to be described later are formed between the thrust trace 16.

The rotation preventing mechanism of the orbiting scroll member 11 includes an Oldham ring (auto rotation preventing member) 18 and the orbiting scroll member 11 and the block member 5 with which the Oldham ring 18 is engaged. The Oldham ring 18 includes a ring portion 18a formed in an annular shape so that the boss portion of the orbiting scroll member can be inserted, and a key portion 18b forming a pair protruding in the normal direction from the orbiting scroll member 11 side of the ring portion 18a. And a key portion 18c that forms a pair extending in an arm shape in the radial direction of the ring portion 18a, and two key portions 18b are formed at positions shifted in phase by 180 degrees. Two portions 18c are formed at positions shifted in phase by 180 degrees, and are formed by shifting the phase by 90 degrees with respect to the key portion 18b (a key portion that forms a pair with a line connecting the paired key portions 18b). 18c is formed to be orthogonal to the line connecting 18c).

The key portion 18 b passes through a notch 16 b that extends vertically from the center hole 16 a formed in the thrust trace 16 in the figure, and the key groove portion 11 e that extends radially in the recess portion 11 d of the orbiting scroll member 11. Is slidably engaged with a small clearance so that it can move only in the extending direction of the key groove portion 11e (in this example, the vertical direction).

As shown in FIG. 5, the Oldham housing portion 25 that houses the Oldham ring 18 formed on the block member 5 is a circular ring portion housing portion 25 a formed from the opening end of the block member 5 on the thrust trace side. And

key groove portions

25b and 25c extending in a radial direction from the ring portion accommodating portion 25a, and the ring portion 18a of the Oldham ring 18 extends in the direction in which the key portion 18c extends to the ring portion accommodating portion 25a. The key portion 18c that is accommodated so as to allow movement to the slidable portion is slidably engaged with the

key groove portions

25b and 25c with a small clearance, and the

key groove portions

25b and 25c are extended. It can be moved only in the direction (horizontal direction in this example).

Accordingly, the orbiting scroll member 11 generates a rotating force by the rotation of the drive shaft 8, but the key portion 18 b forming the pair of the Oldham ring 18 reciprocally slides on the key groove portion 11 e forming the pair formed on the orbiting scroll member 11. The pair of key portions 18c reciprocally slides along the pair of

key groove portions

25b and 25c formed in the block member 5, so that the rotation of the drive shaft 8 is controlled while revolving. It has become.

The center hole 16a formed in the thrust trace 16 is formed to have a size that allows the boss portion 11b of the orbiting scroll member to pass therethrough but does not allow the ring portion 18a of the Oldham ring 18 to pass therethrough. The portion 18 a can come into sliding contact with the peripheral edge of the central hole of the end surface on the block side of the thrust trace 16. Moreover, the notch 16b which penetrates the key part 18b is formed over the range in which the key part 18b is movable in anticipation of the movement of the Oldham ring 18.

The thrust trace 16 is in close contact with the end surface of the block member 5 so as to close the

key groove portions

25 b and 25 c of the Oldham accommodating portion 25. That is, the thrust trace 16 is brought into close contact with the end surface of the block member 5 until it reaches the radially outer side from the

key groove portions

25b, 25c formed in the block member, and the Oldham accommodating portion 25 of the block member 5 is connected to the thrust trace 16 and the block. It is designed to be formed on the inner side of the close contact portion with the member 5. In this example, since the outer edge of the thrust trace 16 is formed in a size that matches the shape of the end face of the block member 5, the thrust trace is brought into close contact with the entire end face of the block member 5, and a pressure supply path 45 described later is introduced. The groove 38 is also closed at the same time.
The drive shaft 8 is inserted into the block member 5 via the bearing 6, but the seal member 21 is disposed in the seal housing portion 22 of the block member 5, and the drive member 8 is interposed between the drive shaft 8 and the block member 5. Is hermetically sealed by the seal member 21.

Accordingly, the thrust trace 16 has its front side in close contact with the end surface of the block member 5 and its rear side in close contact with the sliding surface 11f of the orbiting scroll member 11 over the entire circumference. A stationary space 50 is formed by a region surrounded by the block member 5.

By the way, between the outer peripheral wall 10b of the fixed scroll member 10 and the outermost peripheral portion of the spiral wall 11c of the orbiting scroll member 11, the refrigerant introduced from the suction port 40 described later is sucked through the suction path 41. A suction chamber 26 is formed, and behind the fixed scroll member 10 in the housing, the refrigerant gas compressed in the compression chamber 15 is discharged through a discharge hole 27 formed substantially at the center of the fixed scroll member 10. A discharge chamber 28 is defined between the rear side wall 2 b of the housing 2. Here, the refrigerant gas discharged into the discharge chamber 28 is separated from oil in the gas to some extent, and is pumped from a discharge port (not shown) to an external refrigerant circuit. The separated oil or refrigerant mixed with oil is also stored in a storage chamber 31 provided below the discharge chamber 28. The discharge chamber 28 and the reservoir chamber 31 form a high pressure region.

On the other hand, a motor housing space 32 for housing the electric motor 4 is formed in a portion of the housing 2 in front of the block member 5, and a stator 33 constituting the electric motor 4 is fixed thereto. The stator 33 is composed of a cylindrical iron core 34 and a coil 35 wound around the iron core 34, and is fixed to the inner surface of the housing 2. The drive shaft 8 is fixed with a rotor 36 made of a magnet housed rotatably inside the stator 33, and the rotor 36 is rotated by the stator 33 as the drive shaft 8 rotates. It can be rotated by magnetic force. The stator 33 and the rotor 36 constitute an electric motor 4 composed of a brushless DC motor.

A suction port 40 for sucking refrigerant gas is formed on the side surface of the housing 2 facing the motor housing space 32, and a gap between the stator 33 and the housing 2 or between the block member 5 and the housing 2 (not shown). In addition, a suction path 41 that guides the refrigerant flowing into the motor housing space 32 from the suction port 40 to the suction chamber 26 through a gap formed between the fixed scroll member 10 and the housing 2 is configured.

In addition, a passage 42 having one end opened in a reservoir chamber 31 that constitutes a part of the discharge region and the other end opened on an end surface facing the thrust race 16 is provided at a lower portion of the fixed scroll member 10. The end plate 10a and the outer peripheral wall 10b are perforated, and a through hole 43 is formed in the thrust trace 16 at a position facing the opening portion of the passage 42. Further, an introduction groove 44 formed along the outer edge of the block member 5 is provided on the end face of the block member 5 facing the thrust trace 16 from the position facing the through hole 43 of the thrust trace 16 to one key groove portion 25b. It has been.

Therefore, the discharge region communicates with one key groove portion 25b through the passage 42, the through hole 43, and the introduction groove 44. The discharge region and the Oldham accommodating portion 25 are connected by the passage 42, the through hole 43, and the introduction groove 44. A pressure supply path 45 that communicates with each other is configured. An orifice 46 is formed in the middle of the pressure supply path 45, in this example, in the vicinity of the end opening to the reservoir chamber 31, and a filter 47 is disposed upstream thereof.

Further, the block member 5 is formed with a pressure discharge path 48 having one end opened to the other key groove portion 25 c and the other end opened to a position facing the motor housing space 32 (suction path) on the back surface of the block member 5. Yes. In the middle of the pressure discharge path 48, for example, at an opening end to the suction path 41, a pressure adjustment valve 49 that opens the pressure to the suction path 41 when the stop space 50 becomes a predetermined pressure or higher is disposed. ing. Therefore, in this example, the pressure in the stationary space 50 is set to an intermediate pressure between the pressure of the working fluid introduced into the compression chamber 15 and the pressure of the working fluid discharged from the compression chamber 15. The intermediate pressure is desirably increased within a range in which the thrust reaction force received by the thrust trace 16 from the orbiting scroll member 11 can be reduced. However, if the thrust is excessively increased, a so-called rollover phenomenon occurs in which the orbiting scroll member 11 tilts. It is set in a range where such a rollover phenomenon does not occur, for example, in a range of 0.02 to 0.05 MPa.

Reference numeral 51 denotes an inverter drive circuit that is mounted on the inverter circuit end plate 53 housed in the inverter housing chamber 52 in the upper part of the housing 2 and performs power feeding control of the motor 4. An inverter side cluster 55 is connected to the inverter drive circuit 51 via a cable 54, and an electric motor side cluster 58 is connected to the stator 33 via a cable 57. The inverter drive circuit 51 and the stator 33 are mounted on the relay terminal 56 (airtight terminal) 56 provided at the rear of the inverter housing chamber 52 from above, and the motor-side cluster 58 is mounted on the relay terminal 56 from below. Are electrically connected to each other via a relay terminal 56 so that power is supplied from the inverter drive circuit 51 to the electric motor 4.

Therefore, when the electric motor 4 rotates and the drive shaft 8 rotates, the orbiting scroll member 11 is rotated about the eccentric shaft 8 a in the compression mechanism 3. Revolve around. At this time, since the orbiting scroll member 11 is prevented from rotating by the rotation preventing mechanism including the Oldham ring 18, only the revolving motion is allowed.

By this revolving motion of the orbiting scroll member 11, the compression chamber 15 moves while gradually decreasing the volume from the outer peripheral side of the

spiral walls

10c, 11c of both scroll members to the center side, so that the suction chamber 26 sucks into the compression chamber 15. The compressed refrigerant gas is compressed, and the compressed refrigerant gas is discharged into the discharge chamber 28 through the discharge hole 27 formed in the end plate 10 a of the fixed scroll member 10. And it is sent to an external refrigerant circuit through the discharge port which is not illustrated.

The refrigerant gas discharged into the discharge chamber 28 is separated to some extent by the lubricating oil mixed in the discharge chamber, and this separated lubricating oil passes through the pressure supply path 45 provided with the orifice 46 together with the refrigerant. Then, it is supplied to the key groove portion 25 b formed in the Oldham accommodating portion 25 of the block member 5 and guided to the stationary space 50 behind the orbiting scroll member 11. Thereafter, the stationary space 50 is traversed from one key groove portion 25b to the other key groove portion 25c, and discharged from the pressure discharge passage 48 provided in the other key groove portion 25c to the suction passage 41 through the pressure adjusting valve 49. .

For this reason, the stationary space 50 is configured by bringing the peripheral edge of the orbiting scroll member 11 and the end surface of the block member 5 into close contact with the thrust trace 16, so that the hydraulic fluid supplied from the compression chamber 15 or an oil-mixed working fluid is provided. (Refrigerant) can be retained in the retaining space 50, and abundant oil can be supplied to the sliding portion of the Oldham ring 18. For this reason, it is possible to ensure the reliability of the rotation prevention mechanism by reliably lubricating the Oldham ring.

Further, the pressure regulating valve 49 provided in the pressure discharge path 48 is opened when the pressure exceeds a set pressure, and the medium stored in the stationary space 50 is discharged to the suction path 41 (motor housing space 32). Therefore, the stationary state of the medium in the stationary space 50 can be adjusted by the pressure adjusting valve 49, and the stationary space 50 can be set to an intermediate pressure.
For this reason, the amount of oil to be retained in the retention space can be adjusted by the pressure adjusting valve 49, and the intermediate pressure is urged from behind the orbiting scroll member 11, so that the compression reaction acting on the orbiting scroll member 11 is performed. The force can be reduced by the intermediate pressure in the stationary space 50.

That is, by adjusting the valve opening pressure of the pressure regulating valve 49, the Oldham ring can be smoothly moved, and the load applied to the thrust trace 16 is reduced within a range in which the orbiting scroll member 11 does not roll over (orbiting). It is possible to alleviate the urging force that the scroll member 11 is pressed against the thrust trace 16), and it is possible to reduce wear at the sliding contact portion between the orbiting scroll member 11 and the thrust trace 16.

Furthermore, according to the above-described configuration, the thrust scroll 16 is interposed between the fixed scroll member 10 and the block member 5, and the orbiting scroll member 11 is brought into contact with the thrust trace 16. In order to increase the back pressure, it is no longer necessary to cover the compression space of the fixed scroll member 10 with the end plate 11a of the orbiting scroll member 11, and the outer diameter of the orbiting scroll member 11 can be reduced. The diameter can be reduced.
Furthermore, since the Oldham ring 18 is held between the block member 5 and the thrust trace 16 so as to cover the Oldham accommodating portion 25, flapping of the Oldham ring 18 can be suppressed.

Further, according to the above-described configuration, the oil separated in the compression chamber or the oil-mixed refrigerant is supplied to one key groove portion 25b of the Oldham storage portion 25 that stores the Oldham ring 18 via the pressure supply path 45, After that, it is sent to the other key groove portion 25c via the ring portion accommodating portion 25a and then discharged to the suction passage 41 via the pressure discharge passage 48, so that the Oldham ring 18, the orbiting scroll member 11 and the thrust trace 16 A path through which abundant oil can be supplied to the sliding contact portion, the bearing 13 and the like is positively formed, and a good lubrication state can be obtained regardless of the installation state of the compressor.

In the above configuration, the oil is naturally separated from the refrigerant discharged into the discharge chamber 28, and the separated oil or the oil-mixed refrigerant is supplied to the stop space 50. However, the oil is discharged into the discharge chamber. An oil separator that separates the oil in the refrigerant may be further provided, and the oil separated by the oil separator may be stored in the reservoir chamber 31 and only the oil may be supplied to the stationary space 50.
Moreover, in the above-described configuration, an example in which the retention space is formed at an intermediate pressure has been shown. However, any configuration may be used as long as the medium after being compressed in the compression space in the compression chamber can be temporarily retained. The pressure adjusting valve 49 is removed from the 48 and the medium is temporarily stopped in the stop space due to the passage resistance of the pressure discharge path itself, or the pressure discharge path 48 and the seal member 21 are eliminated, thereby the suction path via the bearing 6. The pressure may be discharged to 41 and the medium may be temporarily stopped by the passage resistance when passing near the bearing 6.
Furthermore, in the above-described configuration, the example in which the block member 5 is configured as a member fixed to the housing has been described. However, the block member 5 may be integrally formed with the housing.

DESCRIPTION OF SYMBOLS 1 Electric compressor 2 Housing 4 Electric motor 5 Block member 8 Drive shaft 10 Fixed scroll member 11 Orbiting scroll member 11a End plate 11d Recessed part 11f Sliding surface 15 Compression chamber 16 Thrust trace 18 Oldham ring

18a Ring part

18b, 18c Key part 11d 25b Key groove part 25 Oldham accommodation part 50 Stop space 41 Suction path 28 Discharge chamber 45 Pressure supply path 48 Pressure discharge path 49 Pressure control valve

Claims

A fixed scroll member whose movement in the rotational direction and the axial direction is restricted with respect to the inside of the housing;
A drive shaft for transmitting rotational power;
An orbiting scroll member that is disposed opposite to the fixed scroll member and revolves around the axis of the drive shaft by being connected to the drive shaft via an eccentric shaft that is eccentric with respect to the axis of the drive shaft; ,
A block member provided on the opposite side of the orbiting scroll member to the opposite side of the fixed scroll member and supporting the drive shaft;
A plurality of key portions disposed between the orbiting scroll member and the block member and slidably engaged with a plurality of key groove portions formed on the back surface of the orbiting scroll member, and the orbiting of the block member A plurality of key portions that are slidably engaged with a plurality of key groove portions formed on an end surface facing the scroll member are provided, and by engaging these key portions with the corresponding key groove portions, A rotation preventing member for preventing rotation,
In the scroll type compressor that compresses the medium by moving the compression chamber formed by the fixed scroll member and the orbiting scroll member to the center side while reducing the volume by the revolving motion of the orbiting scroll member,
An annular thrust trace that receives the orbiting scroll member in the axial direction is sandwiched between the fixed scroll member and the block member,
The thrust trace is brought into close contact with the entire circumference of the end face of the orbiting scroll member facing the thrust trace, and the thrust trace is moved to the outside in the radial direction from the key groove formed in the block member. Close to the end face of
A scroll-type compression characterized in that a stationary space is defined by the orbiting scroll member, the thrust trace, and the block member, and the medium compressed in the compression chamber is supplied to the stationary space and retained. Machine.
An annular sliding surface is formed on the back surface of the end plate of the orbiting scroll so that the thrust trace closely contacts the sliding scroll, and the sliding surface does not protrude from the thrust trace. The scroll compressor according to claim 1.
A discharge area for discharging the medium stopped in the stop space is formed behind the fixed scroll member in the housing,
3. The scroll compressor according to claim 1, wherein the discharge region and the stationary space communicate with each other via a pressure supply path in which a throttle is formed in the middle.
4. The stop space and a suction path for guiding the medium to the compression chamber communicate with each other via a pressure discharge path, and a pressure adjusting valve is disposed in the middle of the pressure discharge path. Scroll type compressor.
The rotation prevention member is disposed in an Oldham accommodating portion formed in the block portion, and is formed on a ring portion and a rear surface of the orbiting scroll member that protrudes from the ring portion and penetrates the thrust trace. A pair of key portions that are slidably engaged with a pair of key grooves, and a pair of key grooves formed on the block member that project from both sides in the radial direction of the ring portion so as to be slidable. A pair of key parts,
The Oldham housing part is slidably engaged with a ring part housing part for housing the ring part and a pair of key parts communicating with the ring part housing part and projecting on both radial sides of the ring part. It is composed of the key groove part which makes the pair,
The pressure supply path communicates with one of the pair of key grooves formed in the block member, and the pressure discharge path communicates with the other of the pair of key grooves formed in the block member. The scroll compressor according to claim 4, wherein the scroll compressor is provided.