JP7143450B2 - Double-rotating scroll compressor - Google Patents

Description

The present disclosure relates to a double rotating scroll compressor.

As shown in Patent Document 1, a double rotary scroll compressor is known. This includes a driving side scroll and a driven side scroll that rotates synchronously with the driving side scroll. , the driving shaft and the driven shaft are rotated in the same direction at the same angular velocity.

Japanese Patent No. 5443132

In Patent Document 1, compression spaces are formed on both sides of the end plate by providing wrap portions on both sides of the end plate of the driven scroll portion. This is because the compression space can be formed on both sides of the end plate, and the flow rate can be doubled compared to the case where the compression space is formed only on one side of the end plate. However, in order to achieve a larger flow rate, it is necessary to expand the scroll portion in the radial direction. However, expanding the scroll portion in the radial direction increases the amount of deformation and stress in the wrap portion, so there is a limit to increasing the flow rate.
Therefore, an object of the present disclosure is to provide a dual rotary scroll compressor capable of achieving a large flow rate.

Further, when the drive section side space and the compression section side space are partitioned by the partition wall section, the compression section side space has a suction section that sucks the gas before compression. may be lower. For this reason, there is a possibility that a pressure difference may occur between the drive section side space and the compression section side space, which are at atmospheric pressure. If such a pressure difference occurs, the lubricant used in the drive-side bearing that supports the drive shaft with respect to the partition wall may leak into the space of the compression section on the low-pressure side, resulting in poor lubrication.
Therefore, an object of the present disclosure is to provide a dual-rotation scroll compressor that can suppress poor lubrication of the drive-side bearing.

Further, between the first side plate connected to the driven side scroll member, the second side plate spaced apart from the first side plate and substantially parallel to the first side plate, and the center plate connected to the drive section. A configuration is conceivable in which a closed internal space is formed, and a synchronous drive section is provided in this internal space for synchronizing the drive-side scroll member and the driven-side scroll member. In this case, since the center plate and the first side plate are in sliding contact with each other, the lubricant is supplied. However, there is a possibility that the lubricant may leak out due to centrifugal force on the central portion side of the center plate and become insufficient.
Accordingly, an object of the present disclosure is to provide a dual-rotation scroll compressor capable of suppressing the shortage of lubricant between the first side plate and the center plate.

A tip seal is provided in a tip seal groove at the tip in the height direction of the wall portion (wrap) of each scroll member. The tip seal seals by rising to the end plate side due to the pressure of the fluid that has entered the back surface of the tip seal. However, if the pressure ratio is low, the tip seal cannot be sufficiently floated, and the desired sealing performance may not be obtained.
Therefore, an object of the present disclosure is to provide a dual rotary scroll compressor capable of improving the sealing performance of the tip seal.

Moreover, when machining the scroll member, it is necessary to grip the outer periphery of the scroll member with a chuck of a machine tool. At this time, there was a problem that the position to grip the scroll member could not be determined, and it was not possible to stably chuck the scroll member, resulting in poor workability.
Accordingly, an object of the present disclosure is to provide a dual-rotation scroll compressor including a scroll member with good workability.

In addition, an end plate extension protruding radially outward from the wall is provided on the inner portion of the wall in the circumferential direction radially inward of the winding end position in the circumferential direction of the wall. It is conceivable to reduce the size of the scroll member. However, if the end plate extension is provided with a small projecting portion whose radial dimension is smaller than the thickness of the wall, the tip of the wall in the height direction protrudes from the small projecting portion. A tip seal cannot be provided at the tip in the height direction. In this case, the desired sealing performance cannot be obtained in the gap between the small projecting portion and the tip of the wall in the height direction.
Therefore, an object of the present disclosure is to provide a double rotary scroll compressor that can obtain desired sealing performance in a gap between a small projecting portion and a height direction tip of a wall.

Further, there is a case where a configuration is employed in which a fastening portion that fastens the facing drive-side scroll members with the height direction tips of the wall bodies facing each other is provided in each of both the drive-side scroll members. In this case, the driven-side scroll member is sandwiched between the driving-side scrolls. need to stand out. In this case, machining of the tip of the wall in the height direction and machining of the end surface of the fastening portion in the height direction are performed in separate processes, which hinders reduction of the machining time.
Therefore, an object of the present disclosure is to provide a dual-rotation scroll compressor capable of shortening the processing time of a scroll member having a wall having a fastening portion.

A double-rotating scroll compressor according to an aspect of the present disclosure is rotationally driven about a rotation axis by a drive unit, and spiral first drive side walls are arranged on both sides of a first drive-side end plate. A driving side scroll member and a first spiral driven side wall are disposed on respective opposite sides of the first driven end plate, one side of the first side wall relative to one of the first side side walls of the drive. A first driven side scroll member forming a first compression space by being meshed with each other, and being rotationally driven about the rotation axis together with the first driving side scroll member, and the other of the first driven side walls is meshed. a second driving side scroll member in which a spiral second driving side wall forming a second compression space is disposed on the second driving side end plate; and a second spiral driven side wall is disposed in the second driven side end plate a second driven side scroll member disposed in the second driven side wall body and forming a third compression space by meshing the second driven side wall body with the other side of the first driving side wall body; the first driving side scroll member; The first driven-side scroll member and the second driven-side scroll member are rotated in the same direction at the same angular velocity so that the second driving-side scroll member, the first driven-side scroll member, and the second driven-side scroll member rotate in the same direction. 2 a synchronous drive mechanism for transmitting a driving force to a driven scroll member ; a second side plate fixed with a predetermined spacing in the rotation axis direction; and a second side plate disposed between the first side plate and the second side plate and sealed together with the first side plate and the second side plate. a center plate forming an internal space, wherein the first side plate is fixed to the first driven scroll member or the second driven scroll member, and the center plate is fixed to the driving portion. , the synchronous drive mechanism is provided in the internal space .

The first drive-side scroll member is a so-called double-toothed scroll member having first drive side walls on both sides of the first drive-side end plate. The first driven scroll member is also a double-toothed scroll member having first driven side walls on opposite sides of the first driven end plate. Then, one first driving side wall of the double-toothed first driving side scroll member and one of the first driven side wall members of the double-toothed first driven side scroll member are meshed with each other to perform the first compression. A space is formed.
The other first driven side wall of the double-toothed first driven side scroll member meshes with the second driving side wall of the second driving side scroll member to form a second compression space.
The other first drive side wall of the double-toothed first drive side scroll member meshes with the second driven side wall of the second driven side scroll member to form a third compression space.
Thus, by using two double-toothed scroll members, three compression spaces can be formed on either side of each end plate. Thereby, a large flow rate can be realized.
The number of double-toothed scroll members is not limited to two, and may be three or more. That is, the second driving side scroll member and the second driven side scroll member may have both teeth instead of one tooth.

Further, in the dual-rotation scroll compressor according to one aspect of the present disclosure, the fluid compressed in each of the compression spaces is provided with a final discharge port through which the fluids compressed in the compression spaces are merged and discharged, and the central portion of the first drive-side end plate is formed with a first drive-side discharge port through which compressed fluid is discharged, and a first driven-side discharge port through which compressed fluid is discharged is formed in the central portion of the first driven-side end plate. The cross-sectional areas of the first driving side outlet and the first driven side outlet are smaller on the upstream side than on the downstream side with respect to the final outlet.
The fluid compressed in each compression space is discharged to the outside of both rotary scroll compressors from the final discharge port after joining. Since the upstream outlet has a lower flow rate than the downstream outlet after the fluids are merged, the possibility of choking is low, so the flow passage cross-sectional area of the upstream outlet is smaller than that of the downstream side. can do. Therefore, of the first drive side outlet and the first driven side outlet, the upstream side with respect to the final outlet has a flow passage cross-sectional area smaller than the downstream side.
In addition, by reducing the channel cross-sectional area of the outlet on the upstream side, the wall can be formed closer to the outlet than when the channel cross-sectional area is large, so the pressure ratio can be increased.

Further, in the double-rotating scroll compressor according to an aspect of the present disclosure, a drive section-side space that accommodates the drive section, the first drive-side scroll member, the second drive-side scroll member, and the first driven-side scroll member are provided. a compression section-side space that accommodates the scroll member, the second driven scroll member, and the synchronous drive mechanism; an intake section that is connected to the compression section space and sucks gas before being compressed; and the drive section-side space. and the compression side space; a drive shaft that is rotationally driven by the drive unit and penetrates the partition wall; and a drive that rotatably supports the drive shaft with respect to the partition wall. A pressure equalizing hole is formed in the partition wall portion for equalizing pressure between the driving portion side space and the compression portion side space.

The driving section side space and the compression section side space are partitioned by a partition wall. Since the compression section side space has a suction section that sucks the gas before compression, the pressure inside may become lower than the ambient pressure (for example, the atmospheric pressure). Therefore, a pressure difference may occur between the drive section side space and the compression section side space, which are at ambient pressure. If such a pressure difference occurs, the lubricant used in the drive-side bearing that supports the drive shaft may leak into the space of the compression section on the low-pressure side, resulting in poor lubrication. Therefore, a pressure equalizing hole is formed in the partition wall to equalize the pressure between the driving side space and the compressing side space. As a result, the pressure difference between the drive-side space and the compression-side space can be reduced, and poor lubrication of the drive-side bearing can be suppressed.

Further, in the dual-rotation scroll compressor according to one aspect of the present disclosure, a lubricant space for containing a lubricant is provided between the first side plate and the center plate and in the region on the rotation axis side. department is provided.

A closed internal space is formed by the first side plate, the second side plate and the center plate, and a synchronous drive is provided in this internal space. The center plate is lubricated as it is in sliding contact with the first side plate to form an enclosed space. A lubricant space for accommodating a lubricant is provided between the first side plate and the center plate and in a region on the rotation axis side. As a result, even if the center plate rotates about the rotation axis and the lubricant flows radially outward due to centrifugal force, it is possible to prevent the lubricant from becoming insufficient.

Furthermore, in the dual-rotation scroll compressor according to one aspect of the present disclosure, lubrication is provided between the first side plate and the center plate using relative movement between the first side plate and the center plate. A lubricant introduction channel is provided to guide the lubricant to the lubricant space.

Since the lubricant existing between the first side plate and the center plate is guided to the lubricant space by the lubricant introduction channel, it is possible to further suppress the shortage of the lubricant. The lubricant introduction channel is formed as a groove in the first side plate or the center plate, for example.

Further, in the double-rotating scroll compressor according to one aspect of the present disclosure, a tip seal for sealing between the wall body and the corresponding end plate is provided at the tip in the height direction of the wall body. A tip seal groove for accommodating the tip seal is formed at the tip in the vertical direction, and radially outward of the tip seal groove centered on the rotation axis is formed toward the tip in the height direction of the wall. A first sloping wall is provided that slopes radially outward.

By providing the first inclined wall portion, the tip seal subjected to centrifugal force moves along the first inclined wall portion toward the opposing end plate. Thereby, the sealing performance of the tip seal can be improved.

Further, in the dual-rotation scroll compressor according to one aspect of the present disclosure, radially inwardly of the tip seal groove centered on the rotational axis line is provided radially toward the tip side in the height direction of the wall body. A second inclined wall portion is provided on the inner side thereof, the second inclined wall portion being inclined symmetrically with the first inclined wall portion.

Since the second inclined wall portion is provided symmetrically with the first inclined wall portion, workability of the tip seal groove is improved.

Further, in the double-rotating scroll compressor according to one aspect of the present disclosure, a tip seal for sealing between the wall body and the corresponding end plate is provided at the tip in the height direction of the wall body. A tip seal groove for accommodating the tip seal is formed at the front end in the width direction, and a tip seal groove is provided at the outer end of the tip seal groove in the circumferential direction toward the front end side in the height direction of the wall body. A third inclined wall portion is provided that is inclined toward the tip.

As the scroll member rotates, the tip seal moves circumferentially outward. This movement can be used to move the tip seal toward the end plate along the third inclined wall . Thereby, the sealing performance of the tip seal can be improved.

Further, in the double-rotating scroll compressor according to one aspect of the present disclosure, the winding end portion of the wall in the circumferential direction protrudes radially outward from the wall and has a center at the center position of the end plate. A circular arc is provided.

A circular arc portion protruding radially outward from the wall is provided at the winding end portion of the wall in the circumferential direction. Since the arc portion has an arc shape centered at the center position of the end plate, it can be easily and accurately positioned when it is held by a chuck of a machine tool when machining the scroll member. can be improved.

Further, in the double-rotating scroll compressor according to an aspect of the present disclosure, the winding end portion is provided with a projection projecting radially outward from the wall body and having a positioning or fixing hole, The circular arc portion is provided on the outer side in the circumferential direction or the inner side in the circumferential direction of the protrusion.

The protrusion is provided with a positioning or fixing hole. The holes are used to position and fix the facing scroll members. By providing the arc portion on the outer side in the circumferential direction of the protrusion, the protrusion can be provided on the outer side in the circumferential direction as much as possible, and can be easily gripped by the chuck of the machine tool. Further, by providing the circular arc portion on the inner side in the circumferential direction of the projecting portion, it is possible to reduce the inertia force when the scroll member rotates as much as possible.

Further, in the dual-rotating scroll compressor according to an aspect of the present disclosure, the wall body is provided at a circumferentially outer side portion of the wall body positioned radially inward with respect to the winding end position in the circumferential direction of the wall body. There is an arc projecting radially outwardly from the end plate and centered at the center of the end plate.

The circular arc portion is provided in the circumferentially outer side portion of the wall located radially inward with respect to the winding end position in the circumferential direction of the wall. As a result, the distance of the arc portion from the center of the end plate can be reduced, so that the rotational inertia force of the arc portion can be reduced.

Further, in the dual-rotating scroll compressor according to an aspect of the present disclosure, the wall body is provided at a circumferentially outer side portion of the wall body positioned radially inward with respect to the winding end position in the circumferential direction of the wall body. an endplate extension projecting radially outwardly from the wall, said endplate extension having a minor projection radially dimensioned less than the thickness of said wall, said wall of said minor projection An abradable coating is applied to the surface facing the body or the tip in the height direction of the wall facing the small projecting portion.

The end plate extension faces the height direction tip of the opposing wall. At this time, if the end plate extension is provided with a small protruding portion whose radial dimension is smaller than the thickness of the wall, the tip of the wall in the height direction protrudes from the small protruding portion. A tip seal cannot be provided at the tip in the height direction. Therefore, an abradable coating is applied to the surface facing the wall of the small projecting portion or the tip of the wall facing the small projecting portion in the height direction. As a result, the size of the gap between the small projecting portion and the tip of the wall in the height direction can be made as small as possible, and the sealing performance can be improved.

Further, in the dual-rotation scroll compressor according to an aspect of the present disclosure, the first drive-side scroll member and the second drive-side scroll member are arranged in a state in which the height direction tips of the wall bodies face each other A fastening portion to be fastened is provided on each of the first drive-side scroll member and the second drive-side scroll member, and the height direction tip of the wall of one of the drive-side scroll members and the height direction of the fastening portion are provided. or a fastening portion that fastens the first driven scroll member and the second driven scroll member with the tips of the walls facing each other in the height direction. Provided on each of the first driven scroll member and the second driven scroll member, the height direction tip of the wall of one of the driven scroll members and the height direction tip of the fastening portion are at the same height. ing.

Since the height direction tip of the wall body and the height direction tip of the fastening portion are at the same height, there is no need to change the position in the height direction during processing, so the processing time can be shortened. can.
The fastening portion of the other scroll member has a shape different in height from the wall so as to come into contact with the fastening member of the one scroll member.

According to the double rotary scroll compressor of the present disclosure, a large flow rate can be achieved.

According to the dual rotary scroll compressor of the present disclosure, it is possible to suppress poor lubrication of the drive-side bearing.

According to the double rotary scroll compressor of the present disclosure, it is possible to suppress the shortage of lubricant between the first side plate and the center plate.

According to the dual rotary scroll compressor of the present disclosure, it is possible to improve the sealing performance of the tip seal.

According to the dual rotary scroll compressor of the present disclosure, it is possible to improve workability of the scroll member.

According to the dual rotary scroll compressor of the present disclosure, desired sealing performance can be obtained in the gap between the small projecting portion and the tip of the wall in the height direction.

According to the dual rotary scroll compressor of the present disclosure, it is possible to shorten the processing time of the scroll member including the wall having the fastening portion.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a vertical cross-sectional view showing a double rotary scroll compressor according to a first embodiment of the present disclosure; FIG. 2 is a plan view showing a first driving sidewall body of FIG. 1; FIG. 2 is a plan view showing a first driven sidewall body of FIG. 1; FIG. 2 is a longitudinal sectional view showing a modification of FIG. 1; FIG. 6 is a vertical cross-sectional view showing a double rotary scroll compressor according to a second embodiment of the present disclosure; FIG. 10 is a vertical cross-sectional view showing a double rotary scroll compressor according to a third embodiment of the present disclosure; FIG. 7 is a plan view showing a modification of the center plate of FIG. 6; FIG. 3 shows a fourth embodiment of the present disclosure, and is a cross-sectional view taken along section line AA in FIG. 2; FIG. 4 shows a fourth embodiment of the present disclosure and is a cross-sectional view taken along the line BB in FIG. 2; FIG. 11 is a plan view showing a first drive-side scroll member according to a fifth embodiment of the present disclosure; FIG. 11 is a plan view showing a modification of FIG. 10; FIG. 11 is a plan view showing a modification of FIG. 10; FIG. 11 is a plan view showing a first drive-side scroll member according to a sixth embodiment of the present disclosure; FIG. 14 is a cross-sectional view taken along line CC of FIG. 13; FIG. 20 is a vertical cross-sectional view showing a main part of a connecting portion of a drive-side scroll member according to a seventh embodiment of the present disclosure;

Embodiments according to the present disclosure will be described below with reference to the drawings.
[First embodiment]
A first embodiment of the present disclosure will be described below.
FIG. 1 shows a double rotary scroll compressor 1 . The double-rotating scroll compressor 1 is, for example, a supercharger for compressing combustion air (fluid) supplied to an internal combustion engine such as a vehicle engine, a compressor for supplying compressed air to electrodes of a fuel cell, a railway It can be used as a compressor for supplying compressed air used in a braking device of a vehicle, etc., and a refrigerant compressor used in an air conditioner.

The double rotary scroll compressor 1 includes a housing 3, a motor (driving unit) 5 housed at one end of the housing 3, a driving side scroll member 70 and a driven side scroll member housed at the other end of the housing 3. 90.

The housing 3 has a substantially cylindrical shape, and includes a motor accommodating portion 3a forming a driving portion side space for accommodating the motor 5, and a scroll accommodating portion 3b forming a compressing portion side space for accommodating the scroll members 70, 90 and the like. and The motor accommodating portion 3a and the scroll accommodating portion 3b are partitioned by a partition wall portion 3e.
An end portion (the left end in FIG. 1) of the scroll accommodating portion 3b is formed with an external discharge port 3d for discharging compressed air to the outside. Although not shown in FIG. 1, the scroll housing portion 3b is provided with an air suction port (suction portion) for sucking air.

The motor 5 is driven by being supplied with power from a power supply source (not shown). Rotation control of the motor 5 is performed by a command from a control unit (not shown). A stator 5 a of the motor 5 is fixed to the inner peripheral side of the housing 3 . The rotor 5b of the motor 5 rotates around the driving side rotation axis CL1. A drive shaft 6 extending on the drive-side rotation axis CL1 is connected to the rotor 5b. The drive shaft 6 is connected to a drive shaft portion 72 d fixed to the first drive side scroll member 71 of the drive side scroll member 70 .

A drive-side bearing 11 that rotatably supports the drive shaft 6 is provided at the front end of the drive shaft 6 (the left end in FIG. 1). The drive shaft 6 is rotatably supported with the housing 3 at the rear end of the drive shaft 6 (the right end in FIG. 1), that is, at the end of the drive shaft 6 opposite to the drive scroll member 70 . A rear end bearing 17 is provided.

The driving side scroll member 70 has three driving side scroll members 71 , 72 and 73 . These drive-side scroll members 71, 72, and 73 are arranged and connected in the direction of the drive-side rotation axis CL1.

<First driving side scroll member 71>
The first drive-side scroll member 71 includes a first drive-side end plate 71a and a first drive side wall 71b. The first drive-side end plate 71a extends in a direction perpendicular to the drive-side rotation axis CL1. The first drive-side end plate 71a has a substantially disk shape when viewed from above. A first drive-side discharge port 71d is formed in the center of the first drive-side end plate 71a along the drive-side rotation axis CL1.

As shown in FIG. 2, on the first driving side end plate 71a, there are provided three spiral first driving side walls 71b, that is, three streaks. The three first driving side wall bodies 71b are arranged at equal intervals around the driving side rotation axis CL1. The number of the first drive side wall body 71b may be one, two, or four or more.

As shown in FIG. 1, the first driving side walls 71b are provided on both sides of the first driving side end plate 71a. Therefore, the first drive side scroll member 71 is a so-called double tooth.

<Second Drive Side Scroll Member 72>
A second drive-side scroll member 72 is provided on the motor 5 side (right side in FIG. 1) of the first drive-side scroll member 71 . The second drive side scroll member 72 includes a second drive side end plate 72a and a second drive side wall 72b. The second drive side wall 72b has three lines, like the first drive side wall 71b (see FIG. 2). The number of the second drive side wall body 72b may be one, two, or four or more.

As shown in FIG. 1, the second drive side wall 72b is provided only on one side of the second drive side end plate 72a. That is, the second driving side wall body 72b is provided toward the first driving side scroll member 71 side. Therefore, the second drive side scroll member 72 has a so-called single tooth.

A drive shaft portion 72d extending along the drive-side rotation axis CL1 is fixed to the center of rotation of the second drive-side end plate 72a. A center plate 20 is provided integrally with the drive shaft portion 72d. The center plate 20 extends parallel to the second drive-side end plate 72a.

A third drive-side scroll member 73 is provided on the first drive-side scroll member 71 on the side of the external outlet 3d (on the left side in FIG. 1). The third drive-side scroll member 73 includes a third drive-side end plate 73a and a third drive side wall 73b. The third drive side wall 73b has three lines, like the first drive side wall 71b (see FIG. 2). The number of the third drive side wall 73b may be one, two, or four or more.

As shown in FIG. 1, the third driving side wall 73b is provided only on one side of the third driving side end plate 73a. That is, the third drive side wall body 73b is provided toward the first drive side scroll member 71 side. Therefore, the third driving side scroll member 73 has a so-called single tooth.

A third drive-side shaft portion 73c extending in the direction of the drive-side rotation axis CL1 is connected to the third drive-side end plate 73a. The third drive-side shaft portion 73c is rotatably provided with respect to the housing 3 via the third drive-side bearing 14, which is a ball bearing. A third drive-side discharge port 73d is formed in the third drive-side end plate 73a along the drive-side rotation axis CL1.

Two seal members 26 are provided between the third drive-side shaft portion 73c and the housing 3 on the tip side (left side in FIG. 1) of the third drive-side shaft portion 73c relative to the third drive-side bearing 14. It is The two seal members 26 and the third drive-side bearing 14 are arranged with a predetermined spacing in the direction of the drive-side rotation axis CL1. Between the two seal members 26, lubricant such as grease, which is a semi-solid lubricant, is enclosed. It should be noted that the number of seal members 26 may be one. In this case, lubricant is enclosed between the seal member 26 and the third drive side bearing 14 .

The first drive-side scroll member 71 and the second drive-side scroll member 72, and the first drive-side scroll member 71 and the third drive-side scroll member 73 are separated from each other by the tips (free ends) of the walls 71b, 72b, and 73b. are fixed facing each other. The first drive-side scroll member 71 and the second drive-side scroll member 72, and the first drive-side scroll member 71 and the third drive-side scroll member 73 are fixed in the circumferential direction so as to protrude radially outward. This is performed by bolts 31 fastened to flange portions 74 provided at a plurality of locations.

<First driven side scroll member 91>
The driven scroll member 90 has two driven scroll members 91 and 92 .
The first driven scroll member 91 is arranged on the motor 5 side (on the right side in FIG. 1) with respect to the second driven scroll member 92 . The first driven-side scroll member has a first driven-side end plate 91a located substantially in the center in the axial direction (horizontal direction in the figure). A first driven-side discharge port 91d is formed in the center of the driven-side end plate 90a, and compressed air flows to the first driving-side discharge port 71d.

A first driven side wall body 91b is provided on each side of the first driven side end plate 91a. Therefore, the first driven side scroll member 91 is a so-called double tooth.
A first driven side wall 91b installed on the motor 5 side from the first driven side end plate 91a is meshed with a second driving side wall 72b of the second driving side scroll member 72, and the first driven side end plate 91a is connected to the outside. The first driven side wall 91b installed on the discharge port 3d side is meshed with the first driving side wall 71b of the first driving side scroll member 71. As shown in FIG.

As shown in FIG. 3, three first driven side walls 91b are provided. The three first driven side wall bodies 91b are arranged at regular intervals around the driven side rotation axis CL2. The number of threads of the first driven side wall 91b may be one, two, or four or more.

<Synchronous drive mechanism>
A first side plate 27 is provided on the motor 5 side (right side in FIG. 1) of the first driven scroll member 91 . The first side plate 27 is fixed to the tip (free end) of the first driven side wall 91b by a bolt 28. As shown in FIG. A first side plate hole 27h is formed at the center of rotation of the first side plate 27 to allow the drive shaft 72d to pass therethrough.

A second side plate 30 is provided on the motor 5 side of the first side plate 27 with a predetermined gap therebetween. The second side plate 30 is fixed to the first side plate 27 by bolts 34 . A second side plate hole 30h is formed in the center of rotation of the second side plate 30 to allow the drive shaft 72d to pass therethrough.

A second side plate shaft portion 30a is provided on the central axis side of the second side plate 30, and the second side plate shaft portion 30a includes a second side plate bearing 32 which is an angular ball bearing. It is fixed to the housing 3 via. As a result, the driven side scroll member 90 rotates around the driven side rotation axis CL2 via the second side plate 30 and the first side plate 27 .

The first side plate 27, the second side plate 30, and the center plate 20 form a liquid-tight closed space. The pin 15 and the pin bearing 18 are accommodated in this sealed space.

Both ends of the pin 15 are fixed to the first side plate 27 and the second side plate 30 . The pin 15 is inserted through the inner peripheral side of a pin bearing 18 which is a rolling bearing (for example, a needle bearing) provided on the center plate 20 . Lubricant such as grease is enclosed in the pin bearing 18 . Alternatively, the pin bearing 18 may be omitted and the pin 15 may be inserted through a through hole formed in the center plate 20 .

The pin 15 and the pin bearing 18 serve as a synchronous drive mechanism for transmitting driving force from the drive shaft portion 72d to the driven scroll member 90 so that the driving scroll member 70 and the driven scroll member 90 synchronously revolve. Used.
Preferably, a plurality of synchronous drive mechanisms having pins 15 are provided. For example, three are provided at equal angular intervals around the drive-side rotation axis CL1.

<Second driven side scroll member 92>
The second driven scroll member 92 is arranged on the side of the first driven scroll member 91 toward the external outlet 3d (left side in FIG. 1). The first driven-side scroll member 91 and the second driven-side scroll member 92 face each other in the direction of the driven-side rotation axis CL2 and are fixed to each other by bolts or the like (not shown).

The second driven-side scroll member 92 has a second driven-side end plate 92a located substantially in the center in the axial direction (horizontal direction in the drawing). A second driven-side discharge port 92d is formed in the center of the second driven-side end plate 92a, and compressed air flows to the third drive-side discharge port 73d.

A second driven side wall body 92b is provided on each side of the second driven side end plate 92a. Therefore, the second driven side scroll member 92 is a so-called double tooth.
The second driven side wall 92b installed on the motor 5 side from the second driven side end plate 92a is engaged with the first driving side wall 71b of the first driving side scroll member 71, and the second driven side end plate 92a is connected to the outside. The second driven side wall 92b installed on the discharge port 3d side is meshed with the third driving side wall 73b of the third driving side scroll member 73. As shown in FIG.

Like the first driven side wall 91b, there are three second driven side walls 92b, that is, three rows (see FIG. 3). The three second driven side wall bodies 92b are arranged at regular intervals around the driven side rotation axis CL2. The number of threads of the second driven side wall body 92b may be one, two, or four or more.

A support member 33 is provided on the second driven side scroll member 92 on the side of the external outlet 3d (left side in FIG. 1). The support member 33 is fixed to the tip of the second driven side wall 92b by a bolt 25. As shown in FIG.

A support member shaft portion 35a is provided on the central axis side of the support member 33, and the support member shaft portion 35a is attached to the housing 3 via a second support member bearing 38, which is a ball bearing. Fixed. As a result, the driven side scroll member 90 rotates around the driven side rotation axis CL<b>2 via the support member 33 .

The dual rotary scroll compressor 1 having the above configuration operates as follows.
When the drive shaft 6 is rotated around the drive-side rotation axis CL1 by the motor 5, the drive-side scroll member 70 and the center plate 20 also rotate around the drive-side axis CL1 via the drive shaft portion 72d connected to the drive shaft 6. do. The driving force transmitted to the center plate 20 by the rotation of the center plate 20 is transmitted from the first side plate 27 and the second side plate 30 to the driven side scroll member 90 via the pin 15 as a synchronous drive mechanism, The driven scroll member 90 rotates around the driven rotation axis CL2. As a result, both scroll members 70 and 90 relatively perform a revolving motion.

When both scroll members 70 and 90 perform revolving motion, the air sucked from the suction port of housing 3 is sucked from the outer peripheral side of both scroll members 70 and 90, and the compression chamber formed by both scroll members 70 and 90 is compressed. be taken into Then, it is separately compressed in the compression chambers formed on both sides of the first driven scroll member 91 and the compression chambers formed on both sides of the second driven scroll member 92 . The volume of each compression chamber decreases as it moves toward the center, and the air is compressed accordingly. The air compressed by the first driven side wall 91b and the second drive side wall 72b passes through the first driven side discharge port 91d and is compressed by the first driven side wall 91b and the first drive side wall 71b. , and the air after merging goes toward the first drive-side discharge port 71d. After that, it merges with the air compressed by the first driving side wall 71b and the second driven side wall 92b, goes to the second driven side discharge port 92d, and flows through the second driven side wall 92b and the third driving side wall 73b. , flows to the third driving side discharge port 73d, and is finally discharged to the outside of the double rotary scroll compressor 1 from the external discharge port 3d.

<Action and effect of the first embodiment>
By using two or more (three in this embodiment) double-toothed scroll members 71, 91, 92, three or more (four in this embodiment) on both sides of each end plate 71a, 91a, 92a. of compression space can be formed. Thereby, a large flow rate can be realized.
The number of double-toothed scroll members may be two, or may be four or more.

<Modified Example of First Embodiment>
As shown in FIG. 4, the channel cross-sectional areas of the first driven side discharge port 91d, the first drive side discharge port 71d, and the second driven side discharge port 92d may be changed. Specifically, the upstream side is configured to have a smaller cross-sectional area than the downstream side with respect to the external ejection port 3d, which is the final ejection port. For example, when the shape of each outlet is circular, the diameter of the first driven side outlet 91d is d3, the diameter of the first driving side outlet 71d is d2, and the diameter of the second driven side outlet 92d is d1. ,
d3< d2 <d1
Determine the channel cross-sectional area so as to have the relationship of

The effects of this modification are as follows.
The air compressed in each compression chamber is discharged to the outside of the dual rotary scroll compressor 1 from the external discharge port 3d after joining. Since the upstream outlet has a lower flow rate than the downstream outlet after the air merges, choke is less likely to occur. can do. Therefore, assuming the relationship of d3<d 2 <d1, the channel cross-sectional area is made smaller on the upstream side than on the downstream side with respect to the external discharge port 3d.
In addition, by reducing the flow channel cross-sectional area of the upstream side discharge port, the wall 91b can be formed closer to the first driven side discharge port 91d and up to the inner peripheral side than when the flow channel cross-sectional area is large. The pressure ratio can be increased.

[Second embodiment]
A second embodiment of the present disclosure will be described. In addition, the same code|symbol is attached|subjected about the structure which is common in 1st Embodiment, and the description is abbreviate|omitted.
As shown in FIG. 5, the partition wall portion 3e of the housing 3 is formed with a through-hole pressure equalizing hole 3h. One or two or more pressure equalizing holes 3h may be provided. The pressure equalizing hole 3h equalizes pressure between the driving portion side space in the motor housing portion 3a and the compression portion side space in the scroll housing portion 3b. No through hole is formed in the partition wall portion 3e other than the hole in which the driving side bearing 11 is installed.

According to this embodiment, the following effects are obtained.
The drive section side space and the compression section side space are partitioned by a partition wall portion 3e. Since the scroll accommodating portion 3b forming the compression portion side space has an intake portion (not shown) that inhales the gas before compression, the internal pressure may become lower than the ambient pressure (for example, atmospheric pressure). For this reason, there is a possibility that a pressure difference may occur between the driving section side space and the compressing section side space in the scroll accommodating portion 3b, which are at ambient pressure. If such a pressure difference occurs, the lubricant used in the drive-side bearing 11 that supports the drive shaft portion 72d may leak into the space of the compression portion on the low-pressure side, resulting in poor lubrication. In the present embodiment, since the pressure equalizing hole 3h is formed in the partition wall portion 3e, the pressure difference between the driving portion side space and the compression portion side space is reduced, and poor lubrication of the driving side bearing 11 is suppressed. be able to.

The configuration in which the pressure equalizing hole 3h is formed in the partition wall portion 3e can only be used for the double rotary scroll type compressor 1 having three double toothed scroll members 71, 91 and 92 as in the present embodiment. Instead, it can be applied to both a double-rotating scroll type compressor composed only of a single-toothed scroll member and a double-rotating scroll type compressor having a combination of one double-toothed scroll member and two single-toothed scroll members. can. That is, the present invention can be applied to a dual rotary scroll type compressor having a driving side scroll member and a driven side scroll member.

[Third embodiment]
A third embodiment of the present disclosure will be described. This embodiment differs from the first embodiment in that there are three double-toothed scroll members 71, 91, and 92 in that only one double-toothed scroll member is provided. Also, the mechanism for transmitting power from the drive shaft portion 72d to each scroll member is different. Since the other points are the same, the same reference numerals are given to the configurations that are common to the first embodiment, and the description thereof is omitted.
Further, the present embodiment can also be applied to the double rotary scroll compressor 1 shown in FIG.

As shown in FIG. 6, in a double-rotating scroll compressor 1A of the present embodiment, the first drive-side scroll member 71 of the first embodiment is omitted, and the single-toothed second drive-side scroll member 72 and the single-toothed scroll member 72 are omitted. A drive-side scroll member 70 is configured by the third drive-side scroll member 73 . The driven scroll member 90 is composed of only one first driven scroll member 91 having both teeth.

The driving side plate 37 is connected to the second driving side end plate 72a. The driving side plate 37 extends parallel to the second driving side end plate 72a. The drive-side plate 37 is connected to the outer peripheral portion of the third drive-side end plate 73a by a fixing portion 37a provided at the outer peripheral end. The fixed portion 37a has a cylindrical shape extending parallel to the driving side rotation axis CL1. A through hole is formed in the fixing portion 37a, and the fixing portion 37a is fixed to the second drive side end plate 72a by inserting a bolt 37b into the through hole.

A shaft portion 37 c is provided in the center of the driving side plate 37 . The shaft portion 37 c has a cylindrical shape, and the inner peripheral side thereof is fixed to the outer peripheral side of the drive shaft portion 72 d of the center plate 20 . The center axis of the shaft portion 37c is the driving side rotation axis CL1. As a result, the shaft portion 37c of the drive-side plate 37 is fixed to the drive shaft portion 72d. The connection between the shaft portion 37c and the drive shaft portion 72d is performed by serrations, shrink fitting, bolts, keys, or the like.

A space surrounded by the first side plate 27 and the second side plate 30 accommodates the center plate 20 .

An O-ring 36 is provided as a sealing member on the central side of the second side plate 30 . The O-ring 36 is provided to seal with the end face of the center plate 20 . The O-ring 36 encloses the lubricant for the pin bearing 18 in the accommodation space formed between the first side plate 27 and the second side plate 30 .

At the center of the second side plate 30, a split shaft portion 30e is provided that protrudes toward the motor 5 side in parallel with the driven side rotation axis CL2. A tip end of the split shaft portion 30 e is supported by a side plate bearing 39 provided in the housing 3 . As a result, the driven side scroll member 90 rotates around the driven side rotation axis CL2 via the second side plate 30 and the first side plate 27 . The divided shaft portions 30e are shaft portions that are divided in the circumferential direction, and are provided, for example, three at equal intervals in the circumferential direction.

Between the first side plate 27 and the center plate 20 and on the center side where the rotation axes CL1 and CL2 are located, a lubricant space for accommodating a lubricant is provided. Specifically, a first side plate groove portion 27c is formed in the central portion of the first side plate 27 so as to form a recess. A center plate groove portion 20c is formed in the central portion of the center plate 20 so as to form a recess. These grooves 27c and 20c are formed so that their opening sides face each other. Note that only one of the grooves 27c and 20c may be used.

The effects of this embodiment are as follows.
A closed internal space is formed by the first side plate 27, the second side plate 30 and the center plate 20, and a synchronous driving portion for the pin 15 and the pin bearing 18 is provided in this internal space. Since the center plate 20 is in sliding contact with the first side plate 27 to form an enclosed space, it is supplied with lubricant. Between the first side plate 27 and the center plate 20 and in regions on the sides of the rotation axes CL1 and CL2, grooves 27c and 20c are provided as lubricant spaces for accommodating lubricant. As a result, even if the center plate 20 rotates around the drive-side rotation axis CL1 and the lubricant flows radially outward due to the centrifugal force, it is possible to prevent the lubricant from becoming insufficient.

[Modification of Third Embodiment]
As shown in FIG. 7, this embodiment can be modified as follows.
FIG. 7 is a plan view of the center plate 20 from the side of the center plate groove portion 20c. As shown in the figure, a plurality of radial grooves (lubricant introduction passages) 20d are formed radially outward from a center plate groove 20c formed in the center. Each radial groove portion 20d is provided so as to have an angle of attack with respect to the rotation direction. As a result, the rotation is used to guide the lubricant from the outer peripheral side to the central side.

Since the radial groove portion 20d guides the lubricant existing between the first side plate 27 and the center plate 20 to the central center plate groove portion 20c, it is possible to further suppress the shortage of the lubricant on the central side. can.
The first side plate 27 may be provided with the same configuration as the radial groove portion 20d, and the radial groove portions may be provided in the plates 27 and 20 on both sides. Alternatively, only one of the plates 27, 20 may be provided with radial grooves.

[Fourth embodiment]
A fourth embodiment of the present disclosure will be described. In addition, the same code|symbol is attached|subjected about the structure which is common in 1st Embodiment, and the description is abbreviate|omitted.
FIG. 8 shows a cross section taken along line AA in FIG. FIG. 8 is an enlarged view of the tip of the first driving side wall 71b in the height direction. A tip seal groove 72c for accommodating a tip seal (not shown) is formed at the tip in the height direction of the first drive side wall body 71b. As shown in FIG. 8, the cross section of the tip seal groove 72c has a shape that is narrow at the bottom and wide at the opening side. Specifically, the first inclined wall portion 71c1 is provided so that the radially outer wall surface about the drive-side rotation axis CL1 is inclined radially outward toward the distal end side, and the radially inner wall surface is inclined toward the distal end side. A second inclined wall portion 71c2 is provided so as to be inclined inward in the radial direction. The inclination angles of the first inclined wall portion 71c1 and the second inclined wall portion 71c2 are symmetrical.

By providing the first inclined wall portion 71c1, the tip seal that receives the centrifugal force moves along the first inclined wall portion 71c1 toward the tip end side, ie, the opposing end plate side. Thereby, the sealing performance of the tip seal can be improved. In particular, when the pressure ratio of the two-rotating scroll type compressor 1 is small, it is effective because a sufficient force for floating the tip seal cannot be obtained.

Further, since the second inclined wall portion 71c2 is provided symmetrically with the first inclined wall portion 71c1, workability of the tip seal groove is improved.
It should be noted that the second inclined wall portion 71c2 may be a wall portion that stands substantially vertically without being inclined.

FIG. 9 shows a cross section taken along line BB in FIG. FIG. 9 is an enlarged view of the tip of the first driving side wall 71b in the height direction. As shown in FIG. 9, at the outer end of the tip seal groove 71c in the circumferential direction, there is provided a third groove that is inclined toward the outer end in the circumferential direction toward the height direction end of the first drive side wall body 71b. An inclined wall portion 71c3 is provided.

When the first drive-side scroll member 71 rotates, the tip seal moves outward in the circumferential direction. This movement can be used to move the tip seal toward the end plate along the third inclined wall portion 71c3. Thereby, the sealing performance of the tip seal can be improved.

In this embodiment, the inclined wall portions 71c1, 71c2, and 71c3 are provided on the first drive side wall member 71b, but the walls of the other drive side scroll members 72 and 73 and the driven side scroll members 91 and 92 are provided. may be set to
In addition, the inclined wall portions 71c1, 71c2, 71c3 can be used not only in the double-rotating scroll type compressor 1 having three double-toothed scroll members 71, 91, 92 as in the present embodiment, but also in the single-toothed scroll type compressor 1. It can be applied to both a double-rotating scroll type compressor composed only of a scroll member and a double-rotating scroll type compressor having a combination of one double-toothed scroll member and two single-toothed scroll members. That is, the present invention can be applied to a dual rotary scroll type compressor having a driving side scroll member and a driven side scroll member.

[Fifth embodiment]
A fifth embodiment of the present disclosure will be described. In addition, the same code|symbol is attached|subjected about the structure which is common in 1st Embodiment, and the description is abbreviate|omitted.
FIG. 10 shows a plan view of the first drive-side scroll member 71. As shown in FIG. A flange portion (protruding portion) 74 protruding radially outward from the outer peripheral surface is provided at the winding end portion of the first driving side wall body 71b. The flange portion 74 is used, as shown in FIG. 1, to fasten the driving side scroll members 71, 72, 73 together. Therefore, a hole portion 74a for bolting is provided. Also, the flange portion 74 may have a positioning hole.

A circular arc portion 75a that protrudes radially outward and has a center on the driving side rotation axis CL1 is provided on the outer side in the circumferential direction of the flange portion 74 . The arc portion 75a has a shape formed by extending the first drive-side end plate 71a in the outer peripheral direction. The arc portion 75a is provided at the winding end portion of each wall 71b. That is, in this embodiment, three are provided with an angular interval of 120°.

No protruding portion corresponding to the end plate 71a is provided on the inner side of the flange portion 74 in the circumferential direction up to the circumferentially adjacent wall body 71b. Therefore, in this area, the outer peripheral surface of the wall 71b constitutes the outer shape of the scroll member 71. As shown in FIG. As a result, the size of the scroll member 71 is reduced.

The arc portion 75a has an arc shape having a center on the drive-side rotation axis CL1, which is the center position of the end plate. Positioning can be performed easily and accurately, and workability can be improved.

Further, as shown in FIG. 11, an arc portion 75b may be provided on the inner side of the flange portion 74 in the circumferential direction. As a result, the inertial force generated when the first driving side scroll member 71 rotates can be reduced as much as possible.

No protruding portion corresponding to the end plate 71a is provided inwardly in the circumferential direction from the arc portion 75b to the circumferentially adjacent wall body 71b. Therefore, in this area, the outer peripheral surface of the wall 71b constitutes the outer shape of the scroll member 71. As shown in FIG. As a result, the size of the scroll member 71 is reduced.

Further, as shown in FIG. 12, a circular arc portion 75c is formed in a circumferentially outer side portion of the first drive side wall body 71b located radially inward of the winding end position in the circumferential direction of the first drive side wall body 71b. You can set it. No projecting portion corresponding to the end plate 71a exists on the outer side in the circumferential direction of the arc portion 75c, and the outer peripheral surface of the first driving side wall 71b forms the outer shape of the scroll member 71. As shown in FIG. By providing the arc portion 75c at the position shown in FIG. 12, the distance of the arc portion 75c from the center of the end plate can be made smaller than the arc portion 75a in FIG. 10 and the arc portion 75b in FIG. power can be reduced.

The arc portions 75a, 75b, 75c described above may be applied not only to the first drive-side scroll member 71, but also to the other scroll members 72, 73, 91, 92.
In addition, the arc portions 75a, 75b, 75c can be used not only in the double-rotating scroll type compressor 1 having three double-tooth scroll members 71, 91, 92 as in the present embodiment, but also The present invention can be applied to both a double-rotating scroll type compressor composed only of a scroll member and a double-rotating scroll type compressor having a combination of one double-toothed scroll member and two single-toothed scroll members. That is, the present invention can be applied to a dual rotary scroll type compressor having a driving side scroll member and a driven side scroll member.

[Sixth embodiment]
A sixth embodiment of the present disclosure will be described. In addition, the same code|symbol is attached|subjected about the structure which is common in 1st Embodiment, and the description is abbreviate|omitted.
FIG. 13 shows the first driving side scroll member 71 . An end plate extension portion 76 protruding radially outward is provided on the outer circumferential portion of the first driving side wall 71b, which is located radially inward with respect to the winding end position of the first driving side wall 71b in the circumferential direction. It is The end plate extension 76 is used as the outermost end plate portion when suction is shut off. The end plate extension 76 has a small projecting portion 76a sized radially less than the thickness of the opposing walls 72b, 73b.

No projecting portion corresponding to the end plate 71 a is provided between the end plate extension portion 76 and the flange portion 74 . Therefore, in this area, the outer peripheral surface of the wall 71b constitutes the outer shape of the scroll member 71. As shown in FIG.

As shown in FIG. 14, an abradable coating is applied to a facing surface 76b of a small projecting portion 76a that faces the tip of the walls 72b and 73b in the height direction. As the abradable coating, a resin such as an epoxy system or Teflon (registered trademark) is used.

According to this embodiment, the following effects are obtained.
The end plate extensions 76 face the height direction tips of the walls 72b and 73b. At this time, if the end plate extension 76 is provided with a small protruding portion 76a having a radial dimension smaller than the thickness of the walls 72b, 73b facing each other, the tips of the walls 72b, 73b facing each other in the height direction protrudes from the small protruding portion 76a (see FIG. 14), the tip seals cannot be provided at the ends in the height direction of the opposed wall bodies 72b and 73b. Therefore, an abradable coating is applied to the facing surface 76b of the small projecting portion 76a facing the walls 72b and 73b. As a result, the clearance between the small projecting portion 76a and the height direction tips of the walls 72b and 73b can be made as small as possible, and the sealing performance can be improved.

Note that an abradable coating may be applied to the top surface of the first driving side wall 71b in the height direction facing the small projecting portion 76a.
Further, the abradable coating described above may be applied not only to the first driving side scroll member 71 but also to the other scroll members 72 , 73 , 91 and 92 .
In addition, the abradable coating can be applied not only to the double-rotating scroll type compressor 1 having three double-toothed scroll members 71, 91, and 92 as in the present embodiment, but also to the single-toothed scroll member. It can be applied to both a double-rotating scroll type compressor composed of and a double-rotating scroll type compressor in which one double-toothed scroll member and two single-toothed scroll members are combined. That is, the present invention can be applied to a dual rotary scroll type compressor having a driving side scroll member and a driven side scroll member.

[Seventh Embodiment]
A seventh embodiment of the present disclosure will be described. In addition, the same code|symbol is attached|subjected about the structure which is common in 1st Embodiment, and the description is abbreviate|omitted.
As described with reference to FIG. 1, the first drive-side scroll member 71 and the second drive-side scroll member 72 are provided with flange portions that are fastened with the ends of the walls 71b and 72b facing each other in the height direction. A (fastening portion) 74 is provided.

FIG. 15 shows an enlarged view of the connecting structure between the first drive-side scroll member 71 and the second drive-side scroll member 72 . As can be seen from the figure, the height direction tip of the first drive side wall 71b of the first drive side scroll member 71 and the height direction tip of the flange portion 74 are at the same height H. As shown in FIG.

On the other hand, the flange portion 74 of the second drive side scroll member 72 has a height higher than that of the second drive side wall body 72b so as to come into contact with the flange portion 74 of the first drive side scroll member 71. there is

Since the first driving side scroll member 71 has both teeth, the flange portion 74 (the left side flange portion 74 in FIG. 15) facing the third driving side scroll member 73 (see FIG. 1) also has the first The height is preferably the same as the height of the drive side wall 71b.

Since the tip of the first driving side wall 71b in the height direction and the tip of the flange portion 74 in the height direction are at the same height H, there is no need to change the position in the height direction during machining. Time can be shortened.

In this embodiment, the fastening structure of the driving side scroll members 71, 72, 73 has been described, but the flange portion for fastening the driven side scroll members 91, 92 can also be used.

1, 1A double-rotating scroll compressor 3 housing 3a motor accommodating portion 3b scroll accommodating portion 3d external discharge port 3e partition wall portion 3h pressure equalizing hole 5 motor (driving portion)
5a Stator 5b Rotor 6 Drive shaft 11 Drive-side bearing 14 Third drive-side bearing 15 Pin (synchronous drive mechanism)
18 pin bearing (synchronous drive mechanism)
20 center plate 20c center plate groove (lubricant space)
20d radial groove (lubricant introduction channel)
25 bolt 26 sealing member 27 first side plate 27c first side plate groove (lubricant space)
27h First side plate hole 28 Bolt 30 Second side plate 30a Second side plate shaft 30e Split shaft 30h Second side plate hole 31 Bolt 32 Second side plate bearing 33 Support member 36 O-ring 37 drive-side plate 37a fixing portion 37b bolt 37c shaft portion 38 second support member bearing 39 side plate bearing 70 drive-side scroll member 71 first drive-side scroll member 71a first drive-side end plate 71b first drive side wall 71c chip Seal groove 71c1 First inclined wall portion 71c2 Second inclined wall portion 71c3 Third inclined wall portion 71d First driving side discharge port 72 Second driving side scroll member 72a Second driving side end plate 72b Second driving side wall body 72d Drive shaft Portion 73 Third drive side scroll member 73a Third drive side end plate 73b Third drive side wall 73c Third drive side shaft portion 73d Third drive side discharge port 74 Flange portion (protruding portion, fastening portion)
74a hole portions 75a, 75b, 75c arc portion 76 end plate extension portion 76a small projecting portion 76b facing surface 90 driven side scroll member 91 first driven side scroll member 91a first driven side end plate 91b first driven side wall body 92 second Driven side scroll member 92a Second driven side end plate 92b Second driven side wall CL1 Drive side rotation axis CL2 Driven side rotation axis

Claims (12)

a first driving side scroll member that is rotationally driven about a rotation axis by a driving portion and has spiral first driving side walls arranged on both sides of a first driving side end plate;
A spiral-shaped first driven sidewall is disposed on each side of the first driven endplate, one of the first driven sidewalls meshing against one of the first drive sidewalls to provide a first drive sidewall. a first driven scroll member forming a compression space;
A spiral second drive side wall member is rotationally driven about the rotation axis together with the first drive side scroll member, and is engaged with the other of the first driven side wall members to form a second compression space. a second drive-side scroll member disposed on the side end plate;
A spiral-shaped second driven side wall is disposed on the second driven side end plate, and the second driven side wall is meshed with the other of the first drive side walls to form a third compression space. 2 a driven side scroll member;
The first driving side scroll member, the second driving side scroll member, the first driven side scroll member and the second driven side scroll member are rotated in the same direction at the same angular velocity, from the driving section side to the second driving side scroll member. a synchronous drive mechanism that transmits a driving force to one driven scroll member and the second driven scroll member;
with
a first side plate arranged on the rotational axis direction side with respect to each of the scroll members;
a second side plate fixed to the first side plate with a predetermined gap in the rotation axis direction;
a center plate disposed between the first side plate and the second side plate and forming a closed internal space together with the first side plate and the second side plate;
with
The first side plate is fixed to the first driven scroll member or the second driven scroll member,
The center plate is fixed to the drive unit,
The dual rotary scroll compressor , wherein the synchronous drive mechanism is provided in the internal space . a drive unit-side space that accommodates the drive unit;
a compression section side space accommodating the first driving side scroll member, the second driving side scroll member, the first driven side scroll member, the second driven side scroll member, and the synchronous drive mechanism;
an inhalation unit connected to the compression unit side space and inhaling gas before compression;
a partition wall portion that partitions the drive portion side space and the compression portion side space;
a drive shaft that is rotationally driven by the drive unit and penetrates the partition wall;
a drive-side bearing that rotatably supports the drive shaft with respect to the partition wall;
with
2. The double rotary scroll compressor according to claim 1, wherein a pressure equalizing hole is formed in said partition wall portion for equalizing pressure between said driving portion side space and said compressing portion side space. 2. The double-rotating scroll type compression system according to claim 1, wherein a lubricant space for containing a lubricant is provided in a region between the first side plate and the center plate and on the side of the rotation axis. machine. Between the first side plate and the center plate, there is provided a lubricant introduction passage for guiding the lubricant to the lubricant space by utilizing the relative movement of the first side plate and the center plate. 4. The double rotary scroll compressor according to claim 3, wherein: A tip seal for sealing between the wall and the corresponding end plate is provided at the tip in the height direction of the wall,
A tip seal groove for accommodating the tip seal is formed at the tip in the height direction of the wall,
2. A first inclined wall portion is provided radially outward of said tip seal groove centered on said rotational axis and inclined outwardly in said radial direction toward a tip side in a height direction of said wall. 2. The dual rotary scroll compressor described in . A second inclined wall, which is radially inward about the rotational axis of the tip seal groove and is inclined symmetrically with the first inclined wall portion, is inclined radially inwardly toward a tip side in a height direction of the wall body. 6. A double rotary scroll compressor according to claim 5, wherein a section is provided. A tip seal for sealing between the wall and the corresponding end plate is provided at the tip in the height direction of the wall,
A tip seal groove for accommodating the tip seal is formed at the tip in the height direction of the wall,
2. A third inclined wall portion is provided at a circumferentially outer tip of the tip seal groove, the third inclined wall portion being inclined toward a circumferentially outer tip toward a height direction tip side of the wall body. 2. The dual rotary scroll compressor described in . 2. The double-rotating scroll type according to claim 1, wherein a circular arc portion projecting radially outward from the wall body and having a center at the center position of the end plate is provided at the winding end portion of the wall body in the circumferential direction. compressor. A projecting portion projecting radially outward from the wall body and having a positioning or fixing hole is provided at the winding end portion,
9. The double rotary scroll compressor according to claim 8, wherein the arc portion is provided on the circumferentially outer side or the circumferentially inner side of the protrusion. At a circumferentially outer portion of the wall located radially inwardly of the winding end position in the circumferential direction of the wall, a radially outwardly protruding portion from the wall and having a center at the center position of the end plate 2. A double rotary scroll compressor according to claim 1, wherein said circular arc portion is provided. An end plate extension projecting radially outward from the wall is provided at a circumferentially outer portion of the wall located radially inward of the winding end position in the circumferential direction of the wall,
the end plate extension having a small projection dimensioned radially less than the thickness of the wall;
2. The double-rotating scroll type compression according to claim 1, wherein abradable coating is applied to a surface of said small protruding portion facing said wall or a tip in a height direction of said wall facing said small protruding portion. machine. A fastening portion for fastening the first drive-side scroll member and the second drive-side scroll member with the tips of the wall bodies facing each other in the height direction is formed by the first drive-side scroll member and the second drive-side scroll member. provided in each of the drive-side scroll members, the height direction tip of the wall of one of the drive-side scroll members and the height direction tip of the fastening portion being the same height,
or
A fastening portion for fastening the first driven scroll member and the second driven scroll member in a state in which the tips of the wall bodies in the height direction are opposed to each other is provided to the first driven scroll member and the second driven scroll member. 2. The dual rotation according to claim 1, wherein each of the driven side scroll members is provided with a height direction tip of the wall of one of the driven side scroll members and a height direction tip of the fastening portion are at the same height. scroll compressor.

Images