JP2002227789A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary compressor capable of suppressing an abnormal rise of the pressure in a high pressure division in a sealed vessel and sensing an internal temperature rise of the vessel due to abnormal rise of the pressure for the purpose of protection. SOLUTION: The rotary compressor is structured so that a motor part 52, a compressing mechanism part 53, and a lubricating oil 4 are accommodated in the closed vessel 51, wherein a high pressure relief valve 65 to admit flow of a refrigerant gas only in the direction from a high pressure space to a low pressure space is installed at a stationary scroll 54 of the compressing mechanism part 53 to partition the high pressure space 100 from the low pressure space 200, and a motor protecting device 64 of current and temperature sensing type is installed at the coil end 52f of the motor part 52.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a protection device for a rotary compressor used in, for example, a refrigerating air conditioner.

[0002]

2. Description of the Related Art FIG.
Longitudinal sectional view showing a conventional rotary compressor disclosed in
9 is a sectional view taken along the line DD of the rotary compressor shown in FIG. 8, FIG. 10 is a sectional view taken along the line E--E of FIG. 9, and FIG. 11 is an enlarged detailed view of a portion F shown in FIG. As shown in FIG. 8, this conventional rotary compressor has an internal high-pressure sealed container 1 in which lubricating oil 4 is stored at the bottom.
And a motor section 2 and a compression mechanism section 3 provided in the high-pressure space 100 in the closed casing 1.

The compression mechanism 3 has a cylinder 5 disposed on the surface of the lubricating oil 4 and an eccentric shaft 2b attached to a drive shaft 2a of the electric motor 2, fitted therein.
A roller 6 that revolves while rotating within the cylinder 5 by rotation of the cylinder 5 and a vane 7 that partitions the inside of the cylinder 5 by pressing the tip 7a against the outer peripheral surface 6a of the roller 6 with an elastic body 8 (see FIG. 9). A frame 9 having a bearing 9a for rotatably supporting the drive shaft 2a and closing an upper opening of the cylinder 5, and a head 10 having a bearing 10a and closing a lower opening of the cylinder 5; It is configured.

[0004] Reference numeral 11 denotes a suction hole formed in the cylinder 5 in a radial direction, and communicates the inside of the cylinder 5 with a suction pipe 12 for introducing refrigerant gas. As shown in FIG. 10, the suction hole 11 communicates with a high-pressure relief valve 14, which will be described later, via small-diameter communication holes 13 formed in the cylinder 5 and the head 10, respectively.

As shown in FIGS. 10 and 11, the high-pressure relief valve 14 has a coil spring 14a and a valve 14b incorporated in the head 10, and a seating surface 14c which is appropriately opened and closed by the valve 14b. And a press-fitting plate 14d which is press-fitted and fixed.
The press-fit plate 14 d has a high-pressure space 100 in the closed container 1.
A U-shaped communication pipe 15 having one end opened is attached to the communication pipe 15. The communication pipe 15 immersed in the lubricating oil 4 has a plurality of small holes 15a.

Next, the operation principle of the above-described conventional rotary compressor will be described. The refrigerant gas is led from the suction pipe 12 and reaches the inside of the cylinder 5. Then, the refrigerant gas in the cylinder 5 is gradually compressed by the rollers 6 revolving by the rotation of the eccentric shaft portion 2b of the drive shaft 2a accompanying the rotation of the electric motor portion 2, and once discharged into the sealed container 1, then discharged. Discharged from the pipe 16.

When the conventional rotary compressor is mounted on a refrigerating air conditioner and operated, a condenser fan (not shown) is used.
If the high pressure in the refrigerant circuit rises abnormally due to the stop of the operation or the like, the pressure difference between the high pressure space 100 and the low pressure space 200 in the cylinder 5 causes the valve 14b of the high pressure relief valve 14 to increase the spring force Fs of the coil spring 14a. It overcomes and separates from the seating surface 14c formed on the press-fit plate 14d, and releases the pressure from the high-pressure space 100 to the low-pressure space 200. This operation makes it possible to reduce the loads on the bearings 9a and 10a of the head 9 and the frame 9 that rotatably supports the drive shaft 29.

On the other hand, the lubricating oil 4 flows into the cylinder 5 from the small hole 15a of the communication pipe 15 due to the dynamic pressure action of the refrigerant gas flowing in the communication pipe 15 due to the pressure difference between the high pressure space 100 and the low pressure space 200. The wear of the rollers 6 and the vanes 7 rotating in the cylinder 5 is prevented.

Next, another conventional rotary compressor will be described with reference to FIGS. FIG.
FIG. 13 is an enlarged detailed view of a portion G shown in FIG. 12 showing a conventional rotary compressor disclosed in Japanese Patent No. 42175.

The rotary compressor shown in FIG.
The fixed scroll 23 and the oscillating scroll 24 that form the compression chamber 300 by meshing the respective plate-shaped spiral teeth 23b and 24a provided therein, and the oscillating scroll 24 are supported in the axial direction and 24
A frame 26 that supports a drive shaft 22a of a motor unit 22 that drives the motor in a radial direction with a bearing 25, restricts the rotation of an orbiting scroll 24, and
And an Oldham ring 27 that realizes a revolving motion with respect to. In addition, the outer peripheral surface 23c of the base plate portion 23a of the fixed scroll 23 is brought into close contact with the inner wall 21a of the sealed container 21. It is partitioned into a space 100.

As shown in FIG. 13, a high pressure space 100 and a low pressure space 20 are provided on the base plate portion 23a of the fixed scroll 23.
And a communication hole 23d communicating with the communication hole 2d.
A high pressure relief valve 28 is provided in 3d.
The high-pressure relief valve 28 includes a steel ball 28a abutting against a seating surface 23e formed in the communication hole 23d, a coil spring 28b for urging the steel ball 28a against the seating surface 23e with a predetermined load, and a coil spring 28b. And a spring retainer 28c for supporting one end of the spring 28b.

The operation principle of another conventional rotary compressor configured as described above will be described. When the orbiting scroll 24 revolves with respect to the fixed scroll 23 due to the rotation of the eccentric shaft portion (not shown) of the drive shaft 22a accompanying the rotation of the motor section 22, the plate-shaped spiral of the orbiting scroll 24 and the fixed scroll 23 is formed. Compression chamber 30 formed by teeth 23b, 24a
The refrigerant gas in 0 is gradually compressed. Then, the high-pressure refrigerant gas is once discharged from the discharge port 23f of the fixed scroll 23 to the high-pressure space 100 in the sealed container 3, and is discharged from the discharge pipe 29.

When the conventional rotary compressor is mounted on a refrigerating air conditioner and operated, a condenser fan (not shown) is used.
If the high pressure in the refrigerant circuit rises abnormally due to a cause such as stoppage of the pressure, the load Fp due to the pressure difference between the high pressure space 100 and the low pressure space 200 becomes larger than the force Fs of the coil spring 28b of the high pressure relief valve 28, The ball 28a is separated from the seating surface 23e formed on the fixed scroll 23. At this time, the high pressure relief valve 28 is
To release the pressure to the low-pressure space 200 in which the motor unit 22 is housed. With this operation, the bearing load that increases due to abnormal pressure rise in the high-pressure space 100 is reduced, and damage to the rotary compressor is prevented.

Next, the conventional rotary compressor shown in FIGS. 14 and 15 will be described. FIG. 14 is a longitudinal sectional view showing another conventional rotary compressor, and FIG. 15 is an enlarged detailed view of a portion H shown in FIG. The conventional rotary compressor shown in FIG. 14 includes a motor unit 32 including a stator 32a and a rotor 32b disposed in a high-pressure space 100 in a closed container 31, and a motor unit 32.
, And a stator 32 a of the electric motor 32 is connected to the inner wall 3 of the closed vessel 31.
1a is locked by shrink fitting or the like.

Reference numeral 34 denotes a fixed scroll of the compression mechanism 33, which is fastened to the guide frame 35 by bolts (not shown) or the like. With this configuration, the fixed scroll 34
The inside of the sealed container 31 is partitioned into a high-pressure space 100 and a low-pressure space 200 at a fastening surface 34 a between the guide container 35 and the guide frame 35.

Reference numeral 36 denotes an orbiting scroll. On the upper surface of the base plate portion 36a, plate-shaped spiral teeth 36b having substantially the same shape as the plate-shaped spiral teeth 34b of the fixed scroll 34 are formed. The base plate portion 36a has a small-diameter bleed hole 36c that communicates the upper surface with a surface on the compliant frame 37 side described later. Numeral 38 denotes an Oldham ring, which restricts the rotation of the orbiting scroll 36 and serves as a fixed scroll 3.
4 has achieved revolving motion.

The compliant frame 37 is fitted and engaged with the inner peripheral surfaces 35a and 35b of the guide frame 35, and is allowed to move only in the axial direction. Also,
The compliant frame 37 is provided with a main bearing 37a for radially supporting a drive shaft 32c that is driven to rotate by the electric motor section 32, and has an outer peripheral surface 37b provided with two seal grooves 37c for accommodating a seal material such as an O-ring. It is formed in several places. One sealing groove 37c has an upper sealing material 37 in it.
d, a lower seal member 37e is fitted in the other seal groove 37c. In addition, compliant frame 37
From the surface of the thrust bearing 37f.
A communication hole 40 is formed to communicate with a space 39 formed by d, 37e, the inner peripheral surface 35c of the guide frame 35, and the outer peripheral surface 37b of the compliant frame 37.

Reference numeral 41 denotes a check valve provided on the compliant frame 37, and when a predetermined pressure difference is applied, the thrust bearing 37f of the compliant frame 37, the swing bearing 36d of the swing scroll 36, and the compliant frame 37. The space 4 sealed by the 37 main bearings 37a
2 allows only the flow of the refrigerant gas to the low-pressure space 200.

Next, the operation of this conventional rotary compressor during steady operation will be described. Closed vessel 31 during normal operation
Is guided to the boss space 43 of the orbiting scroll 36 via a high-pressure oil supply hole 32d provided through the drive shaft 32c in the axial direction. Then, the high-pressure lubricating oil 4 is reduced in pressure by the oscillating bearing 36d to become an intermediate pressure,
It flows into the space 42. As another route, the high-pressure lubricating oil 4 in the high-pressure oil supply hole 32d is guided to the lower side of the high pressure side of the main bearing 37a from the lateral hole 32e provided in the drive shaft 32c, and is depressurized by the main bearing 37a to reduce the intermediate pressure. And flows into the same space 42 as above.

At this time, the intermediate pressure Pm1 in the space 42 is given by Pm1 = Ps + α (Ps is the pressure of the low-pressure space 200) by a predetermined magnification α substantially determined by the check valve 41 provided in the compliant frame 37. Is controlled.

On the other hand, the base plate portion 36a of the orbiting scroll 36
Is constantly or intermittently communicated with the communication hole 40 provided in the compliant frame 37. For this reason, the refrigerant gas under compression from the compression chamber 300 formed by the fixed scroll 34 and the orbiting scroll 36 is supplied to the space 39 via the bleed hole 36 c of the orbiting scroll 36 and the communication hole 40 of the compliant frame 37. It is led to. Therefore, the intermediate pressure Pm2 in the space 39 is limited by the compression chamber 3 to which the bleed hole 36c substantially communicates.
Pm2 = Ps × β (Ps is the pressure of the low-pressure space 200) by a predetermined magnification β substantially determined at the position of 00.

The above arrangement, ie, two intermediate pressures Pm
1, Pm2 and the pressure of the high-pressure space 100 acting on the lower end surface 37g of the compliant frame 37, the compliant frame 37 is guided by the guide frame 35 and lifts up to the fixed scroll 34 side (upward in FIG. 15). Therefore, the orbiting scroll 36 pressed against the compliant frame 37 via the thrust bearing 37f also rises upward, and as a result, the tooth tip and the bottom of the orbiting scroll 36 are in contact with the bottom of the fixed scroll 34, respectively. Since the refrigerant gas is compressed while sliding in contact with the tooth tip, a high-efficiency rotary compressor with less leakage of the refrigerant gas can be obtained.

Also, at the time of start-up or liquid compression, the thrust direction gas load Fgt acting on the orbiting scroll 36 is Fgt.
h becomes large, and the orbiting scroll 36 becomes the thrust bearing 3
Since the compliant frame 37 is pushed down to the non-fixed scroll 34 side (downward in FIG. 15) via 7f, a comparison is made between the tip and the bottom of the orbiting scroll 36 and the bottom and the tip of the fixed scroll 34. A large gap is created,
An abnormal increase in pressure in the compression chamber 300 is avoided, and a highly reliable rotary compressor with less swirl and bearing damage is obtained.

[0024]

In the conventional rotary compressor shown in FIG. 8, when the pressure in the high-pressure space 100 rises abnormally as described above, the high-pressure relief valve 14 operates to drive the drive shaft 2a. While it is possible to temporarily prevent the bearings 9a and 10a from being damaged, the operation of the high-pressure relief valve 14 allows the high-pressure and high-temperature refrigerant gas flowing from the high-pressure space 100 to the low-pressure space 200 to be compressed. Since the compression is performed again at 3, the temperature of the discharge gas of the refrigerant sharply increases. At this time, the temperature of the electric motor unit 2 disposed in the high-pressure space 100 also rises sharply in the same manner as the discharge gas temperature, so that the insulation of the electric motor unit 2 is deteriorated, and the electric motor unit 2 is burned, and the reliability of the rotary compressor is reduced. There is a risk of significantly impairing the

The high pressure relief valve 14 continues to operate unless the abnormal rise of the high pressure space 100 converges.
The temperature of the lubricating oil 4 stored at the bottom of the sealed container 1 which is the high-pressure space 100 also increases, and there is a concern that the bearings 9a and 10a may be damaged or the lubricating oil 4 may be deteriorated due to a decrease in the viscosity of the lubricating oil 4.

Further, when the high-pressure relief valve 14 is operated, a large amount of lubricating oil 4 flows into the cylinder 5 from the plurality of small holes 15a formed in the communication pipe 15, and is compressed again together with the refrigerant gas. 100 is discharged again. At this time, since there is a limit in the separating ability of the refrigerant gas and the lubricating oil 4 in the high-pressure space 100,
The lubricating oil 4 that could not be separated by the above flows out of the closed vessel 1 from the discharge pipe 16 together with the refrigerant gas. Due to this phenomenon, the amount of the lubricating oil 4 stored at the bottom in the closed container 1 decreases, and eventually becomes exhausted, so that it is impossible to supply oil to each sliding portion and the rotary compressor is damaged. It can happen.

In the conventional rotary compressor shown in FIG. 12, when the pressure in the high-pressure space 100 rises abnormally, the high-pressure relief valve 28 operates as described above to drive the drive shaft 22a.
Although it is possible to temporarily prevent bearing damage, etc.,
On the other hand, as long as the abnormal rise of the high-pressure space 100 does not converge, the high-pressure relief valve 28 continues to operate. At this time, since the electric motor unit 22 is disposed in the low-pressure space 200, the electric motor unit 22 is less susceptible to the sudden rise in the discharge gas temperature due to the recompression of the high-pressure and high-temperature refrigerant gas flowing into the low-pressure space 200 from the high-pressure space 100. As in the above-described conventional example, although the possibility of burning of the electric motor unit 22 is low, the rotary compressor continues to operate without detecting an abnormal rise in high pressure caused by any cause. A defect such as a defect occurs. On the other hand, also in the rotary compressor, the discharge gas temperature rises abnormally as described above, so that the deterioration of the lubricating oil is promoted and the reliability of each bearing is significantly reduced.

Further, the high-pressure relief valve 28 provided in the conventional rotary compressor has a steel ball 28 as described above.
a, a coil spring 28b for urging the steel ball 28a with a predetermined load Fs, and a spring retainer 28c for supporting one end of the coil spring 28b, so that when the high-pressure relief valve 28 is actuated, Since there is no means for restricting the steel ball 28a in the radial direction, the steel ball 28a
Becomes unstable, and reliable resetting of the high-pressure relief valve 28 is hindered. When the steel ball 28a retreats from the seating surface 23e until the coil spring 28b comes into close contact with the seat surface 23e, the flow path of the refrigerant gas completely disappears, so that the pressure in the high-pressure space 100 is released to the low-pressure space 200. Even the basic function of the relief valve 28 is impaired, and abnormal pressure rise in the high-pressure space 100 cannot be avoided.

In the conventional rotary compressor shown in FIG. 14, the compliant frame 37 is guided by the two intermediate pressures Pm1 and Pm2 and the pressure of the high-pressure space 100 acting on the lower end surface 37g of the compliant frame 37. It is guided by 35 and rises to the fixed scroll 34 side (upward in FIG. 15). Therefore, the compliant frame 37 is connected via the thrust bearing 37f.
The orbiting scroll 36 pressed against the floating scroll 36 also rises upward, and as a result, the tip of the tooth of the orbiting scroll 36 and the bottom of the tooth of the orbiting scroll 36 come into contact with the respective tooth bottom and the tip of the fixed scroll 34 and slide, and the refrigerant gas is removed. Therefore, a highly efficient rotary compressor with less refrigerant gas leakage can be obtained. In addition, at the time of starting or at the time of liquid compression, the thrust direction gas load Fgth acting on the orbiting scroll 36 becomes large, and the orbiting scroll 36 moves the compliant frame 37 to the side opposite to the fixed scroll 34 via the thrust bearing 37f. 15 (downward in FIG. 15), a relatively large gap is formed between the tooth tip or tooth bottom of the orbiting scroll 36 and the tooth tip or tooth tip of the fixed scroll 34, and an abnormal pressure in the compression chamber 300 is generated. Since the rise is avoided, a highly reliable rotary compressor with less swirl and damage to the bearing can be obtained.

However, with the above-described structure, if the pressure in the high-pressure space 100 rises abnormally while maintaining high reliability in one aspect, a part of the pressure is reduced.
The pressure force of the compliant frame 37 against the fixed scroll 34, which depends on the pressure of the compliant frame 37, also increases, and the compliant frame 37 has a lower load capacity than a general journal bearing due to a low sliding speed. Since the oil film of the thrust bearing 37f formed on the frame 37 disappears, problems such as abnormal wear and seizure are induced, which has a serious problem in reliability.

The oscillating scroll 36 is connected to the compliant frame 37 via a thrust bearing 37f.
Is transmitted to the fixed scroll 34, and the pressing load is supported by the tooth tip of the orbiting scroll 36 and the tooth tip of the fixed scroll 34. In addition, abnormal wear, seizure, or the like due to an increase in the pressing force may occur at the tooth tips of the orbiting scroll 36 or the fixed scroll 34.

The present invention has been made to solve such a problem, and suppresses an abnormal increase in pressure in a high-pressure section in a closed vessel, and detects a temperature rise in the closed vessel due to the abnormal rise in pressure. It is an object to provide a rotary compressor for protection.

[0033]

According to a first aspect of the present invention, there is provided a rotary compressor comprising: a hermetic container having a bottom portion storing lubricating oil;
In a rotary compressor having an electric motor section and a compression mechanism section provided in a high-pressure space formed in the closed container, the compression mechanism section is formed to partition a high-pressure space and a low-pressure space,
A communication hole communicating between the high-pressure space and the low-pressure space, a high-pressure relief valve provided in the communication hole and allowing the flow of the refrigerant gas only from the high-pressure space to the low-pressure space, and a current / temperature detection attached to the motor unit And a motor protection device of a system.

According to a second aspect of the present invention, in the rotary compressor according to the first aspect, the current / temperature detection type motor protection device is a current detection type motor protection device and a temperature detection type motor protection device. And one of them is installed in the closed container, and the other is mounted outside the closed container.

According to a third aspect of the present invention, in the rotary compressor according to the first aspect, the current / temperature detection type motor protection device is a current detection type motor protection device and a temperature detection type motor protection device. The motor protection device of the current detection type and the motor protection device of the temperature detection type are mounted outside the closed container.

According to a fourth aspect of the present invention, in the rotary compressor according to any one of the first to third aspects, the compression mechanism portion includes: a fixed scroll having plate-shaped spiral teeth; An orbiting scroll having plate-shaped spiral teeth that mesh with the plate-shaped spiral teeth of the fixed scroll to form a compression chamber; and an electric motor unit that axially supports the orbiting scroll and drives the orbiting scroll. In a rotary compressor configured with a compliant frame that supports the drive shaft in the radial direction and a guide frame that supports the compliant frame in the radial direction, the high-pressure relief valve is provided on one of the fixed scroll and the guide frame. It is attached.

A rotary compressor according to a fifth aspect of the present invention is the rotary compressor according to any one of the first to third aspects, wherein the compression mechanism section includes a single or a plurality of cylinders having a compression chamber, A roller that revolves while rotating in the cylinder,
In a rotary compressor configured by a vane for partitioning the compression chamber and a frame and a head having a bearing that closes both side openings of the cylinder and rotatably supports a drive shaft of the motor unit, the cylinder or The high-pressure relief valve is attached to one of the frames.

According to a sixth aspect of the present invention, in the rotary compressor according to any one of the first to fifth aspects, the high-pressure relief valve is provided with a seating surface formed in a communication hole of the compression mechanism. A steel ball contacting the seating surface, a piston inserted into the communication hole with a gap to hold the steel ball, and movable only in the axial direction of the communication hole; And an elastic body for pressing the ball against the seating surface.

According to a seventh aspect of the present invention, in the rotary compressor according to any one of the first to fifth aspects, the high-pressure relief valve is provided with a seating surface formed in a communication hole of the compression mechanism. A valve that is inserted into the communication hole with a gap, abuts on the seating surface, and is movable only in the axial direction of the communication hole, and an elastic body that presses the valve against the seating surface. Things.

According to an eighth aspect of the present invention, in the rotary compressor according to any one of the first to seventh aspects, the high pressure relief valve is not immersed in the lubricating oil in the closed container. Is what you do.

According to a ninth aspect of the present invention, in the rotary compressor according to any one of the first to eighth aspects, the refrigerant to be used is any one of a hydrocarbon-based refrigerant, an HFC-based refrigerant, and a CO ₂ refrigerant. The gist is that it has been done.

[0042]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1 Hereinafter, Embodiment 1 of the present invention will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view showing Embodiment 1 of the present invention, and FIG. 2 is an enlarged detailed view of a portion A shown in FIG. The rotary compressor according to the first embodiment shown in FIG. 1 includes a hermetic container 51 in which lubricating oil 4 is stored at a bottom portion, and a stator 52 a and a rotor 52 b arranged in a high-pressure space 100 in the hermetic container 51. And a compression mechanism 53 driven by the motor 52, and a stator 52 of the motor 52.
a is locked to the inner wall 51a of the closed container 51 by shrink fitting or the like. A current / temperature detection type motor protection device 64 is mounted on the coil end 52f of the stator 52a.

The protection function of the above-described motor protection device 64 is separated into a current detection protection device 64a and a temperature detection protection device 64b, as shown in FIG. A configuration in which the other is externally attached to the closed container 51 may be employed.

As described above, the stator 52a is fixed to the inner wall 51a of the closed casing 51 by shrink fitting or the like and is disposed in the high-pressure space 100. Since the temperature of the discharge gas is substantially equal to that of the stator 52a, that is, the electric motor 52, the temperature detection and protection device 64b may be disposed outside the sealed container 51 near the shrink-fit portion of the stator 52a. The protection response in this case is slightly inferior to the embodiment shown in FIG. 1, but is very effective when there is not enough mounting space in the closed container 51, etc. Changing the protection settings is easier than with the built-in type.

Reference numeral 54 denotes a fixed scroll of the compression mechanism 53, which is fastened to the guide frame 55 by bolts (not shown) or the like. With this configuration, the fixed scroll 54
The inside of the sealed container 51 is partitioned into a high-pressure space 100 and a low-pressure space 200 at a fastening surface 54 a between the pressure vessel and the guide frame 55. A high-pressure relief valve 65 is mounted on the base plate portion 54c of the fixed scroll 54.

The high-pressure relief valve 65 is formed in the base plate portion 54c of the fixed scroll 54 as shown in FIG. 2, and is formed in a communication hole 65a for communicating the high-pressure space 100 with the low-pressure space 200 and a communication hole 65a. A steel ball 65c seated on the seating surface 65b, and a holding hole 65e that is inserted into the communication hole 65a with a gap (refrigerant gas flow path 65d) and accommodates and holds the steel ball 65c at the top, A piston 65h having refrigerant gas passages 65f and 65g formed in a cross shape in a substantially central portion, and a steel ball 65c housed in a holding hole 65e of the piston 65h are seated on a seating surface 65b of the communication hole 65a.
Coil spring 6 that urges against a predetermined load Fs
5i, and a refrigerant gas outlet hole 65j through which refrigerant gas from the high-pressure space 100 flowing through the refrigerant gas flow paths 65d and 65g flows out to the low-pressure space 200 is formed.
and a spring retainer 65k that deforms the coil spring 65i to obtain s.

If the flow area of the refrigerant gas flow path 65d formed on the outer periphery of the piston 65h can be sufficiently ensured to reduce the pressure loss, the refrigerant flow paths 65f and 65g provided in the piston 65h can be eliminated. No problem.

Further, the high pressure relief valve 65 is
May be mounted on the guide frame 55 as shown in FIG. In this case, a communication hole 65a for communicating the high-pressure space 100 and the low-pressure space 200 is provided in the guide frame 55, the steel ball 65c housed in the holding hole 65e of the piston 65h is arranged below, and the coil spring 65i is arranged above. I have. The coil spring 65i is connected to the fastening surface 54d of the fixed scroll 54.
Has been deformed. Thus, the coil spring 65i
Is deformed by the fastening surface 54d of the fixed scroll 54, there is no need to provide the spring retainer 65k described above, and the number of components can be reduced.

Reference numeral 56 denotes an orbiting scroll. On the upper surface of the base plate portion 56a, plate-shaped spiral teeth 56b having substantially the same shape as the plate-shaped spiral teeth 54b of the fixed scroll 54 are formed. A small-diameter bleed hole 65c is formed in the base plate portion 56a of the orbiting scroll 56 so as to communicate the upper surface with the surface on the compliant frame 57 side. Reference numeral 58 denotes an Oldham ring, which restricts the rotation of the orbiting scroll 56 and realizes a revolving motion with respect to the fixed scroll 54.

Reference numeral 57 denotes a compliant frame which is fitted and engaged with the inner peripheral surfaces 55a and 55b of the guide frame 55, and is allowed to move only in the axial direction. The compliant frame 57 is formed with a main bearing 57a that radially supports a drive shaft 52c that is driven to rotate by the electric motor section 52, and has an outer peripheral surface 57b with a seal groove for accommodating a seal material such as an O-ring. 57c are formed in two places. One sealing groove 57c has an upper sealing material 57d.
However, a lower seal member 57e is fitted in the other seal groove 57c. Further, the two sealing members 57 are viewed from the thrust bearing 57f of the compliant frame 57.
A communication hole 60 that communicates with a space 59 formed by the inner peripheral surface 55c of the guide frame 55 and the outer peripheral surface 57b of the compliant frame 57 is formed.

Reference numeral 61 denotes a check valve provided on the compliant frame 57. When a predetermined pressure difference is applied, the thrust bearing 57f of the compliant frame 57, the swing bearing 56d of the swing scroll 56, and the compliant frame The space 6 sealed by the main bearing 57a
2 allows only the flow of the refrigerant gas to the low-pressure space 200.

Next, the operation of the rotary compressor according to Embodiment 1 during steady operation will be described. During a steady operation, the lubricating oil 4 at the bottom of the closed vessel 51 is guided to the boss space 63 of the orbiting scroll 56 via a high-pressure oil supply hole 52d provided through the drive shaft 52c in the axial direction. Then, the high-pressure lubricating oil 4 is reduced in pressure by the oscillating bearing 56 d to have an intermediate pressure, and flows into the space 62. As another route, the high-pressure lubricating oil 4 in the high-pressure oil supply hole 52d is guided to the lower side of the high pressure side of the main bearing 57a from the lateral hole 52e provided in the drive shaft 52c, and is depressurized by the main bearing 57a to reduce the intermediate pressure. And flows into the same space 62 as above.

At this time, the intermediate pressure Pm1 in the space 62 is Pm1 = Ps + α (Ps is the pressure of the low-pressure space 200) by a predetermined magnification α substantially determined by a check valve 61 provided in the compliant frame 57. Is controlled.

On the other hand, the base plate portion 56a of the orbiting scroll 56
Is constantly or intermittently communicated with a communication hole 60 provided in the compliant frame 57. Therefore, the refrigerant gas during compression from the compression chamber 300 formed by the fixed scroll 54 and the orbiting scroll 56 is supplied to the space 59 through the bleed hole 56 c of the orbiting scroll 56 and the communication hole 60 of the compliant frame 57. It is led to. Therefore, the intermediate pressure Pm2 in the space 59 is limited by the compression chamber 3 to which the bleed hole 56c substantially communicates.
Pm2 = Ps × β (Ps is the pressure of the low-pressure space 200) by a predetermined magnification β substantially determined at the position of 00.

The above configuration, ie, two intermediate pressures Pm
1, Pm2 and the pressure of the high-pressure space 100 acting on the lower end face 57g of the compliant frame 57, the compliant frame 57 is guided by the guide frame 55 and floats to the fixed scroll 56 side (upward in FIG. 1). Therefore, the orbiting scroll 56 pressed against the compliant frame 57 via the thrust bearing 57f also rises upward, and as a result, the tooth tip and the root of the orbiting scroll 56 are in contact with the root of the fixed scroll 54, respectively. Since the refrigerant gas is compressed while sliding in contact with the tooth tip, a high-efficiency rotary compressor with less leakage of the refrigerant gas can be obtained.

Also, at the time of starting or at the time of liquid compression, the thrust direction gas load Fgt acting on the orbiting scroll 56 is Fgt.
h becomes large, and the orbiting scroll 56 becomes a thrust bearing 57
f, the compliant frame 57 is pushed down to the side opposite to the fixed scroll 54 (downward in FIG. 1).
The fixed scroll 54 and the tip or bottom of the orbiting scroll 56
A relatively large gap is formed between the tooth bottom and the tooth tip, and an abnormal increase in pressure in the compression chamber 300 is avoided, so that a highly reliable rotary compressor with less swirl and damage to the bearing can be obtained. .

When the rotary compressor according to the first embodiment is mounted on a refrigeration air conditioner and operated, if the high pressure in the refrigerant circuit rises abnormally due to a stop of a condenser fan (not shown) or the like. The load Fp due to the pressure difference between the high-pressure space 100 and the low-pressure space 200 is larger than a predetermined load Fs by the coil spring 65i of the high-pressure relief valve 65. At this time, the steel ball 65c of the high-pressure relief valve 65 is separated from the seating surface 65b formed in the communication hole 65a, and releases pressure from the high-pressure space 100 to the low-pressure space 200.

By this operation, part of the high-pressure space 10
Compliant frame 57 dependent on zero pressure
The pressing force against the fixed scroll 54 is prevented from being excessively large, so that the compliant frame 57 is formed to have a lower load capacity than a general journal bearing due to a low sliding speed or the like. In the thrust bearing 57f, a sufficient oil film is formed, and a more reliable rotary compressor can be obtained.

The high-pressure relief valve 65 is also provided at the tip of the orbiting scroll 56 and the tip of the fixed scroll 54 that support the pressing force of the compliant frame 57 against the fixed scroll 54 via the thrust bearing 57f.
As a result, an abnormal increase in the pressure of the high-pressure space 100 is avoided, so that the possibility of abnormal wear or burn-in of the tooth tip due to an increase in the pressing force is extremely reduced.

When the high-pressure relief valve 65 is operated, the high-pressure and high-temperature refrigerant gas flowing from the high-pressure space 100 to the low-pressure space 200 is compressed again by the compression mechanism 53, and the temperature of the discharge gas of the refrigerant rises sharply. The electric motor unit 52 disposed in the high-pressure space 100 from which the discharge gas is once released.
Also, the temperature rises almost in synchronism with the rapid rise in the discharge gas temperature. However, the current / temperature detection type motor protection device 64 attached to the coil end 52f of the motor unit 52 detects the temperature rise of the motor unit 52. As a result, the rotary compressor is stopped, so that deterioration and burnout of the insulating material of the electric motor section 52 can be prevented, and high reliability can be obtained.

A steel ball 65c constituting the high-pressure relief valve 65 is inserted into a communication hole 65a formed in the base plate portion 54c of the fixed scroll 54, and its radial movement is restricted, and the axial direction of the communication hole 65a is restricted. Are accommodated in a holding hole 65e provided substantially at the center of the piston 65h, which allows only the movement of the piston 65h.
The steel ball 65c is released from the urging state by the coil spring 65i via the piston 65h and separated from the seating surface 65b formed in the communication hole 65a due to the pressure difference between the high pressure space 100 and the low pressure space 200. Even when the steel ball 65c is opened, the steel ball 65c exhibits one-dimensional stable behavior only in the axial direction of the communication hole 65a without causing unstable three-dimensional behavior, so that the high-pressure relief valve 65 is reliably reset ( Here, the pressure difference between the high-pressure space 100 and the low-pressure space 200 is reduced, and it is possible to perform the state in which the steel ball 65c is pressed against the seating surface 65b of the communication hole 65a again.) Further, since the contact with the communication hole 65a due to the unstable behavior of the steel ball 65c cannot occur, there is an effect that the inside of the communication hole 65a does not wear.

Further, even when the steel ball 65c retreats with respect to the seating surface 65b until the coil spring 65i comes into close contact (the total length of the spring = the number of turns × the spring wire diameter), the piston 65h
Has refrigerant gas passages 65f and 65g, and spring retainers 65k.
Is formed with a refrigerant gas outlet hole 65j, a refrigerant flow path from the high-pressure space 100 to the low-pressure space 200 is secured, and it is possible to reliably avoid abnormal pressure increase.

When the high pressure in the refrigerant circuit rises abnormally due to the stoppage of the condenser fan of the refrigeration / air-conditioning equipment, the high pressure relief valve 65 releases the pressure from the high pressure space 100 to the low pressure space 200. Problems such as bearing damage due to abnormal rise are eliminated. Further, the discharge gas temperature of the refrigerant, which rises rapidly by recompressing the high pressure and high temperature refrigerant gas flowing from the high pressure space 100 into the low pressure space 200 by the compression mechanism 53, is detected by a current / temperature detection method attached to the motor 52. Since the detection can be performed by the motor protection device 54, it is possible to stop the rotary compressor and protect it before a catastrophic failure such as insulation material deterioration or burnout of the motor unit 52, thereby ensuring high reliability. There is an effect that can be.

Embodiment 2 FIG. 5 is a vertical sectional view of a rotary compressor showing a second embodiment of the present invention, and FIG. 6 is an enlarged detailed view of a portion B shown in FIG. The rotary compressor according to the second embodiment shown in FIG. 5 has an internal high-pressure sealed container 71 in which lubricating oil 4 is stored at the bottom, a motor unit 72 provided in a high-pressure space 100 in the sealed container 71, and a compression mechanism unit. 73.

The compression mechanism 73 includes a cylinder 74,
An eccentric shaft portion 72b attached to a drive shaft 72a of the electric motor portion 72 is fitted therein. A roller 75 that revolves while rotating in the cylinder 74 by the rotation of the eccentric shaft portion 72b.
And a vane 76 for partitioning the inside of the cylinder 74 by pressing a tip end portion 76a against an outer peripheral surface 75a of a roller 75 by an elastic body 76b, and a bearing 7 for rotatably supporting a drive shaft 72a.
7b, a frame 77 for closing the upper opening of the cylinder 74, and a head 78 having a bearing 76c for rotatably supporting the driving shaft 72a at the tip and closing the lower opening of the cylinder 74. ing.

Reference numeral 79 denotes a suction hole formed in the cylinder 74 in the radial direction, and a suction pipe 80 for introducing refrigerant gas and a cylinder 7.
4 communicates. 81 is the lubricating oil 4 in the closed container 71
This is a high-pressure relief valve attached to the flange 77a of the frame 77 so as not to be immersed in the frame 77. The high-pressure relief valve 81 is formed by drilling a flange 77 a of a frame 77.
A communication hole 81b having a seating surface 81a;
b and a communication hole 81c that communicates with the suction hole 79 of the cylinder 74, and a gap (a refrigerant gas flow path 8) in the communication hole 81b.
1d), a valve 81g having refrigerant gas flow passages 81e and 81f formed in a T-shape at the center thereof;
The end surface of the valve 81g is connected to the seating surface 81a of the communication hole 81b.
Coil spring 8 that presses and urges against a predetermined load Fs
1h, and a refrigerant gas outlet hole 81i for allowing the refrigerant gas from the high pressure space 100 flowing through the refrigerant gas flow paths 81d and 81f to flow to the low pressure space 200 is formed.
and a spring retainer 81j that deforms the coil spring 81h to obtain s.

Next, the operation principle of the rotary compressor according to the second embodiment will be described. The refrigerant gas is guided from the suction pipe 80 and reaches the inside of the cylinder 74. Then, the refrigerant gas in the cylinder 74 is gradually compressed by the roller 75 revolving by the rotation of the eccentric shaft portion 72b of the drive shaft 72a accompanying the rotation of the electric motor portion 72, and is once discharged into the sealed container 71, and then discharged. Discharged from the tube 83.

When the rotary compressor is mounted on a refrigerating air conditioner and operated, if the high pressure in the refrigerant circuit rises abnormally due to a stop of a condenser fan (not shown) or the like, the high pressure space 100 The load Fp due to the pressure difference in the low-pressure space 200 is changed by the coil spring 81 of the high-pressure relief valve 81.
h is larger than a predetermined load Fs. At this time, the valve 81g separates from the seating surface 27b of the communication hole 81a, and releases pressure from the high-pressure space 100 to the low-pressure space 200.

By the operation of the high-pressure relief valve 81, the load increases when the high pressure rises. The bearing 77b of the frame 77, the bearing 76c of the head 76, and the vane 76
Since the contact force between the tip end portion 76a of the roller 75 and the outer peripheral surface 75a of the roller 75 can be maintained within an allowable range, a highly reliable rotary compressor with little wear can be obtained.

When the high-pressure relief valve 81 is operated, the high-pressure high-temperature refrigerant gas flowing from the high-pressure space 100 to the low-pressure space 200 is compressed again by the compression mechanism 73, and the discharge gas temperature of the refrigerant rapidly rises. The temperature of the electric motor 72 arranged in the high-pressure space 4 from which the discharge gas is once discharged also rises substantially in synchronization with the rapid rise in the temperature of the discharge gas. The detection type motor protection device 82 is
Since the rotation compressor is stopped by detecting the temperature rise of the motor, deterioration and burnout of the insulating material of the motor 72 can be prevented, and high reliability can be obtained.

A valve 81g constituting the high-pressure relief valve 81 is inserted into a communication hole 81b formed in a flange 77a of the frame 77, and its radial movement is restricted. Since only the movement is permitted, the pressure difference between the high-pressure space 100 and the low-pressure space 200 causes the valve 81g to be released from the state of being pressed and urged by the coil spring 81h, and the seating surface 8 formed in the communication hole 81b.
When the pressure is released from the high-pressure space 100 to the low-pressure space 200, the valve 81g does not cause unstable three-dimensional behavior, and is one-dimensionally stable only in the axial direction of the communication hole 81b. Since the behavior is shown, the high-pressure relief valve 81 is surely reset (here, the pressure difference between the high-pressure space 100 and the low-pressure space 200 is reduced, and
g means that the end face is pressed and urged against the seating surface 81a of the communication hole 81b. ) Is guaranteed. Further, since the outer peripheral portion of the valve 81g is always supported by the inner wall of the communication hole 81b, the valve 81g does not pry and malfunction.

Further, the high pressure relief valve 81 is
Since the refrigerant gas is not immersed in the lubricating oil 4, the refrigerant gas flowing from the high-pressure space 100 to the low-pressure space 200 during the operation of the high-pressure relief valve 81 does not enter a large amount of the lubricating oil 4 and flows into the cylinder 74 again. After being compressed together with the refrigerant gas, the amount of the lubricating oil 4 in the refrigerant gas discharged to the high-pressure space 100 again is small. Accordingly, the separation of the refrigerant gas and the lubricating oil 4 in the high-pressure space 100 is reliably performed, and the lubricating oil 4 in the closed container 71 does not flow out from the discharge pipe 83 to the outside of the closed container 71 together with the refrigerant gas. It does not run out.

In the second embodiment, the high pressure relief valve 81 is provided on the flange 77a of the frame 77, but may be mounted on the cylinder 74 as shown in FIG. The high-pressure relief valve 91 shown in FIG. 7 has a hollow cylindrical case 91b in which a distal end portion 91a is fitted into a mounting hole 74a of a cylinder 74, and a seal provided at an upper part in the case 91b and having a seating surface 91c formed thereon. Plate 91d
And a steel ball 91e in contact with the seating surface 91c of the seal plate 91d and a gap (refrigerant gas flow path f) in the case 91b.
The piston 91j has a holding hole 91g for storing and holding the steel ball 91e at the top, and has a cross-shaped refrigerant gas flow passage 91h, 91i at a substantially central portion.
And a coil spring 91k for urging the steel ball 91e held by the piston 91j against a seating surface 91c formed on the seal plate 91d with a predetermined load Fs. The tip 91a of the case 91b is attached to the cylinder 74 by means such as bolting or welding.

Embodiment 3 Next, an embodiment of the present invention
3 will be described. The rotary compressor of the embodiment
Rotary compression configured as in Embodiment 1 or Embodiment 2
Machine, hydrocarbon-based refrigerants such as propane and isobutane
Or an HFC-based refrigerant such as HFC32 or CO _TwoCool refrigerant
It is enclosed in a freezing air conditioner.

[0075] In the thus constructed rotary compressor, the operating pressure of the refrigerant using a very high becomes HFC32 refrigerant and CO ₂ refrigerant as compared with the conventional HCFC2 like, also, ozone layer depletion and global warming Also in the case of suppressing, the abnormal increase of the high pressure is suppressed by the high-pressure relief valves 65 and 81, and the motor protection devices 64 and 8 are prevented from entering the failure mode.
2 Because the compressor can be stopped and protected with higher responsiveness,
It is possible to reliably prevent abnormal wear and seizure of the sliding portion. In addition, the motor units 52, 72
Therefore, even if a hydrocarbon-based flammable refrigerant such as propane or isobutane is used, there is almost no risk of explosion, and a safe refrigeration / air-conditioning apparatus can be provided.

[0076]

According to the first aspect of the present invention, a communication hole for communicating the high pressure space and the low pressure space is formed in the compression mechanism, and the flow of the refrigerant gas from the high pressure space to the low pressure space is formed in the communication hole. A high-pressure relief valve that allows only pressure is provided, and a motor protection device is attached to the motor section arranged in the high-pressure space, so an abnormal rise in pressure in the high-pressure space in the closed vessel is suppressed by the high-pressure relief valve, and the high-pressure relief valve An increase in the discharge gas temperature due to the inflowing compressed gas can be suppressed by the electric motor protection device of the current / temperature detection system. Therefore, it is possible to suppress bearing damage, deterioration of the insulating material of the motor, and the like.

According to the invention of claim 2 of the present application, the current / temperature detection type motor protection device is separated into a current detection type motor protection device and a temperature detection type motor protection device, and one of them is a sealed container. The protection set value according to the applied refrigeration / air-conditioning device can be relatively easily changed, since one of the two protection devices is a protection device. A new effect is obtained such that chemical resistance such as refrigerant resistance and lubricating oil resistance becomes unnecessary. Also, this is an effective means when there is no sufficient mounting space in the closed container.

According to the invention of claim 3 of the present application, the current / temperature detection type motor protection device is separated into a current detection type motor protection device and a temperature detection type motor protection device. Since the protection device and the motor protection device of the temperature detection type are mounted outside the closed container, it is easy to change the protection set value according to the applied refrigeration / air-conditioning device, and the protection device itself has refrigerant resistance and resistance. New effects are obtained, such as no need for chemical resistance such as lubricating oil properties. Also, this is an effective means when there is no sufficient mounting space in the closed container.

According to the invention of claim 4 of the present application, the compression mechanism is constituted by a fixed scroll having plate-shaped spiral teeth formed therein, and a plate-shaped spiral formed by engaging the plate-shaped spiral teeth of the fixed scroll to form a compression chamber. An oscillating scroll having teeth, a compliant frame that supports the oscillating scroll in the axial direction, and radially supports a drive shaft of the electric motor unit that drives the oscillating scroll; A high-pressure relief valve is attached to either the fixed scroll or the guide frame in the rotary compressor configured with the guide frame that supports in the direction. If the pressure rises abnormally, the high-pressure relief valve releases pressure from the high-pressure space to the low-pressure space. The pressing force of the compliant frame on the fixed scroll, which depends on the high pressure, is prevented from becoming excessively large, and the load capacity is assumed to be lower than that of a general journal bearing due to a low sliding speed. A sufficient oil film is also formed on the thrust bearing formed on the compliant frame, and a more reliable rotary compressor can be obtained. In addition, the high pressure relief valve is used to increase the pressure at the tip of the plate-shaped spiral tooth of the orbiting scroll or the plate-shaped spiral tooth of the fixed scroll that supports the pressing force of the compliant frame against the fixed scroll via the thrust bearing. Since an abnormal increase in pressure in the space is avoided, the possibility of occurrence of abnormal wear, seizure, or the like due to an increase in the pressing force is extremely reduced.

According to the invention of claim 5 of the present application, the compression mechanism section divides the compression chamber into a single or a plurality of cylinders having a compression chamber, a roller which revolves while rotating in each cylinder. In a rotary compressor including a vane, a frame and a head having a bearing that closes both side openings of a cylinder and rotatably supports a drive shaft of a motor unit, the high-pressure relief is applied to one of a cylinder and a frame. If a high pressure in the refrigerant circuit rises abnormally due to a stoppage of the condenser fan in the refrigeration and air conditioning equipment, the high pressure relief valve operates to release the pressure from the high pressure space to the low pressure space. Allows the contact force between the outer periphery of the roller and the bearings of the frame, head bearing, etc. Can be kept in the 囲内, it is possible to obtain a rotary compressor wear less reliable.

According to the invention of claim 6 of the present application, the high pressure relief valve has a seating surface formed in the communication hole of the compression mechanism, a steel ball in contact with the seating surface, and a gap in the communication hole. The high pressure relief valve is actuated by a piston that is inserted and held to hold the steel ball, and is movable only in the axial direction of the communication hole, and an elastic body that presses the steel ball against the seating surface via the piston. In some cases, the steel ball exhibits one-dimensional stable behavior only in the axial direction of the communication hole without causing unstable three-dimensional behavior, and it is possible to reliably reset the high-pressure relief valve. Further, since the contact between the communication hole and the steel ball due to the unstable behavior of the steel ball cannot occur, abrasion cannot occur on the inner wall of the communication hole.

According to the invention of claim 7 of the present application, the high-pressure relief valve is inserted into the communication hole of the compression mechanism with a gap between the communication hole and the communication hole, and is inserted into the seat with a gap. When the high-pressure relief valve is activated, the valve has an unstable three-dimensional behavior because it is constituted by a valve that abuts and moves only in the axial direction of the communication hole and an elastic body that presses the valve against the seating surface. Without causing the problem, a one-dimensional stable behavior is exhibited only in the axial direction of the communication hole, and the high-pressure relief valve can be reliably reset. Further, since the valve behavior is unstable, that is, collision between the inner wall of the communication hole and the valve due to so-called jamming cannot occur, abrasion does not occur on the inner wall of the communication hole and the like, and it is also possible to solve the problem of prying operation failure. .

According to the invention of claim 8 of the present application, since the high-pressure relief valve is not immersed in the lubricating oil in the closed vessel, the refrigerant gas flowing from the high-pressure space to the low-pressure space when the high-pressure relief valve is operated. Does not allow a large amount of lubricating oil to be mixed in, so that the lubricating oil does not flow out of the closed vessel from the discharge pipe together with the refrigerant gas, and the lubricating oil in the closed vessel is not depleted. Since reliable lubricating oil is supplied, it is possible to obtain a more reliable rotary compressor.

According to the ninth aspect of the present invention, since the refrigerant to be used is any one of a hydrocarbon refrigerant, an HFC refrigerant, and a CO ₂ refrigerant, the operating pressure of the refrigerant is much higher than that of the conventional HCFC22 or the like. It becomes higher by using the HFC32 refrigerant and CO ₂ refrigerant, even in the case of suppressing the ozone layer depletion and global warming, suppresses abnormal increase in pressure by the high pressure relief valve, high by the motor protector against failure mode rush The rotary compressor can be stopped and protected with responsiveness, so that abnormal wear and seizure of the sliding portion can be reliably prevented. In addition, since the electric motor cannot be burned, a safe refrigeration and air-conditioning apparatus can be provided which has a low risk of explosion even when a hydrocarbon-based flammable refrigerant such as propane or isobutane is used.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing Embodiment 1 of the present invention.

FIG. 2 is an enlarged detailed view of a portion A shown in FIG.

FIG. 3 is a longitudinal sectional view showing another protection mode according to the first embodiment.

FIG. 4 is a longitudinal sectional view showing another high-pressure relief valve according to the first embodiment.

FIG. 5 is a longitudinal sectional view of a rotary compressor according to a second embodiment of the present invention.

6 is an enlarged detailed view of a portion B shown in FIG.

FIG. 7 is a longitudinal sectional view showing another high-pressure relief valve according to the second embodiment.

FIG. 8 is a longitudinal sectional view showing a conventional rotary compressor disclosed in Japanese Patent Application Laid-Open No. 58-101291.

9 is a cross-sectional view of the rotary compressor shown in FIG.

FIG. 10 is a sectional view taken along the line EE of FIG. 9;

FIG. 11 is an enlarged detail view of a portion F shown in FIG. 10;

FIG. 12 is a longitudinal sectional view showing a conventional rotary compressor disclosed in Japanese Patent Application Laid-Open No. 9-42175.

FIG. 13 is an enlarged detailed view of a portion G shown in FIG.

FIG. 14 is a longitudinal sectional view showing another conventional rotary compressor.

FIG. 15 is an enlarged detailed view of a portion H shown in FIG.

[Explanation of symbols]

51, 71 Closed container, 51a Inner wall, 52, 72 Motor unit, 52a Stator, 52b Rotor, 52c, 7
2a drive shaft, 52d high-pressure oil supply hole, 52e side hole, 5
2f, 72c Coil end, 53, 73 Compression mechanism, 54 Fixed scroll, 54a, 54d Fastening surface,
54b plate-shaped spiral tooth, 54c base plate portion, 55 guide frame, 55a, 55b, 55c inner peripheral surface, 56 swing scroll, 56a base plate portion, 56b plate-shaped spiral tooth, 5
6c Bleed hole, 56d swing bearing, 57 compliant frame, 57a main bearing, 57b, 75a outer peripheral surface, 57c seal groove, 57d upper seal material, 57e
Lower seal material, 57f thrust bearing, 57g lower end face,
58 Oldham ring, 59, 62 space, 60 communication hole, 61 check valve, 63 boss space, 64, 82 Motor protection device, 64a Current detection protection device, 64b
Temperature detection protection device, 65, 81, 91 High pressure relief valve, 65a, 81b, 81c Communication hole, 65b, 8
1a, 91c seating surface, 65c, 91e steel ball, 65d,
65f, 65g, 81d, 81e, 81f, 91f Refrigerant gas flow path, 65e, 91g Holding hole, 65h, 91j
Piston, 65i, 81h, 91k Coil spring, 6
5j, 81i Refrigerant gas outflow hole, 65k, 81j Spring retainer, 72b Eccentric shaft part, 74 cylinder, 74a mounting hole, 75 roller, 76 head, 76a, 91a
Tip, 76b Elastic body, 76c, 77b Bearing, 77
Frame, 78 vane, 77a flange, 79 suction hole, 80 suction pipe, 81g valve, 83 discharge pipe, 9
1d seal plate, 91b case, 100 high-pressure space, 200 low-pressure space, 300 compression chamber.

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Fumiaki Sano 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsui Electric Co., Ltd. (72) Inventor Tsuyoshi Fushiki 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Rishi Electric Co., Ltd. (72) Inventor Teruhiko Nishiki 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsui Electric Co., Ltd. Incorporated (72) Inventor Shin Sekiya 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsubishi Electric Corporation (72) Inventor Susumu Kawaguchi 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsubishi Electric Corporation F term (reference) 3H003 AA05 AB03 AB04 AC03 CC02 CD01 CD03 CE03 CF04 3H029 AA02 AA04 AA13 AA14 AB03 BB11 BB47 CC07 CC09 CC13 CC23 CC27 CC56 CC59 CC65 CC82 3H0 39 AA03 AA06 AA12 BB12 BB17 BB25 CC03 CC08 CC27 CC30 CC32 CC33

Claims (9)

[Claims] 1. A closed container having lubricating oil stored in a bottom thereof,
In a rotary compressor having an electric motor section and a compression mechanism section provided in a high-pressure space formed in the closed container, a compression mechanism section that partitions a high-pressure space and a low-pressure space is formed. A high-pressure relief valve provided in the communication hole to allow the flow of the refrigerant gas only from the high-pressure space to the low-pressure space; and a current / temperature detection type motor protection device attached to the motor unit. A rotary compressor comprising: 2. The motor protection device of the current / temperature detection system is separated into a motor protection device of a current detection system and a motor protection device of a temperature detection system, one of which is installed in the closed container and the other is installed. The rotary compressor according to claim 1, wherein the rotary compressor is mounted outside the closed container. 3. The current / temperature detection type motor protection device is separated into a current detection type motor protection device and a temperature detection type motor protection device, and the current detection type motor protection device and the temperature detection type motor are provided. 2. The rotary compressor according to claim 1, wherein a protection device is mounted outside the closed container. 4. A fixed scroll having plate-shaped spiral teeth formed therein, an orbiting scroll having plate-shaped spiral teeth meshing with the plate-shaped spiral teeth of the fixed scroll to form a compression chamber, A compliant frame that supports the orbiting scroll in the axial direction and radially supports a drive shaft of the electric motor unit that drives the orbiting scroll, and a guide frame that supports the compliant frame in the radial direction. The rotary compressor according to any one of claims 1 to 3, wherein the high-pressure relief valve is attached to one of the fixed scroll and the guide frame. 5. A compression mechanism comprising: a single or a plurality of cylinders each having a compression chamber; a roller revolving while rotating in each cylinder; a vane defining the compression chamber; and both sides of the cylinder. In a rotary compressor configured to include a frame and a head having a bearing that rotatably supports a drive shaft of the electric motor unit while closing an opening, the high-pressure relief valve is attached to one of the cylinder and the frame. Claims 1-3 characterized by the above-mentioned.
A rotary compressor according to any one of the above. 6. The high-pressure relief valve is inserted into the communication hole of the compression mechanism with a gap between the communication hole, a steel ball contacting the seating surface, and a steel ball. A piston which holds the ball and is movable only in the axial direction of the communication hole, and an elastic body which presses the steel ball against the seating surface via the piston. 5. The rotary compressor according to any one of 5. 7. The high-pressure relief valve is inserted into the communication hole of the compression mechanism portion with a gap between the communication hole and the communication hole, and is brought into contact with the seat surface. The rotary compressor according to any one of claims 1 to 5, comprising a valve movable only in a direction, and an elastic body that presses the valve against the seating surface. 8. The high pressure relief valve is not immersed in lubricating oil in the closed container.
8. The rotary compressor according to any one of 7 above. 9. The rotary compressor according to claim 1, wherein the refrigerant used is any one of a hydrocarbon-based refrigerant, an HFC-based refrigerant, and a CO ₂ refrigerant.