JPS63150490A - Scroll gas compressor - Google Patents

Abstract

PURPOSE:To obtain the captioned device having high efficiency and the superior durability by realizing an oil feeding passage controller having a wide application range by utilizing the pressure difference between a suction chamber and compression chamber which does not communicate to a discharge chamber and the suction chamber. CONSTITUTION:A compressor starts operation, and a swire scroll 10 performs a turning movement to inhale the gas in a suction chamber 33 into a compression chamber, and said gas is compressed to a certain compression ratio and then discharged into a discharge chamber 5. Further, the plunger of an oil feeding passage control valve device 17 installed midway in an oil feeding passage is advanced by the differential pressure force between a back pressure chamber A36 communicating to the first compressor which does not communicate to the discharge chamber 5 nor the suction chamber 33 and a back pressure chamber B39 which communicates to the second compression chamber communicating to the suction chamber 33, and the oil feeding passage is opened, and the lubricating oil in an oil reservoir part 23 is supplied to the space where lubrication is necessary, by the differential pressure. While, when the compressor stops, the pressure in the compression space and the pressure in the suction chamber 33 are made nearly equal through the gap of the compression space, and also the differential pressure between in the both back pressure chambers A and B becomes zero, and the plunger retreats to cut off the oil feeding passage.

Description

[Detailed description of the invention] Industrial applications The present invention relates to a scroll gas compressor.

Conventional technology Scroll compressors with low vibration and low noise characteristics have a suction chamber on the outer periphery and a discharge boat in the center of the vortex. It is generally known that a rotary compressor does not require a discharge valve for compressing fluid, has a constant compression ratio, has relatively small discharge pulsation, and does not require a large discharge space.

However, especially when compressing gas, it is necessary to make the dimensional accuracy of the scroll part extremely high in order to reduce the leakage gap in the compression part. The problem was that the machine cost was high and performance varied greatly.

Therefore, as a measure to solve this kind of problem, it is expected that the dimensional accuracy of the spiral part will be optimized and the compressor performance will be stabilized by the sealing effect using a lubricating oil film to prevent gas leakage during compression. (The configuration shown in Fig. 18 is considered, in which a part of the lubricating oil supplied to the sliding part flows into the compression chamber together with the suction gas, and after the lubricating oil is separated from the compressed gas after being compressed and discharged, the oil return passage is opened. The cap 5 provided in the discharge space 582 is designed to reduce lubricant oil leakage to the outside of the compressor by returning the lubricant oil to the space communicating with the lubricant reservoir through the
The lubricating oil separated from the compressed gas in the space 520 in the 19 is returned to the space 580 which becomes the suction passage through the oil return passages of the holes 522 to 584, collected in the oil sump 508, and returned to the sliding part by the pump device. The structure was supplied (Japanese Patent Laid-Open No. 60-75795).

In addition, the configuration shown in FIG. 19 is also considered, in which the lubricating oil contained in the compressed gas is separated by an oil separation element 672 provided in the discharge chamber 674, and the lubricating oil is collected in an oil reservoir 673 on the fixed scroll end plate 603. After the sliding surface 631 between the fixed scroll 601 and the orbiting scroll 606 is lubricated with differential pressure, lubricating oil is allowed to flow into the suction chamber 699 to reduce leakage of compressed gas in the compression chamber by the sealing effect of the oil film. (Japanese Unexamined Patent Publication No. 165787/1987).

Alternatively, a configuration in which lubricating oil is directly flowed into the compression chamber during compression as shown in FIGS. 20 and 21 is also considered, and in FIG. It has a structure in which the internal space 702 of the sealed container is used as a discharge chamber, and the lubricating oil in the oil reservoir 710 at the bottom of the discharge chamber is directly flowed into the compression chamber 723 in the middle of compression through the oil suction pipe 722 (as disclosed in Japanese Patent Application Laid-Open No. Publication No. 57-8386), No. 21
The figure shows a structure in which a compression section is placed in the upper part of a closed container 801 and a motor 803 is placed in the lower part, and a space 802 inside the closed container is used as a discharge chamber. Orbiting scroll 804
A back pressure chamber 808 in an intermediate pressure state provided on the back side on the side opposite to the compression chamber.
A sleeve hole 89 in the drive shaft 802 provided before and after the
9. The lubricating oil in the oil reservoir 809 at the bottom of the closed container 801 is caused to flow through the oil supply pipe 815 into the compression chamber 823 during compression by differential pressure (Japanese Patent Laid-Open No. 59-110893
Publication No.).

Problems to be Solved by the Invention However, if the oil return passage (hole 5
In the configuration in which the discharge space 582 and the low pressure side space 580 are always in communication through the holes 22 to 584), even if lubricating oil is always present in the space 520 and the discharge space 582, the rotation of the compressor drive shaft is prevented. As the speed changes, the amount of oil supplied to the sliding parts changes, and the amount of lubricating oil contained in the compressed gas also changes, as well as the differential pressure between the discharge space 582 and the low-pressure side space 580 and the viscosity of the lubricating oil. It is extremely difficult to set up an oil return passage that returns the lubricating oil in just the right amount, and when the compressor is operating at high speed, the amount of lubricating oil discharged is large, preventing large amounts of lubricating oil from leaking outside the compressor. It is impossible.

Furthermore, while the compressor is stopped, the lubricating oil in the space 520 and the discharge space 582 flows into the oil sump 508 at the bottom of the compressor due to differential pressure and dead weight, and for a while after the compressor is restarted, the lubricating oil in the space 520 and the discharge space 582 flows into the space 520 and the discharge space 5B2. There is not enough lubricating oil, and a large amount of compressed gas passes through the oil return passage (holes 522 to 584) to the space 5 on the low pressure side.
There was a problem in that the suction efficiency and compression efficiency were significantly lowered and the durability was deteriorated.

In addition, a fixed scroll end plate 60 as shown in FIG.
In the configuration in which the lubricating oil in the oil reservoir 673 above 3 flows into the suction chamber 699 through the sliding surface 631, when the compressor drive shaft rotates at high speed and the gas discharge amount increases, as in the case of FIG. There are also situations where there is no lubricant in the reservoir 673. In such a case, a large amount of compressed gas in the discharge chamber 674 flows into the suction chamber 699 via the sliding surface 631, causing not only a significant decrease in suction efficiency and compression efficiency but also wear and seizure of the sliding surface 631. There were other problems.

In addition, a configuration in which the lubricating oil in the oil reservoir 710 at the bottom of the closed container internal space 702, which is equal to the discharge pressure as shown in FIG. When the compressor is stopped, a large amount of refrigerant that returns to the compressor from the refrigeration cycle outside the compressor due to its own weight and differential pressure accumulates in a liquefied state on the underside of the motor 703 above the oil sump 710, causing refrigerant liquid and In some cases, lubricating oil flows into the compression chamber 723 through the oil suction pipe 722 and fills the compression chamber 723, and in such a state, the compression load is too large and restart operation is impossible. Even if it is possible, it will cause damage to the compressor.

Furthermore, depending on the compressor operating conditions, there may be a shortage of lubricating oil in the oil reservoir 710. In such conditions, compressed gas may flow into the compression chamber 723, resulting in a significant decrease in compression efficiency or an abnormal pressure increase in the compression chamber, causing the compressor to malfunction. There was a problem that it caused damage.

In addition, the oil sump 809 at the bottom of the compressor as shown in FIG.
Even with the configuration in which lubricating oil is supplied to the compression chamber 823 in the middle of compression via the back pressure chamber 808 in an intermediate pressure state leading to However, there was also the problem that compression efficiency was significantly lowered and durability was lowered.

On the other hand, as shown in FIGS. 22 and 23, when the compressor is operating, the oil supply passage 919 leading to the oil sump 916 at the bottom of the discharge chamber 910 is opened to supply differential pressure oil to the compression section, and when the compressor is stopped, the oil supply passage is closed. The invention of the structure is also known from Japanese Patent Publication No. 59-44517, and this invention is a slide vane rotary compressor that requires a discharge valve 908 downstream of the discharge port 907. 92
7 and the pressure in the discharge chamber 910 after passing through the discharge valve 908 is used to operate the plunger 922 to control the on-off valve 925 of the oil supply passage 919.

However, for a while (for example, immediately after starting operation when the compressor is cold),
Since the pressure in the discharge chamber 910 is low, the discharge valve 908 opens from the initial compression stroke in the cylinder 927 and the discharge chamber 910 and the cylinder 9 open.
The pressure difference with 27 is small.

For this reason, the on-off valve 925 does not open and there is no oil supply to the compression section, which causes problems such as a jumping phenomenon of the vanes 5, causing abnormal noise and a reduction in compression efficiency.The oil supply passage control device is not affected by the compressor operating conditions. It was hoped that it would be put into practical use.

Therefore, the present invention focuses on the fact that a scroll compressor does not require a discharge valve to increase the pressure in the compression chamber and has a constant compression ratio. The objective is to provide a scroll gas compressor with high efficiency and excellent durability by putting into practical use a fuel supply passage control device that utilizes pressure differences and has a wide range of applications.

Means for Solving the Problems In order to solve the above problems, the scroll and gas compressor of the present invention communicates an oil reservoir with a space whose pressure is lower than that of the oil reservoir through an oil supply passage. A refueling passage control valve device consisting of an on-off valve that opens and closes the refueling passage and an actuator that controls the on-off valve is installed in the middle, and the actuator has a valve body and a back pressure chamber A and a back pressure chamber arranged on both sides of the valve body. A back pressure chamber B is provided, and the back pressure chamber A communicates with a first compression chamber that does not communicate with either the discharge chamber or the suction chamber, and the back pressure chamber B communicates with the second compression chamber or suction chamber that communicates with the suction chamber or the suction chamber that communicates with this. The pressure difference between the back pressure chamber A and the back pressure chamber A causes the valve body to move forward and open the on-off valve, and when there is no pressure difference, the valve body closes due to its own weight or the biasing force of a spring device. This configuration includes an oil supply passage control valve device whose body moves backward to close the on-off valve.

According to the above structure, the compressor is started, the orbiting scroll performs an orbiting motion, and the gas in the suction chamber is sucked into the compression chamber (second compression chamber), compressed to a constant compression ratio, and then transferred to the discharge chamber. At the same time as the oil is discharged, the valve body of the actuator of the oil supply passage control valve device provided in the middle of the oil supply passage communicates with a back pressure chamber A that communicates with the first compressor, which does not communicate with either the discharge chamber or the suction chamber, and the suction chamber. The back pressure chamber leading to the second compression chamber moves forward due to the pressure difference between the die and the opening/closing valve to open the oil supply passage, and the lubricating oil in the oil reservoir is supplied to the space that requires lubrication under the differential pressure. Ru.

When the compressor stops, the pressure in the compression chamber and suction chamber L becomes the pressure on the suction side if there is a gap between the compression chamber and the pressure chamber, and a non-return valve is installed on the suction side. If there is no anti-viscosity valve, the pressure difference between the compression chamber and suction chamber will become the discharge chamber pressure, and if there is no anti-viscosity valve, the orbiting scroll will rotate in reverse and the pressure difference between the compression chamber and suction chamber will instantly disappear). The differential pressure between back pressure chamber A and back pressure chamber B, which communicate with the suction chamber, also disappears, and the valve body retreats due to its own weight or the biasing force of the spring device, closing the on-off valve. By blocking the oil supply passage and preventing unnecessary loss of lubricating oil in the oil reservoir, compression efficiency and durability can be improved by using useful lubricating oil.

EXAMPLES Below, a scroll gas compressor according to seven embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows the first embodiment of the present invention.
2 and 3 are longitudinal sectional views illustrating the operation of the oil supply passage control valve device in FIG. 1, and FIG. An explanatory diagram of the A-A change in Fig. 1 is shown, and Figs. 6 and 16 show the relationship between the pressure change in the compression chamber that is close to the discharge side and does not communicate with the discharge chamber, and the pressure change introduced into the oil supply passage control valve device. 7 to 14 and 17 are longitudinal sectional views of a hermetic scroll refrigerant compressor in another embodiment of the present invention, and partial sectional views illustrating the operation of the oil supply passage control valve device, etc. shows.

In FIG. 1, 1 and 2 are iron sealed cases, 3 is an iron frame, and the outer peripheral surface of the sealed case 1 and 2 are welded and sealed by a single weld bead 4.
2 is partitioned into an upper discharge chamber 5 and a lower drive chamber 6 (low pressure side).

An orbiting shaft 11 of an orbiting scroll 10 is fitted into an eccentric hole 9 at the upper end of a drive shaft 8 which is supported by a frame 3 and rotationally driven by a motor 7 whose operation is controlled by an inverter power supply (not shown). The rotation prevention part 12 engages with the orbiting scroll 10 and the frame 3, the fixed scroll 13 that meshes with the orbiting scroll 10 is bolted to the frame 3, and the end plate 1 of the fixed scroll 13
4 is provided with a discharge port 15, and a check valve 16 for closing the open end of the discharge port 15 and an oil supply passage control valve device 17 are attached to the upper surface of the end plate 14.

The bottom of the discharge chamber 5 is a discharge chamber oil reservoir 18, and the upper part thereof is an umbrella-shaped punching metal 19 with many small holes attached to the sealed case 1.
A filter 20 made of fine iron wire is packed between the discharge chamber 5 and the discharge pipe 2 provided on the upper surface of the sealed case 1.
1 through the external refrigeration cycle piping system, and through a suction pipe 22 provided on the side surface of the sealed case 2 to the drive chamber 6 on the low pressure side. The lower end of the drive shaft 8 has an eccentric oil filler 24 communicating between the hole 9 and the motor chamber oil reservoir 23.
It is buried in 3.

In FIGS. 2, 3, and 4, the oil supply passage control valve device 17 is attached to the end plate 14 with a gasket 25 interposed therebetween, and is provided in the main body case 26, with one end connected to a blind stopper 27.
A plunger 30 having an outer circumferential groove 29 is movably mounted inside the cylinder 28 which is closed by the cylinder 28 . The cylinder 28 is partitioned into two back pressure chambers by the plunger 30, and the back pressure chamber 831 on the side of the blind stopper 27 is connected to the gas hole 30.
The other back pressure chamber A34 does not communicate with the discharge port 15 through the ultra-thin pressure introduction hole 35 and is connected to the compression chamber A36 (first compression chamber) closest to the discharge port 15.
is connected to. A coil spring 38 made of a shape memory alloy material is disposed in the back pressure chamber 831 and is inserted and supported in a cylindrical hole 37 provided at one end of the plunger 30.
8 has one end pressed against the blind stopper 27 and the coil spring 38
A biasing force is applied to the suction chamber 33 and the compression chamber A3.
When there is almost no differential pressure between the back pressure chamber B31 and the back pressure chamber B31, the plunger 30 is moved a certain amount to expand the volume of the back pressure chamber B31, and the plunger 30 stops at the position shown in FIG. Plunger 3 is used to reduce the volume of back pressure chamber 831 to a certain amount when the differential pressure between A36 and A36 exceeds a set value.
0, the plunger 30 stops at the position shown in Figure 2, and its own temperature reaches the set temperature (for example, 130' (1)
When it exceeds the spring constant, the spring constant increases and the biasing force is strengthened.
1iI and the compression chamber A36 exceeds the set value, the plunger 3 is used to expand the volume of the back pressure chamber 831.
0 is set to move by a certain amount. Suction chamber 3
Compression chamber B59 (third compression chamber) located between 3 and compression chamber A36 and not communicating with suction chamber 33 (compression chamber Ba39m
) communicates with the bottom of the discharge chamber oil sump 18 via an extremely thin oil injection hole 40 (injection pipe 4OA), an outer circumferential groove 29, and an extremely fine oil suction hole 41, and the plunger 30
Communication or interruption occurs depending on the stop position.

In FIG. 5, the horizontal axis represents the rotation angle of the drive shaft load, and the vertical axis represents the refrigerant pressure, which represents the state of change in the pressure of the refrigerant gas during the suction, compression, and discharge processes.

In FIG. 6, the horizontal axis represents the rotation angle of the drive axle load, the vertical axis represents the refrigerant pressure, the solid line 42 represents the pressure in the compression chamber A36, the dashed line 43 represents the pressure in the back pressure chamber A34, and the vertical axis represents the refrigerant pressure. The dashed dotted line 42- represents the pressure in the compression chamber B39.

FIG. 7 is a longitudinal sectional view of a scroll refrigerant compressor according to another embodiment, in which the discharge chamber oil sump 18 is connected to the bearing oil sump of the frame 3a via the oil supply passage control valve device 17 attached to the end plate 14m of the fixed scroll 13m. 44. That is, the oil supply passage from the discharge chamber oil sump 18 to the bearing oil sump 44 is connected to the oil suction hole 41a1 provided in the end plate 14m of the fixed scroll 13m, and the plunger 30 of the oil supply passage control valve device 17.
The outer circumferential groove 29 of the frame 3 is provided with an oil-filled A45 provided in the end plate 14g and has a built-in check valve (not shown) in the middle.
They are successively communicated through an oil filler B46 provided in a.

FIG. 8 is a sectional view of a scroll refrigerant compressor according to another embodiment, in which 1b and 2b are iron closed cases, 45 is an iron support plate, and a single weld bead is formed on the outer peripheral surface of the scroll refrigerant compressor together with the closed cases 1b and 2b. The fixed scroll 13b is attached to the upper surface of the support plate 45 with the orbiting scroll 10b interposed therebetween, and the frame 3 supporting the drive shaft 8b is attached to the lower surface of the supporting plate 45.
b is attached, and the discharge chamber 5b and drive chamber 6b are composed of a discharge gas passage 46m opened on the upper surface of the end plate 14b of the fixed scroll 13b and a discharge gas passage 46 provided in the support plate 45.
An intermediate pressure back pressure chamber 47 formed by the orbiting scroll 10b, the support plate 45, and the frame 3b communicates with the drive shaft 8
It communicates with the motor chamber oil sump 23b via the shaft core oil hole 48 provided in b, the bearings 49 and 50 that engage with the drive shaft 8b, and the orbiting bearing 51, and communicates with the motor chamber oil reservoir 23b, and is provided on the orbiting scroll 10b. It also communicates with the suction chamber 3C1 via an extremely thin bypass hole 50. The annular oil groove 53 provided on the lower surface of the end plate 14b of the fixed scroll 13b against which the orbiting scroll 10b is pressed by the pressure of the intermediate pressure back pressure chamber 47 is connected to the discharge chamber via the oil supply passage control valve device 17 attached to the upper surface of the end plate 14b. It communicates with the oil sump 18b. That is, the oil supply passage from the discharge chamber oil reservoir 18b to the annular oil groove 53 is connected to the oil suction hole 41b1 provided in the end plate 14b of the fixed scroll 13b, the outer peripheral groove 29 of the plunger 30 of the oil supply passage control valve device 17, and the end plate 14b. They are successively communicated by a provided oil tank 54.

The suction pipe 22b passes through the sealed shell 1b and the end plate 14b to reach the suction chamber 331>, and the end of the suction pipe 22b and the suction chamber 3
A check valve 16b is provided between the discharge pipe 21b and the discharge pipe 21b.
is provided in the closed shell 2b and communicates with the drive chamber 6b.

FIG. 9 is a longitudinal cross-sectional view of a scroll refrigerant compressor according to another embodiment, in which the entire interior of the sealed shell 1G is a discharge chamber 5c, the motor 7 is fixed to the upper part, and the compression part and the oil supply passage control valve device 17c are fixed to the lower part. It is attached to the end plate 14a of the scroll 13c and is placed immersed in the oil reservoir 23c at the bottom, and the oil supply passage from the oil reservoir 23c to the suction chamber 33c is connected to the oil supply passage control valve device 17c.
An oil suction hole 41a provided in the main body case 26c,
An outer circumferential groove 29, an oil filler 55 provided on the end plate 14c, and a support plate 45c sandwiched between the frame 3G and the fixed scroll 13c.
an oil well 56 provided in the frame 3c, an oil well 57 provided in the frame 3c, a minute bearing gap between the bearing 58 that supports the drive shaft 8C, the frame 3C, the support plate 45c, and the orbiting scroll 10c.
The intermediate pressure back pressure chamber 47c formed by the 59, the compressed gas passage from the discharge port 15o to the discharge chamber 5c is composed of a bypass hole 52c, a discharge gas passage 60 formed by the fixed scroll 13c and the main body case 26c, the fixed scroll 13c, the support plate 45c, and the frame. It is composed of discharge gas passages 61, 62, and 63 provided in 3G, respectively.

Further, a spiral oil groove 65 is provided on the surface of the drive shaft 8c facing the bearing 64 provided on the frame 3G, and the winding direction of the oil groove 65 is controlled by the screw pump action as the drive shaft 8G rotates. The lubricating oil of 57 can also be supplied to the upper open end of the bearing 64.

Further, the suction pipe 22a is inserted into the fixed scroll 13c through a sealed shell IC and communicates with the suction chamber 33c via a check valve (not shown), and the discharge pipe 21c is inserted into the sealed case 1c.
It is installed on the upper side of the .

FIG. 10 is a partial sectional view of a scroll refrigerant compressor of another embodiment in which the on-off valve part of the oil supply passage control valve device is provided inside the end plate 14d of the fixed scroll 13d, and the cylinder 28d is provided in the end plate 14d, and the discharge Discharge chamber 5 without communicating with chamber 5
The compression chamber A 36 and the back pressure chamber A 34 d, which are closest to each other, communicate with each other through a pressure introduction hole 35 d through a small gap between the embedded screw 66 and the screw hole, and do not communicate with the suction chamber 33 .
Compression chamber B39 on the side closer to and outer circumferential groove 2 of plunger 30
9 is an injection hole 40 provided in the mirror plate 14d.
d. The coil spring 38, which communicates with an extremely thin injection passage 68 formed by the end plate 14d, the gasket 25d, and the gasket retainer 67, and applies a biasing force to the plunger 30, has a temperature that exceeds the set temperature (for example, 130°C). It is made of a shape memory alloy material with spring characteristics that actuates the plunger 30 to strengthen the biasing force and cut off the communication between the outer circumferential groove 29 and the injection passage 68, and extends from the discharge chamber oil sump 18 to the compression chamber 839. The oil supply passage includes an oil suction hole 41d, an outer circumferential groove 29, an injection passage 68, and an injection hole 40d.

FIG. 11 is a vertical sectional view of a scroll refrigerant compressor of another embodiment in which the passage opening/closing mechanism of the oil supply passage control valve device is different;
1 to 16, the spring devices that apply biasing force to the plunger 30 are a coil spring A38m and a coil spring 83.
The coil spring A38m, which is formed with a double structure of 8b and placed outside the coil spring B58b, has a longer free length than the coil spring B58b, and the spring constant of the coil spring B58b is set to be extremely larger than that of the coil spring A38m. As shown in FIG. 12, the oil supply passage from the discharge chamber oil sump 18 to the compression chamber A36 opens into the oil suction hole 41 provided in the end plate 14, the outer peripheral groove 29 of the plunger 30, and the cylinder 28e. Injection hole 4oe (or injection pipe 40a) provided in ・Injection hole 4 provided in end plate 14
0, the plunger 30 is formed by a coil spring B
58b is stopped in a slightly contracted state. In addition, if the pressure in the back pressure chamber A34 communicating with the compression chamber A36 through the pressure introduction hole 35 increases abnormally, the plunger 3
0 is coil spring A38a.

It moves against the coil spring B58b and stops in the state shown in FIG. 14, thereby blocking the oil supply passage between the discharge chamber oil reservoir 18 and the compression chamber 839.

In addition, Fig. 13 shows that when the differential pressure between the back pressure chamber 31 leading to the suction chamber 33 and the back pressure chamber A34 is almost eliminated, the plunger 30 is moved by the biasing force of the coil spring A38m and the refueling passage is blocked. Indicates the state in which the

In addition, when the temperature of the coil spring B58b exceeds the set temperature (for example, 130°C), the plunger 30
It is made of a shape memory alloy material that has the characteristic of shrinking to the extent that it does not apply any biasing force to the body.

In Fig. 15, the horizontal axis represents the rotation angle of the drive axle load,
The vertical axis represents the refrigerant pressure, the solid line 42 represents the pressure in the compression chamber A36 during normal operation, and the dotted line 71 represents the pressure in the compression chamber A3 during abnormal pressure rise.
The one-dot chain line 43 represents the pressure in the back pressure chamber 834 during normal operation, and the two-dot chain line 72 represents the pressure in the back pressure chamber A34 that changes following an abnormal increase in the pressure in the compression chamber A36.

FIG. 17 shows a partial sectional view of another embodiment of the oil supply passage control valve device attached to the fixed scroll, and shows the main body 26.
A thin plate diaphragm 80 sandwiched between 9 and case 26a
is attached to the body 26. by a single weld bead 81 at its outer periphery.
and the case 26f are hermetically welded together, and the internal space formed by the main body 269 and the case 26f is partitioned into a back pressure chamber B51f and a back pressure chamber 34f. The back pressure chamber A34f communicates with the compression chamber A36 via a pressure introduction pipe 35g and an extremely thin pressure introduction hole 35f provided in the end plate 14 of the fixed scroll 13, and the back pressure chamber B51f communicates with the gas hole 82 provided in the main body 26g.
It communicates with the suction chamber 33 via a gas hole 32f provided in the end plate 14. The main body 26g is provided with a cylinder 28f that is open to the back pressure chamber 831f, and a valve hole 83 that is continuous with the cylinder 28f and is larger than the diameter of the cylinder 28f and that is open on the surface where the end plate 41 of the main body 269 is attached.
The opening end of the valve hole 83 is provided in the end plate 14 and is connected to the discharge chamber oil sump 18.
It communicates with an oil suction hole 41 opened at the bottom. The injection hole 40f provided in the main body 26g has its upper end opened in the central inner wall of the cylinder 28f, and the other end communicates with the compression chamber B39 via the injection hole 40 provided in the end plate 14. The cylinder 31 is located in the valve hole 83.
A coil spring 38f larger than the diameter of f and a steel ball 84 are attached to the upper part of the coil spring 38f, and the cylinder 31f has a lower half in the shape of a small diameter pin, an upper half in the shape of a precision cylinder, and has an outer circumferential groove 29f in the center thereof. The plunger 30f is attached in an idle state. The outer circumferential groove 29f connects to the valve hole 83 through the small hole 85.
The movement of the upper end of the plunger 30f is regulated by a diaphragm 80, and the movement of the lower end is regulated by a steel ball 84 biased by a coil spring 38f.

The operation of the scroll refrigerant compressor configured as above will be explained.

1 to 6, when the drive shaft 8 is rotationally driven by the motor 7, the orbiting scroll 10 makes an orbiting motion,
Suction refrigerant gas flows into the drive chamber 6 through the suction pipe 22 from the refrigeration cycle connected to the compressor, and after a part of the lubricating oil contained therein is separated, it is sucked into the suction chamber 33, and the suction refrigerant gas swirls. Scroll 10 and fixed scroll 13
It is confined in a compression chamber formed between the orbiting scroll 10, is sequentially compressed as the orbiting scroll 10 rotates, and is discharged into the discharge chamber 5 through the central discharge port 15 and the check valve 16.
A part of the lubricating oil contained in the discharged refrigerant gas is separated from the discharged refrigerant gas due to its own weight and adheres to the surface of the punched metal 19 when passing through the small holes and the filter 20 made of pure iron wire, and is separated from the discharged refrigerant gas and becomes discharge chamber oil. The remaining lubricating oil is collected in the reservoir 18, and is carried out to the external refrigeration cycle through the discharge pipe 21 together with the discharged refrigerant gas, and is returned into the compressor through the suction pipe 22 together with the sucked refrigerant gas.

On the other hand, the lubricating oil collected in the motor chamber oil sump 23 at the bottom separated from the suction refrigerant gas in the drive chamber 6 is pumped by the centrifugal pump action by the eccentric oil tank 24 of the drive shaft 8, and the lubricating oil is pumped into the eccentric oil tank 24 and the bearings related to the drive shaft 8. The refrigerant flows into the suction chamber 33 together with the suction refrigerant gas by sequentially sliding on the sliding surface of the clearance (including the gap between the eccentric hole 9 and the rotation shaft 11), the thrust bearing part related to the orbiting scroll 10, and the rotation prevention component 12, The gap between adjacent compression spaces is sealed with an oil film to reduce leakage of compressed refrigerant gas.

In addition, the pressure in the compression chamber A36, which is not connected to the discharge chamber 5 and is closest to the discharge port 15, changes greatly during compressor operation as shown in FIG. The back pressure chamber A pressure 43 changes little and is larger than the maximum value of the compression chamber gap 42m. For this reason, back pressure chamber A
34 is stably higher than the pressure in the back pressure chamber 831 communicating with the suction chamber 33, and for this reason, the plunger 30 moves in the direction of the blind stopper 27 against the biasing force of the coil spring 38, as shown in FIG. As shown in the figure, the discharge chamber oil sump 18 and the compression chamber B5
9 (compression chamber on the side close to the suction chamber that does not communicate with the suction chamber 33) is communicated with an oil supply passage consisting of an oil suction hole 41, an outer circumferential groove 29, and an extremely thin injection hole 40,
The lubricating oil in the discharge chamber oil sump 18 passes through the oil supply passage, is gradually reduced in pressure, and is intermittently supplied to the compression chamber 839. This lubricating oil is supplied from the motor chamber oil sump 23, and is compressed together with the suction refrigerant gas through the suction chamber 33. It joins with the lubricating oil conveyed to chamber 839, and further seals the gap between adjacent compression chambers with an oil film.

In addition, after the compressor is stopped, the check valve 16 is closed, and the pressure in the discharge chamber 5 is maintained at the discharge pressure state for several minutes, but the gap between the compression chambers where there is no relative sliding movement is not sealed by the oil film.
The pressure in the discharge boat 15 and each compression chamber becomes the same as that in the suction chamber 33 by instantaneous reversal of the orbiting scroll. As a result, the plunger 30 is moved by the biasing force of the coil spring 38, and as shown in FIG. 3, the oil supply passage is blocked and oil supply from the discharge chamber oil reservoir 1B to the compression chamber B39 is stopped.

In addition, in the unlikely event that the lubricating oil is not returned to the compressor due to a phenomenon such as a clogging of the occlu piping system that freezes during compressor operation, there is a shortage of lubricating oil in the discharge chamber oil sump 18, and a large amount of refrigerant gas is discharged through the oil supply passage. If it flows into the compression chamber 839, the temperature in the compression chamber and the discharge chamber 5 will rise abnormally in a short period of time, causing the coil spring 38 to exceed the set temperature (for example, 130'C), causing the biasing force of the coil spring 38 made of a shape memory alloy material to increase. increases, the plunger 30 is stopped at the position shown in FIG. 3 (the same position as when the compressor is stopped), and the oil supply passage is blocked.

In FIG. 7, during operation of the compressor, the oil in the discharge chamber oil sump 18 is transferred to the oil suction hole 41a1, the outer circumferential groove 29, the oil water A45, the oil water B4 by the operation of the plunger 30 as described above.
6, the pressure is gradually reduced and oil is supplied to the bearing oil reservoir 44, and then the low pressure side is lubricated on the sliding surfaces of the bearings related to the drive shaft 8, the thrust bearings of the orbiting scroll 10, etc. The liquid flows into the drive chamber 6 and suction chamber 33 of.

The lubricating oil that has flowed into the suction waka glaze together with the suction refrigerant gas seals the gap between adjacent compression chambers with an oil film as described above to increase compression efficiency, and the lubricating oil that has flowed into the drive chamber 6 is transferred to the motor chamber oil sump 23 at the bottom. After being collected, the oil is supplied to each sliding surface as described above by the centrifugal pump action of the eccentric oil hole 24 provided in the drive shaft 8.

Note that the shutoff of the oil supply passage, the flow of refrigerant gas, the separation of lubricating oil in refrigerant gas, etc. after the compressor is stopped are the same as described above, and a description thereof will be omitted.

In FIG. 8, a drive shaft 8 is rotationally driven by a motor 7 to cause an orbiting scroll to orbit, and suction refrigerant gas from a refrigeration cycle connected to a compressor passes through a suction pipe 22b provided at its terminal end. It flows into the suction chamber 33b against the check valve 16b, is compressed to a certain compression ratio in the compression chamber, and is then discharged to the discharge chamber 5b, where part of the lubricating oil contained in the discharged refrigerant gas is It is separated from the discharged refrigerant gas due to its own weight and collected in the discharge chamber oil sump 18b.

Thereafter, the discharged refrigerant gas is discharged through the discharged refrigerant gas passages 46a, ta.
A part of the lubricating oil in the discharged refrigerant gas is also separated in the drive chamber 6b and is passed from the bottom to the shaft center oil hole 48 of the drive chamber 8b, the slewing bearing 51, and then to the bypass hole. 5
2 into the suction chamber 33b, the gap between adjacent compression chambers is sealed with an oil film, and the roll 10b is fixed to the fixed scroll 13b.
A thrust force is generated that presses against the surface of the mirror plate 14b.

Further, the plunger aO of the oil supply passage control valve device 17 opens the oil supply passage during compressor operation as described above, and the plunger aO of the oil supply passage control valve device 17 opens the oil supply passage during the compressor operation, and
The lubricating oil 8b is differentially supplied to the annular oil groove 53 of the end plate 14b through the oil suction hole 41b, the outer circumferential groove 29, and the oil/water 54,
After being used to lubricate the sliding surfaces of the end plate 14b and the orbiting scroll 10b, it flows into the suction chamber 33b and also contributes to sealing the gap between adjacent compression chambers. Further, after the compressor is stopped, the check valve 16b closes the suction pipe 22b, the compression chamber pressure becomes equal to the discharge chamber pressure, and the plunger 30 blocks the oil supply passage as described above.

In FIG. 9, the suction chamber 33c is passed through the suction pipe 22c.
After being compressed, the suction refrigerant gas flowing into the discharge port 1
5a1 is discharged into the discharge chamber 5c through the discharge gas passage 60.61.62.63, and a part of the lubricating oil contained in the discharged refrigerant gas is separated from the discharged refrigerant gas due to its own weight and is stored in the motor room oil sump at the bottom. 23c, and the remaining lubricating oil is carried out to the external refrigeration cycle through the discharge pipe 21a together with the discharged refrigerant gas.

As mentioned above, during compressor operation, the oil supply passage control valve device 17c
The plunger 30 operates to open the oil supply passage, and the lubricating oil in the motor chamber oil reservoir 23a flows through the oil suction hole 41c1 and the outer circumferential groove 2.
9. Oil/water 55, 56, 57, minute gap between drive shaft 8@ and bearing 58, intermediate pressure back pressure chamber 47c, minute gap between rotating shaft 11c and rotating bearing 51a, oil/water 59, bypass hole 52c The refrigerant gas is gradually depressurized and flows into the suction chamber 33a while lubricating the sliding surfaces, and is again compressed and discharged together with the suction refrigerant gas. A portion of the lubricating oil in the oil water 57 is also carried out to the discharge chamber 5c by the screw pump action of a spiral oil groove provided on the outer periphery of the drive shaft 8c, and lubricates the sliding surface of the bearing 64.

Further, as described above, after the compressor is stopped, the plunger 30 blocks the oil supply passage.

In FIG. 10, when the lubricating oil in the discharge chamber oil sump 18 runs out during compressor operation, high temperature and low viscosity compressed refrigerant gas is transferred to the oil supply passage (oil suction hole 41d1 outer circumferential groove 29,
Injection passage 68, injection hole 40d
) and flows into the compression chamber 839 in large quantities, causing the pressure and temperature of the compressed refrigerant gas to rise abnormally. As a result, the coil spring 38 made of a shape memory alloy material mounted inside the end plate 14d quickly reaches the set temperature (for example, 130°C) by direct heat transfer between the compression chamber A36, the compression chamber 839, the discharge chamber 5, etc.
The biasing force increases beyond this point, causing the plunger 30 to retreat and cutting off the oil supply passage.

Further, there is sufficient lubricating oil in the discharge chamber oil reservoir 18, and the opening and closing of the oil supply passage during normal compressor operation and after stopping is as described above.

11 to 16, suction refrigerant gas is passed through the suction pipe 22 from the refrigeration cycle connected to the compressor into the drive chamber 6.
The process of the lubricating oil flowing into the refrigeration cycle through the discharge chamber 5 and the discharge pipe 21 and the flow process of the lubricating oil in the motor chamber oil sump 23 are the same as those shown in FIG.
The operation of 7e is different from the above description. That is, during compressor operation when there is sufficient lubricating oil in the discharge chamber oil sump 18, the compression chamber A closest to the discharge port 15 does not communicate with the discharge chamber 5.
The pressure 42 at the opening of the pressure introduction hole 36 changes greatly as shown in FIG. Since it is larger than the maximum value of the pressure 42a in the compression chamber 3a, it is stably larger than the pressure in the back pressure chamber B31 communicating with the suction chamber 3a. Therefore, the plunger 30 moves forward against the biasing force of the coil spring A3Bm, and also applies a biasing force to the coil spring B58b. However, the coil bar*B5
8b is large, the plunger 30 stops at the position shown in FIG. 12, the oil supply passage is opened, and the oil sump 1 in the discharge chamber is opened.
The lubricating oil No. 8 is supplied to the oil suction hole 41, the outer circumferential groove 29, the injection hole 40e (or the injection pipe 40m
), the pressure is gradually reduced through the injection hole 40, and the refrigerant flows into the compression chamber B39, produces the effect of lubricating oil as described above, and is discharged into the discharge chamber 5 together with the compressed refrigerant gas. Also, in the unlikely event that
During compressor operation, lubricating oil is not returned to the compressor due to a clogging phenomenon in the refrigeration cycle piping system, and the lubricating oil in the oil sump 18 in the discharge chamber is insufficient, and the discharged refrigerant gas with high temperature and low viscosity flows through the oil supply passage into the compression chamber. If there is a large inflow on the 39th, the first
As shown in FIG. 5, the pressure in the compression chamber increases abnormally as indicated by the dotted line 70, and as shown in FIG. 16, the average pressure of the pressure cuff 2 in the compression chamber A at the opening of the pressure introduction hole also increases. As a result,
The plunger 30 moves forward against the biasing force of the coil spring B38b and stops at the position shown in FIG. 14, thereby blocking the oil supply passage. Further, after the compressor is stopped, the plunger 30 retreats to the position shown in FIG. 13 to block the oil supply passage as described above.

In FIG. 17, when the compressor is operated, the pressure in the back pressure chamber A34f communicating with the compression chamber A36 increases, and the diaphragm 80 is deformed due to the differential pressure between the back pressure chamber B51f communicating with the suction chamber 33 and the back pressure chamber A34f. The center part of the lever presses the tip of the plunger 30f, moves the steel ball 84 against the urging force of the coil spring 38f, and moves the steel ball 84 from the discharge chamber oil sump 18 to the compression chamber 8.
The oil supply passages up to 39 (oil suction hole 41, valve hole 83, cylinder 28f, small hole 85, outer peripheral groove 29, injection hole 40, 40f) are opened, and lubricating oil is supplied under differential pressure.

After the compressor is stopped, the coil spring 38
The diaphragm 80 is returned to a position of 80 m by the urging force of f, and the steel ball 84 closes the open end of the valve hole 83 of the cylinder 28f, blocking the oil supply passage.

As described above, according to the above embodiment, the bottom of the discharge chamber oil sump 18 and the compression chamber B59 (or the drive chamber 6 which communicates with the suction passage) which is not connected to the suction chamber 33 or the discharge chamber 5 but is close to the suction chamber 33,
Or the bearing 49.50 of the frame 3 that supports the drive shaft 8
An oil suction hole is formed between the gap between the bearing oil reservoir 44 provided between the bearing 49 and the bearing 50, or the annular oil groove 53 on the sliding surface between the end plate 14 of the fixed scroll 13 and the orbiting scroll 10. 41, outer circumferential groove 29, injection hole 4
A plunger 30 (or steel ball 84) that opens and closes the oil supply passage and an actuator that controls the plunger 30 (or steel ball 84) are connected in the middle of the oil supply passage. Oil supply passage control valve device 1
7, and the actuator is provided with a plunger 30 (or diaphragm 80) and a back pressure chamber A34 (or 34f) and a back pressure chamber B51 (or 31f) arranged on both sides of the plunger 30 (or diaphragm 80), The back pressure chamber A34 (or 34f) is a compression chamber A36 (referred to as the first compression chamber) that does not communicate with either the discharge chamber 5 or the suction chamber 33.
The back pressure chamber B51 (or 31?) communicates with the suction chamber 33, and the back pressure chamber A34 (or 34f) and the back pressure chamber 831 (
or 31f) due to the differential pressure between the plunger 30(
t or diaphragm 80) moves forward to open the oil suction hole 41.
and the outer circumferential groove 29 of the plunger 30 and the injection hole 40 (or between the valve hole 83, the cylinder 28f, and the injection hole 40f) are communicated, and the back pressure member 34 (
or 34f) and the back pressure chamber B51 (or 31f), the plunger 30 (or diaphragm 8
0) retreats to close the opening/closing passage
7, since the compression ratio of the refrigerant gas is constant, the pressure in the compression chamber A36 is not affected by the pressure in the discharge chamber 5 and is reliably increased to a pressure that is a constant multiple of the pressure in the suction chamber 33.
The plunger 30 (or diaphragm 80) moves forward due to the differential pressure and opens the oil supply passage immediately after starting the compressor.
The lubricating oil in the discharge chamber oil reservoir 18 is transferred from the initial compression stroke to the compression chamber B3.
9 to seal the gap between adjacent compression chambers with an oil film, it is possible to increase compression efficiency from the initial stage of compressor startup, prevent abnormal temperature rise of compressed refrigerant gas, and improve durability. In addition, by injecting oil into the compression chamber, the machining dimensional accuracy of the scroll portion can be optimized and the cost of the compressor can be reduced.

In addition, after the compressor is stopped, there is no differential pressure between the suction chamber 33 and the compression chamber A36 (the coil spring 38 (or coil spring 38f)
and the lubricating oil pressure in the oil suction hole 41), the plunger 30 (or steel ball 84) retreats and the oil supply passage is cut off, thereby preventing wasted lubricating oil from flowing from the discharge chamber oil sump 18 to the compression chamber 839. By preventing inflow and effectively using lubricating oil, which has a cooling effect and gap sealing effect, it is possible to improve the durability of sliding surfaces and compression efficiency, and prevent compressor damage due to oil compression when restarting the compressor. .

Further, according to the above embodiment, the plunger 30 constituting the actuator also serves as an on-off valve for the oil supply passage.
The opening/closing valve mechanism for the refueling passage is simple and space-saving, making it possible to provide a control device for the refueling passage that is inexpensive and has fewer restrictions on where it can be used.
Compressor size and cost can be reduced.

Further, according to the above embodiment, the back pressure chamber A34f and the back pressure chamber 83
By sealing and fixing the periphery of the thin foil diaphragm 80 sandwiched between the back pressure chamber A34f and the outer wall of the back pressure chamber B51f, the back pressure chamber A34f on the high pressure side is connected to the back pressure chamber B51f on the low pressure side. There is no leakage of refrigerant gas to compression chamber A.
36 and the suction chamber B33, the plunger 30f is advanced to open the valve hole 83, and the lubricating oil in the discharge chamber oil sump 18 can be injected into the compression chamber 839. In the compressor as well, the opening and closing of the oil supply passage can be controlled according to the operating state of the compressor, as described above.

Further, the diaphragm 80 has a back pressure chamber A34f and a back pressure chamber B.
If the differential pressure between 51f and 51f exceeds the set value, the back pressure chamber mill 31f
By providing a trouble deformation spring characteristic that warps toward the back pressure chamber A34f due to the biasing force of the coil spring 38f and the biasing force of the lubricating oil pressure in the oil suction hole 41 when there is no differential pressure, the suction Even when there is differential pressure pulsation between the chamber 33 and the compression chamber A36, the deformation of the diaphragm is stable, and no chattering phenomenon occurs in the steel ball 84 that opens and closes the oil supply passage, so the oil supply passage can be opened and closed stably. The durability of the sliding part and the compression efficiency can be stabilized.

Although the operation of the refrigerant compressor has been described in the above embodiment, similar effects can be expected in the case of compressors of other gases such as oxygen, nitrogen, and helium that use lubricating oil.

Further, in the above embodiment, the injection pipe 40m was used to communicate the outer circumferential groove 29 of the plunger 30 and the compression chamber A36, but the end plate 1 was used instead of the injection pipe 40m.
4 may be provided with the passage.

Further, in the above embodiment, the back pressure chamber 831 and the suction chamber 33 are communicated with each other, but the outer peripheral gap of the plunger 30 and the fill spring 3
By appropriately selecting the biasing force of 8, etc., the suction chamber 3
3 (referred to as the second compression chamber) and back pressure chamber mortar 31
The plunger 30 may be actuated by communicating with the cylinder to reduce the differential pressure. Further, in FIG. 8, the most upstream side of the oil supply passage is set as the discharge chamber oil reservoir 18b, but the intermediate pressure back pressure chamber 47 may be placed at the most upstream side of the oil supply passage.

Moreover, the upstream side of the oil supply passage may be appropriately selected without being limited to the above embodiment.

Further, in the above embodiment, no special sealing member is provided on the outer circumference of the plunger 30, but a piston ring made of Teflon or a rubber O-ring coated with Teflon to improve slippage may be used to seal the plunger 30. -30 Axial leakage from the external part may be reduced.

Effects of the Invention As described above, the present invention connects an oil reservoir and a space with a lower pressure than the oil reservoir through an oil supply passage, and includes an on-off valve and an on-off valve for opening and closing the oil supply passage in the middle of the oil supply passage. The actuator is provided with a valve body and a back pressure chamber A and a back pressure chamber B arranged on both sides of the valve body, and the back pressure chamber A is connected to a discharge chamber. The back pressure chamber B communicates with the second compression chamber or the suction chamber which communicates with the suction chamber or the suction side that communicates with this, and the back pressure chamber A and the back pressure chamber mill communicate with each other. A fuel supply passage control valve device in which the valve body advances due to the differential pressure between the two and opens the on-off valve, and when there is no pressure difference, the valve body moves back due to the weight of the valve body or the biasing force of a spring device to close the on-off valve. Since the compression ratio of the gas is constant, the pressure in the first compression chamber is not affected by the pressure in the discharge chamber and is reliably increased to a pressure that is a constant multiple of the pressure in the suction chamber. The differential pressure between the back pressure chamber A that communicates with the back pressure chamber A that communicates with the second compression chamber (or the suction chamber or the suction side that communicates with this) causes the valve body of the actuator to move forward and open the on-off valve, thereby causing the compression Immediately after the machine is started, the refueling passage opens and moves from the oil reservoir to a space with lower pressure (for example, an oil reservoir with a refueling device,
Lubricating oil is supplied under differential pressure to the bearing oil sump, bearing gap, compression space, etc.), and has a cooling effect, a sealing effect on minute gaps, a sliding resistance reduction effect due to oil film formation, a buffering effect, etc., and the compression space is maintained from the beginning of the compressor startup. In addition to increasing compression efficiency by reducing leakage of compressed gas, it also prevents abnormal temperature rises in the compressed gas and sliding surfaces, improving durability, and reducing compressor costs by optimizing the machining dimensional accuracy of the scroll part. You can also do that.

In addition, after the compressor is stopped, the pressure in the first compression chamber and the second compression chamber (or the suction chamber or the suction side leading to it) becomes the same, and the pressure difference between the back pressure chamber A and the back pressure chamber disappears, and the valve The valve body retreats due to the weight of the body or the biasing force of the spring device, closing the on-off valve and cutting off the oil supply passage. )
By preventing unnecessary lubricating oil from flowing into the compressor, it is possible to improve durability by eliminating insufficient oil supply and oil compression after restarting the compressor. Further, by effectively utilizing lubricating oil, the above-mentioned effects during compressor operation can be further enhanced.

[Brief explanation of the drawing]

FIG. 1 is a vertical cross-sectional view of a hermetic scroll refrigerant compressor according to a first embodiment of the present invention, and FIGS. 2 and 3 are longitudinal cross-sectional views of main parts illustrating the operation of the oil supply passage control valve device in FIG. 1. Figure 4 is an A-A explanatory diagram of Figure 1, Figures 6 and 16 are comparative illustrations of pressure changes at fixed points in the compression chamber, and Figure 7 is an explanatory diagram of pressure changes at fixed points in the compression chamber.
8, 9, and 11 are vertical sectional views of hermetic scroll refrigerant compressors according to different embodiments of the present invention, and FIG. 10 is longitudinal sectional views of hermetic scroll refrigerant compressors according to other embodiments of the present invention. A partial sectional view of the compressor, FIGS. 12, 13, 14, and 17 are partial sectional views explaining the operation of the oil supply passage control valve device in another embodiment of the present invention, and FIGS. 18 and 19. , 20th
Fig. 21 is a vertical sectional view and a partial sectional view of different conventional scroll type gas compressors, respectively, Fig. 22 is a longitudinal sectional view of a rotary type gas compressor equipped with a conventional oil supply passage control device, and Fig. 23 22 is a vertical cross-sectional view taken along line A-A in FIG. 22. 1.2... Sealed case, 5... Discharge chamber, 6... Drive chamber, 7... Motor, 10
...Orbiting scroll, 13...Fixed scroll, 15...Discharge boat, 17...
・・Oil supply passage control valve device, 18・・・・Discharge chamber oil sump, 2
3...Motor room oil sump, 3o...Plunger, 31...Back pressure chamber B, 33...
Suction chamber, 34... Back pressure chamber A136...
Compression chamber A138・mountain・fill spring, 39・river・compression chamber mortar, 40・・・・injection hole, 41・・
...Oil suction hole, 44 ...Bearing oil sump, 4
7...Intermediate pressure back pressure chamber, 8o...Diaphragm, 84...Steel ball. Name of agent: Patent attorney Toshio Nakao and 1 other person No. 1
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Claims (4)

[Claims] (1) An orbiting scroll is engaged with a fixed scroll so as to be able to swing and rotate freely, and a spiral-shaped compression space is formed between both scrolls. A scroll-type compression mechanism is formed that is divided into compression chambers and compresses fluid, and an oil reservoir portion is communicated with a space having a lower pressure than the oil reservoir portion through an oil supply passage, and the oil supply passage is provided in the middle of the oil supply passage. A refueling passage control valve device is provided that includes an on-off valve that opens and closes and an actuator that controls the on-off valve, and the actuator has a valve body and back pressure chambers A and B placed on both sides of the valve body. The back pressure chamber A communicates with a first compression chamber that does not communicate with either the discharge chamber or the suction chamber, and the back pressure chamber B communicates with a second compression chamber or suction chamber that communicates with the suction chamber or the suction side that communicates with this. The pressure difference between the back pressure chamber A and the back pressure chamber B causes the valve body to move forward and open the on-off valve. A scroll gas compressor comprising an oil supply passage control valve device in which the valve body is moved back by force to close the on-off valve. (2) The scroll gas compressor according to claim 1, wherein the valve body also serves as an on-off valve. (3) The scroll gas compressor according to claim 1, wherein the valve body is constituted by a diaphragm around which the valve body is sealed and fixed. (4) If the differential pressure exceeds the set value, the diaphragm will warp toward back pressure chamber B; if there is no differential pressure, the diaphragm will warp toward back pressure chamber A with the biasing force of the spring device or oil reservoir pressure. 4. A scroll gas compressor according to claim 3, having spring characteristics such as: