JPS63150489A - Scroll gas compressor - Google Patents

Abstract

PURPOSE:To improve the durability and compression efficiency of a sliding surface and suppress noise by opening and closing an oil feeding passage control valve according to the differential pressure between in a compression chamber and suction chamber and the urging force of a spring device which possesses the shape memory characteristic. CONSTITUTION:The inhaled coolant gas is compressed and discharged through the turning movement of a swire scroll 10, and the lubricating oil in a motor chamber oil reservoir 23 which is separated in a driving chamber 6 successively lubricates each sliding surface by the centrifugal action in an eccentric hole 24 on a driving shaft 8 and flows into a suction chamber 33, and the gap between the continuous compression chamber is sealed by an oil film. Since the pressure in a compression chamber A36 is higher than that of the suction chamber 33 during operation, the plunger 30 of an oil feeding passage control valve device 17 moves leftward against a spring 38, and intermittently supplies the lubricating oil in the discharge chamber oil reservoir 18 into a compression chamber B39. When the lubricating oil is not returned into a compressor because of the clogging of a piping system, the temperature in the compression chamber rises, and the plunger 30 is moved rightward by the spring 38 made of shape memory alloy, and an oil feeding passage 40 is closed. Therefore, the lubricating oil can be effectively utilized.

Description

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

Conventional technology The Suflow pFE compressor, which has low vibration and low noise characteristics, has a suction chamber on the outer periphery and a discharge boat in the center of the vortex. It is generally known that there is no need for a discharge valve for compressing fluid, such as a rotary compressor, the compression ratio is constant, the discharge pulsation is relatively small, and a large discharge space is not required.

However, especially when compressing gas, the dimensional accuracy of the spiral part must be extremely high in order to reduce the leakage gap in the compression part. There have been problems in that gas compressors are expensive and have large variations in performance.

Therefore, as a measure to solve this type of problem, it is highly 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 is made to flow 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, it is passed through the oil return passage. The cap 5 provided in the discharge space 582 is based on the concept of returning the lubricating oil to the space communicating with the lubricating oil reservoir and reducing the lubricating oil leakage to the outside of the compressor.
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 608, 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 differential pressure lubrication is applied to the sliding surface 631 between the fixed scroll 601 and the orbiting SFlow/L/606, lubricating oil is allowed to flow into the suction chamber 699 to reduce compressed gas leakage in the compression chamber due to the sealing effect of the oil film. (Japanese Unexamined Patent Publication No. 165787/1987).

In addition, a configuration in which lubricating oil is directly flowed into the compression chamber during compression as shown in FIG. 20, factor 2) can also be 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 sump 710 at the bottom of the discharge chamber is directly flowed into the compression chamber 723 in the middle of compression via the oil suction pipe 722. Publication No. 57-8386), No. 2)
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.
An oil film 89 inside 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 into the compression chamber 823 during compression through the oil supply pipe 815 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 a configuration in which the discharge space 582 and the low-pressure side space 580 are always in communication through the holes 584), even if lubricating oil is always present in the space 520 and the discharge space 582, the rotational speed of the compressor drive shaft With the change in the amount of oil supplied to the sliding parts, etc., the amount of lubricating oil contained in the compressed gas also changes, and the differential pressure between the discharge space 582 and the low-pressure side space 580 and the viscosity of the lubricating oil also change. Therefore, it is extremely difficult to set up an oil return passage that returns lubricating oil in just the right amount, and when the compressor is operating at high speed, the amount of lubricating oil discharged is large and it is difficult to prevent large amounts of lubricating oil from leaking outside the compressor. It is possible.

Furthermore, while the compressor is stopped, lubricating oil in the space 520 and discharge space 582 flows into the oil sump 508 at the bottom of the compressor due to differential pressure and dead weight, and remains in the space 520 and discharge space 582 for a while after the compressor is restarted. 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 is also a state where there is no lubricating oil 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 it, and in such a state, the compression load is too large and restart operation is impossible. Even if it can be started, 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.

Also, the oil sump 809 at the bottom of the compressor as shown in Figure 2) above.
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, the oil supply passage 919t leading to the oil sump 916 at the bottom of the discharge chamber 910 is opened when the compressor is in operation to supply differential pressure oil to the compression section, and the oil supply passage is closed when the compressor is stopped. The invention of the structure was published in Japanese Patent Publication No. 59-44517.
As is also known from Japanese Patent Publication No. 2003-120001, this invention discloses that the shilling 9 before passing through the discharge valve 908 of a slide vane type rotary compressor which requires a discharge valve 908 downstream of the discharge port 907.
27 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 immediately after compressor cold startup operation,
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 926 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. By putting into practical use an oil supply passage control device that utilizes pressure differences and has a wide range of applications, the present invention provides a highly efficient and durable Suflow V gas compressor.

Means for Solving the Problems In order to solve the above-mentioned problems, the scroll 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. is equipped with a refueling passage control valve device, and the refueling passage control valve device controls the pressure difference between the compression chamber and the suction chamber, which are not connected to the suction chamber and the discharge chamber, and the biasing force of a spring device having shape memory spring characteristics. is used to operate the actuator of the oil supply passage control valve device to open and close the passage, and when there is a differential pressure or does not exceed the set differential pressure, the passage is opened, and when there is no differential pressure or the set differential pressure is exceeded, the passage is opened. This configuration includes a refueling passage control valve device that closes the passage when the temperature exceeds the set temperature or when the spring device changes the biasing force beyond the set temperature.

According to the above configuration, the compressor is started, the orbiting scroll performs an orbiting motion, and the gas in the suction chamber is sucked into the compression chamber, compressed to a constant compression ratio, and discharged to the discharge chamber. The actuator of the oil supply passage control valve device provided in the middle of the passage is actuated by the differential pressure between the compression chamber and the suction chamber, which do not communicate with either the suction chamber or the discharge chamber, to open the passage and connect the oil supply passage, The lubricating oil in the oil reservoir is supplied to the space that requires oiling by differential pressure. When an abnormal pressure or temperature rise occurs in the compression chamber, the shear actuator operates due to the pressure difference or the change in the biasing force of the spring device, closing the oil supply passage. When the compressor stops, the pressure in the compression space and the pressure in the suction chamber become approximately equal to P through the gap between the compression chambers (immediately after the compressor stops, a non-return valve is installed between the compression space and the discharge chamber. If the pressure of the compression household appliance and the suction chamber is installed on the suction side, the pressure of the compression chamber and the upper suction chamber becomes the discharge chamber pressure, and if the anti-reverse valve is installed on the suction side, the pressure of the compression chamber and the upper suction chamber becomes the pressure of the discharge chamber. (If not, the orbiting scroll reverses and the pressure difference between the compression chamber and the suction chamber disappears instantly), and the actuator of the oil supply passage control valve device closes that passage, cutting off the oil supply passage and releasing the lubricating oil in the oil reservoir. The use of beneficial lubricants can improve compression efficiency and durability.

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 a vertical cross-sectional view of a closed scroll refrigerant pressure M machine in the first embodiment of the present invention, and FIGS.
Fig. 4 shows an explanatory view of the pressure change in Fig. 1, and Fig. 6 and Fig. 16 are close to the discharge side and show the discharge chamber. 7 to 14, and 1 to 14.
FIG. 7 shows a vertical cross-sectional view of a hermetic scroll refrigerant compressor in another embodiment of the present invention and a partial cross-sectional view for explaining the operation of the oil supply passage control valve device.

In Fig. 1, reference numeral 1.2 is an iron closed case, 3 is an iron frame, and the outer peripheral surface of the closed case 1.2 is welded and sealed with 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). A rotation prevention component 12 engages with the orbiting scroll 10 and the frame 3, a fixed scroll 13 that meshes with the orbiting scroll 10 is bolted to the frame 3, and a discharge port 15 is provided on the end plate 14 of the fixed flow/I/13. A check valve 16 for closing the open end of the discharge boat 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 1B, and the upper part thereof is an umbrella-shaped punching metal 19 with many small holes attached to the closed case 1, and a thin iron wire is connected between the closed case 1 and the punched metal 19. The discharge chamber 5 is filled with a low-pressure side air flow through a discharge pipe 2) provided on the top surface of the sealed case 1, an external refrigeration cycle piping system, and a suction pipe 22 provided on the side surface of the sealed case 2. A motor chamber oil sump 23 is provided at the bottom of the drive chamber 6 and communicates with the drive chamber 6, and the lower end of the drive shaft 8 has an eccentric oil film 24 communicating between the eccentric hole 9 and the motor chamber oil sump 23. It is buried in oil sump 23.

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 3° having an outer circumferential groove 29 is movably mounted in the cylinder 28 which is closed by the cylinder 28. The cylinder 2B is partitioned into two back pressure chambers by the plunger 30, and the back pressure chamber B31 on the side of the blind stopper 27 has a gas hole 32.
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 and inserted and supported in a cylindrical hole 37 provided at one end of the plunger 30 is disposed in the back pressure chamber B31.
8 has one end pressed against the blank plug 27 and the plunger 3
A biasing force is applied to the suction chamber 33 and the compression chamber A.
36, move the plunger 30 by a certain amount to expand the volume of the back pressure chamber B31,
The plunger 30 stops at the position shown in FIG.
When the differential pressure between the back pressure chamber B31 and the compression chamber A36 exceeds a set value, the plunger 30 is moved to narrow the volume of the back pressure chamber B31 to a certain amount, and the plunger 30 stops at the position shown in FIG. Its own temperature is the set temperature (e.g. 130°C)
When it exceeds the spring constant, the spring constant increases and the biasing force is strengthened.
The plunger 30 is set to move a certain amount even if the pressure difference between the back pressure chamber B31 and the compression chamber A36 exceeds a set value. A compression chamber B59 (third compression chamber) (compression chamber Ba39a) located between the suction chamber 33 and the compression chamber A36 and not communicating with the suction chamber 33 is connected to the extremely thin oil injector hole 40 (injection pipe 40a) and the outer periphery. It communicates with the bottom of the discharge chamber oil sump 18 via the groove 29 and the extremely thin oil suction hole 41, and is communicated or blocked depending on the stop position of the plunger 3o.

In FIG. 5, the horizontal axis represents the rotation angle to the drive shaft, 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 42a 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 a discharge chamber oil sump 18 is connected to a bearing oil sump in a frame 3a via an oil supply passage control valve device 17 attached to an end plate 14a of a fixed scroll 13a. 44. That is, the oil supply passage from the discharge chamber oil sump 18 to the bearing oil sump 44 includes an oil suction hole 41a provided in the end plate 14a of the fixed scroll 13a, and a plunger 30 of the oil supply passage control valve device 17.
outer circumferential groove 29, an oil film A45 provided on the end plate 14a and having a built-in check valve (not shown) in the middle, and a frame 3a.
The oil holes B46 are connected to each other in sequence.

FIG. 8 is a sectional view of a scroll refrigerant compressor according to another embodiment, in which 1b and 2b are iron closed cases, 46 is an iron support plate, and the outer peripheral surface of the closed case 1b.

2b is welded and sealed with a single weld bead, and a fixed scroll 13b is attached to the upper surface of the support plate 45 with the rotating suf roll 10b in between, and a drive shaft 8b is attached to the lower surface of the support plate 45.
The discharge chamber 5b and the drive chamber 6b communicate with each other through a discharge gas passage 46a opened on the upper surface of the end plate 14b of the fixed scroll 13b and a discharge gas passage 46b provided in the support plate 45. , an intermediate pressure back pressure chamber 47 formed by the orbiting scroll 10b, the support plate 46, and the frame 3b is connected to the drive shaft 8bK - the provided shaft center oil film 4B.
bearings 49 and 50, and a swing bearing 51 that engage with the drive shaft 8b.
It communicates with the motor chamber oil sump 23b via each minute gap, and also communicates with the suction chamber 33b via an extremely thin bypass hole 50 provided in the orbiting scroll 10b. End plate 14b of fixed flow/L'13b where rotating flow A/10b is pressed by the pressure of intermediate pressure back pressure chamber 47
An annular oil groove 53 provided on the lower surface of the oil passage 53 communicates with the discharge chamber oil reservoir 18b via an oil supply passage control valve device 17 attached to the upper surface of the end plate 14b. That is, the oil supply passage from the discharge chamber oil sump 18b to the annular oil groove 53 is connected to the fixed flow 7L/
Oil suction hole 41b provided in end plate 14b of 13b,
Outer circumferential groove 2 of plunger 30 of oil supply passage control valve device 17
9. The mirror plates 14bK are sequentially communicated through the thin holes 54 formed therein.

The suction pipe 22b passes through the sealed case 1b and the end plate 14b to reach the suction chamber 33b, and the end of the suction pipe 22b and the suction chamber 33
A check valve 16b is provided between the discharge pipe 2)b, and the discharge pipe 2)b is provided with a sealed case 2bK and communicates with the drive chamber 6b.

FIG. 9 is a longitudinal sectional view of a scroll refrigerant compressor according to another embodiment, in which the entire inside of a sealed shell 1C is a discharge chamber 5c, a motor 7 is fixed to the upper part, and a compression section and an oil supply passage control valve device 17c are fixed to the lower part. It is attached to the end plate 14c of the Suflow/1/13c and is placed immersed in the oil sump 23c at the bottom.
The oil supply passage from c to the suction chamber 33c includes an oil suction hole 41c provided in the main body case 26c of the oil supply passage control valve device 17c, an outer peripheral groove 29, and a thin hole 55 provided in the end plate 14c.
, a small hole 56 provided in the support plate 45c sandwiched between the frame 3c and the fixed scroll 13c, a small hole 57 provided in the frame 3cK, a minute bearing gap on the bearing 5 that supports the drive shaft 8c, and the frame 3c and the support. The intermediate pressure back pressure chamber 47c formed by the plate 45c and the orbiting flow/L'10c, the minute bearing gap between the orbiting bearing 51c provided at the lower end of the drive shaft 8c and the orbiting shaft 11c of the orbiting scroll 10c, the orbiting The scroll 10c is composed of a small hole 59 provided in K and a bypass hole 52C, and is connected to the discharge chamber 5 from the discharge boat 15c.
The compressed gas passage up to c is a discharge gas passage 60 formed by the fixed Suflow/L/13c and the main body case 26c, the fixed Suflow IV 13c, the support plate 45c, and the frame 3c.
It is composed of discharge gas passages 61, 62, and 63 provided in each.

Further, a spiral oil groove 65 is provided on the surface of the drive shaft 8c facing the bearing 64 provided on the frame 3C, and the winding direction of the oil groove 65 is determined by the screw pump action accompanying the rotation of the drive shaft 8c. ) The lubricating oil in the small hole 57 is provided in a direction that can also be supplied to the upper open end of the bearing 64.

Further, the suction pipe 22c penetrates the sealed case 1c, is inserted into the fixed scroll 13c, and communicates with the suction chamber 33c via a check valve (not shown), and the discharge pipe 22c is connected to the upper surface of the sealed case 1c. It is set in.

FIG. 10 is a partial cross-sectional view of another embodiment of a scroll refrigerant compressor in which the opening/closing valve part of the oil supply passage control valve device is provided inside the end plate 14d of the fixed flow II/13d.
d is provided on the mirror plate 14d, and the compression chamber A36 and back pressure chamber A34d, which do not communicate with the discharge chamber 5 and are closest to the discharge chamber 5, are pressure introduction holes through a small gap between the embedded screw 66 and the screw hole. The compression chamber B39 on the side closer to the suction chamber 33 and the outer circumferential groove 29 of the plunger 30 communicate with each other through the injection hole 40d provided in the end plate 14d, the end plate 14d, the gasket 25d, and the gasket holder. 67 and an extremely thin injection passage 6 formed by
The fill spring 38 that communicates with 8 and applies a biasing force to the plunger 30 has its own set temperature (for example, 130°C).
It is made of a shape memory alloy material with spring characteristics that actuates the plunger 30 in order to strengthen the biasing force and cut off the communication between the outer circumferential groove 29 and the injection passage 68 when the pressure exceeds 100. The oil supply passage up to B39 is composed of an oil suction hole 41d, an outer peripheral 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 device that applies a biasing force to the plunger 30 is formed of a double structure of a coil spring A 38 a and a coil spring B 58 b, and the coil spring A 38 a disposed outside the coil spring B 58 b has its free length. The coil spring B58 is longer than the coil spring B58b.
The spring constant of b is set extremely large for the coil spring A38a, and the spring constant from the discharge chamber oil sump 1B to the compression chamber A3 during normal operation is set to be extremely large.
As shown in FIG. 12, oil supply passages up to 6 are provided with an oil suction hole 41 provided in the end plate 14, an outer circumferential groove 29 of the plunger 30, and an injection hole 40e (or It is formed by the injection pipe 40a) and the injection hole 40 provided in the end plate 14, and the plunger 30 is stopped with the coil spring B58b slightly contracted.

Furthermore, 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 30 moves against the coil spring A38a and the coil spring B58b, resulting in the state shown in FIG. Stop and discharge chamber oil sump 1B
The oil supply passage between the compression chamber B39 and the compression chamber B39 is cut off.

Further, FIG. 13 shows that when the differential pressure between the back pressure chamber B31 and the back pressure chamber A34 communicating with the suction chamber 33 is almost eliminated, the brunge r-30 moves by the biasing force of the coil spring A38a and closes the oil supply passage. Indicates a state in which the signal is blocked.

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 shaft 4,
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.
6, the one-dot chain line 43 represents the pressure in the back pressure chamber B34 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 A38.

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.
g and case 26! A thin plate diaphragm 80 sandwiched between
The main body weighs 26g due to a single weld bead 81 at its outer periphery.
and the case 26f, and the internal space formed by the main body 26g and the case 26 is divided into a back pressure chamber B31f and a back pressure chamber A34.The back pressure chamber A34f is fixed to the pressure introduction pipe 35g. The compression chamber A3 is
6, and the back pressure chamber B31f communicates with the suction chamber 33 via a gas hole 82 provided in the main body 26g and a gas hole 32f provided in the end plate 14.

The main body 26g has a cylinder 2 opened to the back pressure chamber B31f.
8f, and cylinder 2 provided continuously to cylinder 28f.
The end plate 41 of the main body 26g is attached with a valve hole 83 that is larger in diameter than the diameter of the end plate 8f and is opened on the surface, and the open end of the valve hole 83 is provided in the end plate 14 and has an oil suction opening at the bottom of the oil sump 18 in the discharge chamber. It leads to hole 41. The injection hole 40 provided in the main body 26g has its upper end connected to the cylinder 28.
f, and the other end communicates with the compression chamber B39 via an injection hole 40 provided in the chain plate 14. A coil spring 38f larger than the diameter of the cylinder 31 and a steel ball 84 are attached to the valve hole 83, and a steel ball 84 is attached to the upper part of the coil spring 38f. A plunger 30f having an outer circumferential groove 29f is attached in a loose manner. The outer circumferential groove 29f communicates with the valve hole 83 through a small hole 85, and 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.

In Figures 1 to 6, when the drive shaft 8 is rotationally driven by the motor 7, the rotating flow/1/10 moves in a circular motion, and the suction refrigerant gas flows into the suction pipes 2 and 2 from the refrigeration cycle connected to the compressor. A part of the lubricating oil contained therein is separated and sucked into the suction chamber 33, and this suction refrigerant gas is formed between the orbiting scroll 10 and the fixed flow A/13. It is confined in the compression chamber and is sequentially compressed with the orbiting movement of the orbiting scroll 10, and is transferred to the discharge chamber 5 through the discharge boat 16 in the center and the check valve 16t.
A part of the lubricating oil contained in the discharged refrigerant gas adheres to its own weight and the surface of the filter 20 made of small holes and fine iron wire of the punching metal/I/19, resulting in the lubricating oil contained in the discharged refrigerant gas. The remaining lubricating oil is collected in the discharge chamber oil sump 18, and the remaining lubricating oil is collected in the discharge pipe 2 together with the discharge refrigerant gas.
), it is carried out to an external refrigeration cycle, and returns to the compressor through the suction pipe 22 together with the suction 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 thin hole 24 of the drive shaft 8, and the lubricating oil is pumped through the eccentric thin hole 24 and the bearing related to the drive shaft 8. The gap (including the gap between the eccentric hole 9 and the rotating shaft 11), the thrust bearing part related to the rotating scroll 10, and the sliding surface of the rotation prevention component 12 are sequentially lubricated, and the suction refrigerant gas flows into the suction chamber 33 with the suction refrigerant gas, and the adjacent The gap between the compression chambers 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 6 and is closest to the discharge boat 15, changes greatly during compressor operation as shown in FIG. The back pressure chamber A pressure 43 changes less and is larger than the maximum value of the compression chamber B pressure 42a. For this reason, back pressure chamber A
, 34 is stable and larger than the pressure in the back pressure chamber B31 which communicates with the suction chamber 33. Therefore, the plunger 3o moves in the direction of the blind stopper 27 against the biasing force of the coil spring 38, and As shown in Figure 2, the discharge chamber oil sump 18 and the compression chamber B
59 (compression chamber on the side that does not communicate with the suction chamber 33 and is close to the suction chamber)
The lubricating oil in the discharge chamber oil sump 1B passes through the oil supply passage and is appropriately gradually depressurized to the compression chamber B39. This lubricating oil is supplied from the motor chamber oil sump 23 and is combined with the lubricating oil that has been conveyed to the compression chamber B39 through the suction chamber 33 together with the suction refrigerant gas, and fills the gap between adjacent compression chambers. A further seal is achieved 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 port 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 3B, and as shown in FIG. 3, the oil supply passage is blocked and oil supply from the discharge chamber oil sump 18 to the compression chamber B39 is stopped.

In addition, in the unlikely event that lubricant oil is not returned to the compressor due to a clogging phenomenon in the refrigeration cycle piping system during compressor operation, lubricant oil in the discharge chamber oil sump 18 becomes insufficient, and discharged refrigerant gas flows through the oil supply passage. If a large amount flows into the compression chamber B39, the temperature inside the compression chamber and the discharge chamber 6 will rise abnormally in a short period of time, causing the coil spring 38
exceeds the set temperature (for example, 130°C), the biasing force of the coil spring 3B made of shape memory alloy material increases, and the plunger 30 is placed in the position shown in Fig. 3 (the same position as when the compressor is stopped).
It comes to a standstill and the refueling passage is cut off.

In FIG. 7, lubricating oil in the discharge chamber oil sump 1B during compressor operation is transferred to the oil suction hole 41a1, the outer circumferential groove 29, the narrow hole A45, and the narrow hole B4 by the operation of the plunger 3o as described above.
6, the pressure is gradually reduced and oil is supplied to the bearing 111tl reservoir 44. After that, the low pressure side is lubricated on the sliding surfaces of the bearings related to the drive shaft 8 and the thrust bearings of the swing flow 1v10. drive chamber 6 and suction chamber 33
flows into.

The lubricating oil that has flowed into the suction chamber together with the suction refrigerant gas seals the gap between adjacent compression chambers with an oil film to increase compression efficiency, as described above, and the lubricating oil that has flowed into the drive chamber 6 flows into the motor chamber oil sump 23 at the bottom. After being collected, it is supplied to each sliding surface as described above by the centrifugal pump action of the eccentric thin 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 reverse 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 flows through the discharged refrigerant gas passage 46a.

A part of the lubricating oil in the discharged refrigerant gas is separated in the drive chamber 6b and collected in the motor chamber oil sump 23b at the bottom. The lubricating oil in the motor chamber oil sump 23b gradually passes through the shaft center small hole 4B of the drive chamber 8b, the minute gap of the swing bearing 51, and the minute gap of the bearings 49, 50 of the frame 3b due to the differential pressure with the intermediate pressure back pressure chamber 47. After the oil is depressurized and supplied to the intermediate pressure back pressure chamber 47, it flows into the suction chamber 33b through the bypass hole 52, and the gap between adjacent compression chambers is sealed with an oil film to improve compression efficiency.

Further, the lubricating oil pressure in the intermediate pressure back pressure chamber 47 generates a thrust force that presses the surface of the end plate 14b of the orbiting scroll 10bt and the fixed scroll 13b.

Further, as described above, the plunger 30 of the oil supply passage control valve device 17 opens the oil supply passage during compressor operation, and
The lubricating oil 8b is supplied to the annular oil groove 53 of the end plate 14b by differential pressure through the oil suction hole 41b, the outer circumferential groove 29, and the thin hole 54,
After being used to lubricate the sliding surfaces of the mirror plate 14b and the rotating scroll L'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 18b 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
The lubricating oil contained in the discharged refrigerant gas is discharged into the discharge chamber 5c through the 5C1 discharge gas passages 60, 61. 23c, and the remaining lubricating oil is discharged to the external refrigeration cycle through the discharge pipe 2)c 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 23c flows through the oil suction hole 41c1 and the outer circumferential groove 2.
9. Small holes 55, 56, 57, small gap between drive shaft 8C and bearing 5B, intermediate pressure back pressure chamber 47C1, small gap between rotating shaft 11c and rotating bearing 51c, small hole 59, bypass hole 52c The refrigerant gas is gradually depressurized and flows into the suction chamber 33C 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 thin hole 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 1B becomes insufficient during compressor operation, compressed refrigerant gas with high temperature and low viscosity is transferred to the oil supply passage (oil suction hole 41d, outer circumferential groove 29,
Injection passage 6B, injection hole 40d
), a large amount of refrigerant gas flows into the compression chamber B39, causing an abnormal increase in the pressure and temperature of the compressed refrigerant gas. As a result, the coil spring 3B 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 through the compression chamber A36, the compression chamber B39, the discharge chamber 5, etc.
The biasing force increases beyond t-, 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 1B, and the opening and closing of the oil supply passage during normal compressor operation and after stopping is as described above.

In Figs. 11 to 16, suction refrigerant gas from the refrigeration cycle connected to the compressor flows into the drive chamber 6 through the suction pipe 22t, passes through the discharge chamber 5 and the discharge pipe 2), and is then carried out to the refrigeration cycle again. The process and the flow process of the lubricating oil in the motor chamber oil sump 23 are the same as those shown in FIG. 1, but the operation of the oil supply passage control valve device 17e is different from the above-mentioned contents. That is, during compressor operation when there is sufficient lubricating oil in the discharge chamber oil sump 1B, the pressure introduction hole opening pressure 42 of the compression chamber A36, which is not in communication with the discharge chamber 5 and is closest to the discharge boat 15, is at the 16th level. As shown in the figure, the pressure 43 in the back pressure chamber A introduced through the ultra-thin pressure introduction hole 35 changes greatly, but the change is smaller than the maximum value of the pressure 42a in the compression chamber B at the injection hole opening. Since it is large, the pressure in the back pressure chamber B31 communicating with the suction chamber 33 is also stable and large. For this reason, the plunger 30
moves forward against the biasing force of coil spring A38a, and also applies biasing force to coil spring B58b. However, coil spring B
Since the urging force of 58b is large, the plunger 30 is the 12th one.
It stops at the position shown in the figure and the oil supply passage is opened, and the lubricating oil in the discharge chamber oil sump 1B is supplied to the oil suction hole 41, outer circumferential groove 29, injection hole 40e (or injection pipe 40a).
), 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 a large amount flows into B39, 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 B58b and stops at the position shown in FIG. 14, thereby blocking the oil supply passage. In addition, after the compressor is stopped, the plunger 30
is retreated to the position shown in FIG. 13 to block the oil supply passage.

In FIG. 17, the compressor is operated and the back pressure chamber A34 is connected to the compression chamber A36! The pressure increases, and the diaphragm 80 is deformed due to the pressure difference between the back pressure chamber B31f communicating with the suction chamber 33 and the back pressure chamber 341, and its center presses the tip of the plunger 30f, causing the coil spring 38 to be biased. , the steel ball 84 is moved against the force, and the oil supply passage (oil suction hole 41, valve hole 83,
28 shillings! , the small hole 86, the outer circumferential groove 29, and the injection hole 40.4Of) 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 the position 80a by the urging force of the plunger 30, and the steel ball 8.4 closes the open end of the valve hole 83 of the cylinder 281 and blocks the oil supply passage.

As described above, according to the above embodiment, the bottom of the discharge chamber oil sump 1B and the compression chamber B59 (between the suction pressure and the discharge pressure intermediate pressure) through an oil supply passage formed by an oil suction hole 41, an outer circumferential groove 29, and an injection hole 40,
A refueling passage control valve device 17 is provided in the middle of the refueling passage, and an actuator (plunger 3
0 or diaphragm 80) is connected to both the discharge chamber 6 and the suction chamber 33.
The compression chamber A36 (first compression chamber) closest to the discharge chamber 5 and the compression chamber (first compression chamber) in the pre-compression stroke than the compression chamber A36 are
(including the compression chamber leading to the suction chamber 33, referred to as the second compression chamber), or the pressure difference between the compression chamber A36 and the suction chamber 33 or the suction side leading thereto, or by its own temperature. The oil supply passage is opened and closed by the coil spring 38 having shape memory characteristics with different biasing forces and the above-mentioned differential pressure, and the oil supply passage is opened when there is a differential pressure and does not exceed the set differential pressure, and when there is no differential pressure or the set differential pressure is By providing the oil supply passage control valve device 17 that closes the oil supply passage when the temperature exceeds the set temperature or when the coil spring 3B rapidly increases the biasing force by exceeding the set temperature, the compression ratio of the refrigerant gas is constant, so that the compression chamber A36 is The pressure rises reliably to a constant multiple of the pressure in the suction chamber 33 without being affected by the pressure in the discharge chamber 5, and the actuator (plunger 30 or diaphragm 80) moves forward due to the differential pressure, starting immediately after starting the compressor. Open the oil supply passage and inject the day's lubricating oil from the discharge chamber oil reservoir into the compression chamber B39 from the initial compression stroke, sealing the gap between adjacent compression chambers with an oil film to increase compression efficiency from the beginning of compressor startup. At the same time, it is possible to 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. Furthermore, even if the lubricating oil in the discharge chamber oil sump 1B is insufficient and discharged refrigerant gas with low viscosity and extremely low passage resistance flows into the compression chamber 839, the pressure and temperature of the compression chamber may rise abnormally, resulting in differential pressure and actuation.

- When the temperature of the tank exceeds a set value and the plunger 30 is further advanced, the plunger 30 is moved backward to close the oil supply passage and prevent a decrease in compression efficiency.

In addition, after the compressor is stopped, the differential pressure between the suction chamber 33 and the compression chamber A36 disappears, and the oil supply passage is cut off.
Preventing unnecessary lubricating oil from flowing into the compression chamber B39 from B,
It is also possible to improve the durability of sliding surfaces and compression efficiency by effectively using lubricating oil, and to prevent damage to the compressor due to oil compression when restarting the compressor.

Further, according to the above embodiment, there is a connection between the drive chamber 6, which is connected to the suction passage and in which the oil supply device (lubrication by the centrifugal pump action of the eccentric sleeve hole 24 provided in the drive shaft 8) is arranged, and the discharge chamber oil sump 1B. By communicating with the oil supply passage and providing the above-mentioned oil supply passage control valve device 17 in the middle of the passage, the oil supply passage is opened and the discharge chamber is opened only when the compressor is operating and there is lubricating oil in the discharge chamber oil sump 18. The lubricating oil in the oil sump 18 can be returned in appropriate amounts to the drive chamber 6 to supply oil to the sliding parts, and it can also be remixed with the suction refrigerant gas and flow into the compression chamber again to seal the gap between the compression chambers. It is also possible to increase the durability and compression efficiency of the sliding part. In addition, the lubricating oil collected in the discharge chamber oil sump 1B is always kept in a small amount to improve the efficiency of separating the lubricating oil from the discharged refrigerant gas in the discharge chamber 5, and the separated lubricating oil is mixed into the discharged refrigerant gas again. By preventing lubricating oil from flowing into the refrigeration cycle outside the compressor, various adverse phenomena related to lack of lubricating oil in the compressor can be prevented.

In addition, according to the above embodiment, the space between the compression chamber (referred to as the third compression chamber) in the pre-compression stroke and the discharge chamber oil sump 18 and the drive chamber 6, which is not in communication with the suction chamber 33 and is in the pre-compression stroke than the compression chamber A36, is By communicating with the discharge chamber oil sump 18 through an oil supply passage, and by providing the above-mentioned oil supply passage control valve device 17 in the middle of the passage, it can be used only when the compressor is operating and there is lubricating oil in the discharge chamber oil sump 18. The oil supply passage is opened and the lubricating oil in the discharge chamber oil sump 18 is returned to the drive chamber 6 and the compression chamber B39 in appropriate amounts to lubricate the sliding parts and seal the gap between the compression chambers, thereby increasing the durability of the sliding parts. In addition to increasing the compression efficiency, the lubricating oil is allowed to flow into the compression chamber B39 after suction is completed, so that the suction efficiency is not reduced. Also,
This is a configuration in which the oil supply passage control valve device 17 is shared, and the cost of the oil supply passage relative to the functional effect is relatively low.

In addition, according to the above embodiment, the gap between the bearings 49 and 50 of the frame 3 that supports the drive shaft 8, the bearing oil reservoir 44 provided between the bearings 49 and 50, and the end plate 14 of the fixed scroll 13 rotate. Annular oil groove 5 on sliding surface with scroll 10
3 and the discharge chamber oil reservoir 1B are communicated by an oil supply passage,
By providing the above-mentioned oil supply passage control valve device 17 in the middle of the passage, the oil supply passage is opened and oil is supplied only when the compressor is in operation which requires oil supply and lubricating oil is present in the discharge chamber oil sump 18. This prevents excessive lubricant supply and eliminates lubricant shortages, contributing to improved durability and stabilization of compression efficiency.

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 40a was used to communicate the outer peripheral groove 29 of the plunger 30 and the compression chamber A36, but instead of the injection pipe 40a, an end plate 1 was used.
4 may be provided with the passage.

Further, in the above embodiment, the back pressure chamber B31 and the suction chamber 33 are communicated with each other, but by appropriately selecting the dimensions of the plunger 30, the fill spring 38, etc., the compression chamber communicating with the suction chamber 33 or the suction chamber 33 can be communicated with each other. The compression chamber B39 on the side closer to the suction chamber 33 and the back pressure chamber B31 may be communicated with each other. Also,
In FIG. 7, a bypass hole communicating with the drive chamber 6 may be provided from the middle of the use hole B46.

In addition, in FIG. 8, the most upstream side of the oil supply passage is the discharge chamber oil sump 18b.
However, the intermediate pressure back pressure chamber 47 may be located at the most upstream side of the oil supply passage.

Furthermore, the present invention is not limited to the above embodiment, and the upstream and downstream portions of the oil supply passage may be appropriately selected.

In addition, in the above embodiment, the oil supply passage control valve device is attached to the end plate of the fixed scroll so that the plunger moves in the horizontal direction, and when the differential pressure between the back pressure chamber A and the back pressure chamber B disappears, the spring The configuration is such that the plunger is retracted by the biasing force of the device, but the back pressure chamber A is placed on the lower side and the back pressure chamber B is placed on the upper side, so that when the differential pressure between the chambers disappears, the plunger will move under its own weight. A vertical oil supply passage control valve device that retreats to shut off the on-off valve may be attached to the top or side surface of the end plate.

Further, in the above embodiment, no special seal member is provided on the outer circumference of the plunger 30, but for example, a Teflon piston ring or a Teflon-coated rubber O-ring (0-ring) is used to seal the plunger. -30 Axial leakage from the outer circumference may be reduced.

In addition, although the above explanation deals with the case where lubricating oil is supplied by differential pressure, even when injecting refrigerant liquid or refrigerant gas on the high-pressure side into a chamber, the passage can be opened and closed using a similar concept, and various methods can be used. It is also possible to expand the idea of passage control to various fields.

Effects of the Invention As described above, 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, and includes an oil supply passage control valve device in the middle of the oil supply passage for opening and closing the passage. The actuator of the oil supply passage control valve device is provided with a differential pressure between a first compression chamber that does not communicate with either the discharge chamber or the suction chamber and a second compression chamber that is in a pre-compression stroke than the first compression chamber, or the first compression chamber. The refueling passage is opened and closed by the pressure difference between the chamber and the suction chamber or the suction side leading thereto, or by the spring device having a shape memory characteristic whose urging force differs depending on its own temperature and the above-mentioned pressure difference. Opens the oil supply passage when the set differential pressure is not exceeded, and closes the oil supply passage when there is no differential pressure or exceeds the set differential pressure, or when the spring device exceeds the set temperature and changes the biasing force. By providing the oil supply passage control valve device, the compression ratio of the compressed gas in the scroll compression mechanism is constant during compressor operation, so the first passage does not communicate with the discharge chamber.
Since the pressure in the compression chamber is not affected by the pressure in the discharge chamber and reliably rises to a constant multiple of the pressure in the suction chamber (or suction side), the pressure in the first compression chamber and the suction chamber, or the suction side leading to this, increases from the beginning of compressor startup. A pressure difference between the two compression chambers or a pressure difference between the first compression chamber and the second compression chamber is reliably generated, and the differential pressure operates the 7 actuator of the oil supply passage control valve device to open the oil supply passage. lubricating oil can be supplied to various parts of the compressor, such as sliding parts, oil sump, and compression space, at a differential pressure from the beginning of compressor startup, and the oil film and cooling effect of the lubricating oil can be effectively utilized to reduce the pressure of the compressor sliding parts. It can contribute to improving durability, compression efficiency, and reducing noise.

In addition, if an abnormality occurs such as the lubricating oil in the oil supply passage running out and the temperature inside the compressor or the pressure inside the compression chamber rises abnormally, and the temperature of the spring device or the differential pressure acting on the actuator exceeds the set value, the spring biasing force will increase. The actuator is actuated by the change in the pressure and the differential pressure, and the oil supply passage is closed, thereby preventing abnormal development caused by the communication of the oil supply passage and preventing deterioration of durability.

In addition, when the compressor stops operating and the differential pressure between the compression chamber and the suction chamber or the suction side leading to it disappears, the actuator operates and closes the oil supply passage, causing wasteful lubricant oil to flow out from the oil reservoir. The lubricating oil can be adjusted according to the operating condition of the compressor by preventing such problems, and the effective use of lubricating oil, which has a cooling effect and gap sealing effect, improves the durability of sliding surfaces, improves compression efficiency, and reduces noise. It is possible to provide a scroll gas compressor that can improve various characteristics depending on the temperature and exhibits many excellent effects.

[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 a cross-sectional view of the compression section taken along line A-A in Figure 1, Figures 5 and 15 are explanatory diagrams, and Figures 6 and 16 are comparisons of pressure changes at fixed points in the compression chamber. Introductory drawings, Figures 7 and 8. 9 and 11 are longitudinal sectional views of a hermetic scroll refrigerant compressor according to another embodiment of the present invention, and FIG. 10 is a partial sectional view of a scroll refrigerant compressor according to another embodiment of the present invention. , FIG. 12, FIG. 13, FIG. 14, and FIG. 17 are partial sectional views explaining the operation of the oil supply passage control valve device in another embodiment of the present invention, FIG. 18, FIG. 19, FIG. 20, 2nd)
The figures are a longitudinal cross-sectional view and a partial cross-sectional view of different conventional scroll-type gas compressors, respectively, FIG.
FIG. 3 is a longitudinal 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, 1B...Discharge chamber oil sump, 23...Motor room oil sump, 30...Plunger, 31...Back Pressure chamber B, 33...
...Suction chamber, 34...Back pressure chamber A136...
...Compression chamber A, 3B... Coil spring, 39...
...Compression chamber B, 4o...Injection hole, 41...Oil suction hole, 44...
Bearing oil reservoir, 47...Intermediate pressure back pressure chamber, 80...
... Guyafram, 84... Steel ball. Name of agent: Patent attorney Toshio Nakao and one other person
Jc1 figure f ■ 12-person 3h booth 3-7 frame 4-: M? c-Draw Chuchiiku 19-Pashichin 7x Taxi 22-W Emmigration tube 23-F: 1 tie y oil distillation Z4-Shoulder mI 33-Usumaru, 1 Fig. 2 fo-Kozuchi - Le f3 - Sonokashi Nugrol / 4-5 anti-necessity rsu 1 to 29-ri) Tsuki ■ Town 3θ - Niransha J / - Beak 5rL! VB, 32-Power Base 33-■ Shibe! , 34-% Tanuki-1 (△ 85-λ巳 ll base 2S elephant 36-) D helmet 1 Takumi A 31-Fl 箭Σ ( 38-coil to 3q-7 Ren WB ♂ Taichiman'' Kozei 4 Kuin Usagi Fushigon Daikoro - Ishishi no Fun mlj including 4f - Enclosure I O U entry 5th figure KWD vJ axis] Matsukyu paper (rad) layer * @ TMdn (rad> di] ab 9 key! Figure 10 12-11 shadow〉su Figure 12 Figure 13 Game 18-Note 7!Rainbow 29-ri) A0 Qing δθ-7 Run layer 31-One beak and!8 X-Inhalation of ten thousand su! y- Blue and violet A 35-Okinori gourd entering pa, 3ro-λL arrival "Tsutomon 38 magazine-Koilba TA 40-Inshi Kasa Gushonku #-4] Ji 17 Ji 9: / 1 warehouse ae-In Miku 14 〈 6q - Sword shift of the 5th seismic wave, 70 - Ikko normal pressure case, π power drive, S turning angle, Figure 17, Figure 18 Prisoner & υ Figure 19 Figure 20 Figure 2)

Claims (6)

[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 is communicated with a space having a lower pressure than the oil reservoir through an oil supply passage, and an oil supply passage control is provided in the middle of the oil supply passage. A valve device is provided, and the actuator of the oil supply passage control valve device controls the pressure difference between a first compression chamber that does not communicate with either the discharge chamber or the suction chamber and a second compression chamber that is in a pre-compression stroke than the first compression chamber. or a spring device having a shape memory characteristic whose biasing force differs depending on the pressure difference between the first compression chamber and the suction chamber or the suction side leading thereto, or the temperature of the spring device and the pressure difference to cause the oil supply passage to flow. open and close, and open the oil supply passage when the differential pressure exists or does not exceed the set differential pressure, and when the differential pressure does not exist or exceeds the set differential pressure, or the spring device exceeds the set temperature. A scroll gas compressor comprising the oil supply passage control valve device that closes the oil supply passage when a biasing force is changed. (2) The scroll gas according to claim 1, wherein the oil reservoir is an oil reservoir communicating with the discharge chamber, and a space with a lower pressure than the oil reservoir is a suction passage and a drive chamber in which an oil supply device is arranged. compressor. (3) The oil reservoir is an oil reservoir that communicates with the discharge chamber, and a space with a lower pressure than the oil reservoir is not communicated with the suction chamber but is a third compression chamber in the pre-compression stroke than the first compression chamber. Scroll gas compressor according to scope 1. (4) The oil reservoir is an oil reservoir communicating with the discharge chamber, and a space with a lower pressure than the oil reservoir is connected to the suction passage, and a drive chamber and a third compression chamber in which an oil supply device is arranged are provided in claim 1. Scroll gas compressor as described in Section 1. (5) The scroll according to claim 1, wherein the oil reservoir is an oil reservoir communicating with the discharge chamber, and the space whose pressure is lower than the oil reservoir is a sliding part oil reservoir, a gap, or a sliding part oil groove. gas compressor. (6) The oil reservoir is defined as a back pressure chamber on the side opposite to the compression chamber of the orbiting scroll, and the space with lower pressure than the oil reservoir is defined as a suction chamber, a second compression chamber, or a third compression chamber. Scroll gas compressor as described in Section 1.