KR970005860B1 - Multi-stage gas compressor provided with bypass valve device - Google Patents

Abstract

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Description

[Name of invention]

Multi-stage gas compressor with bypass valve device

[Brief Description of Drawings]

1 is a piping system diagram of a two-stage compressed refrigeration cycle using a conventional two-stage refrigerant compressor.

2 is a plan explanatory diagram of a compression mechanism in the compressor.

3 is a detailed cross-sectional view of the lubricator in the compressor.

4 is an explanatory diagram of compression timing in another conventional two-stage compressor.

5 is a cross-sectional view of a main compression portion of the compressor.

6 is a piping system diagram of a two-stage compressed refrigeration cycle using a two-stage refrigerant compressor according to the first embodiment of the present invention.

7 is a sectional view of the compressor.

8 is a sectional view of a main part of the compression in the compressor.

9 is a perspective view of a bypass valve used in the compressor.

FIG. 10 is a partial plan view along the line A-A in FIG. 8. FIG.

Fig. 11 is a sectional view of the main part of the compression showing the operating states of the bypass valve device and the directional control valve device in the compressor.

12 is a partial sectional view of the main compression of the two stage refrigerant compressor of the second embodiment of the present invention.

13 is a longitudinal sectional view of the two-stage refrigerant compressor of the third embodiment of the present invention.

14 is a partial cross-sectional view taken along line B-B in FIG.

15 is a longitudinal sectional view of a two-stage refrigerant compressor of the fourth embodiment of the present invention.

Detailed description of the invention

[Technical Field]

The present invention relates to the improvement of the compression efficiency and durability and the reduction of vibration and noise by the suppression of abnormal pressure rise in the communication path between the low-stage compression element and the high-short compression element in a multistage compressor.

[Background]

In recent years, in the field of refrigeration equipment, research on the practical use of refrigerant compressors suitable for high-compression ratio operation has been prevalent as part of securing a low-temperature heat source and a high-temperature heat source.

In particular, various multistage rotary compressors have been proposed as a measure for improving the compression efficiency by reducing the pressure difference between the compression chamber and the suction chamber to reduce the amount of leakage gas during compression.

Specifically, a two-stage compression refrigeration cycle system diagram in which a roller piston rotary two-stage compressor and a dynamic compressor are connected is proposed in the configuration of FIGS. 1 to 3 (Japanese Patent Laid-Open No. 50-72205). In the same drawing, a driving motor 1005 is connected to the upper part of the sealed container 1003, and a rotating side 1005c of the driving motor 1005 is connected to the lower part, and the compression mechanism formed in two upper and lower stages (the upper part is a low compression mechanism ( 1007), a lower portion of the high pressure compression mechanism 1009 is disposed in the bottom (oil basin), the vane (bane) for each cylinder of the low compression mechanism (1007), high pressure compression mechanism (1009) to the suction chamber and the compression chamber The back surface of (1007c) and (1009c) passes into the interior space of the sealed container (1003), and the back pressure applied to the vanes (1007c) and (1009c) is formed by the reaction force of the spring device and the pressure in the sealed container (1003). have.

The refrigerant gas discharged from the low compression mechanism 1007 is connected to an external gas-liquid separator 1017 via the discharge pipe 1007e, and is again internally sealed through the communication tube 1009d '. Inflow to the cooling of the drive motor (1005).

When the discharged refrigerant gas re-introduced into the sealed container 1003 passes through the suction pipe 1009d provided with the oil absorption pipe 1023, the lubricating oil at the bottom of the sealed container 1003 is sucked and introduced into the high pressure compression mechanism 1009. Lubricant is then provided for cooling the sliding surface and sealing the compression chamber clearance.

The exhaust refrigerant gas recompressed by the high pressure compression mechanism (1009) is sent to the external measuring device (1013) via the discharge pipe (1009e), and the first expansion valve (1015), gas-liquid separator (1017), second expansion valve 1019, the evaporator 1021 is sequentially returned to the low compression mechanism 1007 through the suction pipe 1007d.

In addition, although there is no illustration in the embodiment, in order to improve the large torque fluctuation during compression, which is a drawback of the rotary piston type rotary compressor as described in the description, the difference is 180 degrees in the crank part eccentric direction of the rotating shaft 1005c. The positive compression mechanism (low compression element mechanism 1007, high pressure compression element mechanism 1009) causes the attachment direction of the vanes 1007c and 1009c to be 75 to 80 degrees between the high end side and the low end side. Accordingly, a method of reducing torque fluctuations has been proposed than in rotary single stage compressors.

The two-stage compression refrigeration cycle is constructed by such a component device, and the inner space of the sealed container 1003 is studied to maintain the intermediate pressure such as the condensation pressure and the evaporation pressure of the refrigerant.

However, in the configuration as shown in FIGS. 1 to 3, the refrigerant gas flowing into the suction side of the high pressure compression element mechanism 1009 is heated when passing around the drive motor 1005. There is a problem that a significant decrease in the compression efficiency occurs due to a decrease in the refrigerant gas suction efficiency and an abnormal pressure rise of the refrigerant gas during compression.

As is well known, the suction cylinder volume of the high pressure compression element mechanism 1009 in the two-stage compressor is set to correspond to the volume of refrigerant gas discharged from the low pressure compression element mechanism 1007, but the suction and discharge of the positive compression element mechanism is equivalent. In the stroke period, there is an oversufficiency between the volume of the refrigerant gas discharged from the low compression element mechanism 1007 and the suction cylinder volume of the high compression element component 1009. As a result, pressure pulsation occurs in the intermediate passage passing between the positive compression elements. As a result of this, the discharge pressure is momentarily increased in the low compression element mechanism 1007, or the suction pressure is momentarily lowered in the high compression element mechanism 1009, causing the compression ratio to fluctuate, resulting in an input loss.

For this reason, in a configuration in which the intermediate passage passing between the positive compression elements bypasses the pipe outside the sealed container, and the remarkably long configuration, the compression device becomes large and the high pressure compression element mechanism 1009 follows the suction gas. There was a problem that a delay occurred and the input loss increased.

As mentioned above, measures to improve the problems of the two-stage compressor described above have been proposed as shown in FIGS. 4 and 5 (Japanese Patent Laid-Open No. 1-247785).

The compressor directly communicates between the low compression element (2005) and the high compression element (2006) in the compressor to reduce the size of the two-stage compressor, and discharges the exhaust gas discharged from the high compression element (2006) to the motor compartment. It is configured to mainly pressurize the back of the vane for dividing the cylinder into the suction chamber and the compression chamber by cooling the electric motor by using lubricating oil acting as the discharge pressure.

4 is an explanatory diagram of the compression timing between the high stage compression element 2006 of the low stage compression element 2005 of the compressor, and FIG. 5 is a partial cross-sectional view of the dynamic compressor, and the low stage disposed inside the vertical hermetic casing 2001. Crankshaft 2004 for driving compression element 2005, its valve cover 2028, intermediate frame 2020 through positive compression element 2005, 2006, positive compression element 2005, 2006, low stage A passage 2023, (not shown in FIG. 5), etc., which pass through the discharge side of the compression element 2005 and the suction side of the high stage compression element 2006, and the like, are provided, and the pressure pulsation of the passage 2023 is reduced. In order to reduce the loss, the vanes (2011) and (2012) are arranged 90 degrees apart and vertically sealed casings to delay the compression timing of the high compression element (2006) by about 90 degrees from the low compression element (2005). 2001) is filled with the exhaust gas of the high compression element (2006).

Furthermore, the refrigerant gas compressed by the low stage compression element 2005 joins the low stage discharge chamber formed by the valve cover 2027 and then the high stage compression element 2006 through the passage 2023 and (not illustrated in FIG. 5). Inlet to the suction side of the) and then compressed, discharged to the high stage discharge chamber surrounded by the valve cover 2028, and then sent to the electric motor chamber disposed above.

However, for a short time immediately after starting the compressor, the refrigerant is introduced into the suction side of the low stage compression element 2005 and stayed in the cylinder of the low stage compression element 2005 of the refrigerant liquid or the evaporated refrigerant during the compressor stop. Since the amount of refrigerant gas far exceeding the cylinder suction volume of 2006) is discharged into the valve cover 2027, the pressure rise of the passage 2023 is rapid, and as a result, the compression torque of the lower stage compression element 2005 becomes large, so that Due to the large vibration, there were problems such as the cost increase due to the enlargement of the motor and the limit of the power supply equipment due to the increase of the starting current.

In addition, the pressure rise in the vertical hermetic casing 2001 is slow due to the low discharge side temperature for a while immediately after the compressor cooler is started, and the vane 2012 of the high stage compression element 2006 until the constant pressure is reached. Lack of pressing force acting on the back.

In such a state, since the pressure rise of the passage 2023 is fast, the suction pressure (pressure in the passage 2023) is higher than the back pressing pressure of the high stage compression element 2006 to the vane 2012, causing a drastic jump in the vane 2012. . As a result, there is a problem that the noise and vibration are large and the durability of the vanes 2021 and the rollers 2008 is deteriorated according to the violent collision sound generated between the tip of the vanes 2012 and the rollers 2008 and the vibration thereof. .

In addition, due to the drastic leap phenomenon of the vane 2012, there are a lot of refrigerant gas leakage from the compression chamber to the suction chamber, and the compression efficiency of the initial startup during cooling causes a significant decrease.

Furthermore, if frost adheres to the surface of the heat exchanger side during the hot water supply operation or air conditioning heating operation during the winter period using two stage compression and two stage expansion refrigeration cycles, the pipe to the heat absorber side and the pipe to the radiator side are Immediately after switching to the solenoid valve and starting the defrost operation, a large amount of high-pressure liquid refrigerant on the radiator side flows into the suction side of the two-stage compressor, and the hydraulic side is generated by the low stage compression element 2005. The pressure rose abnormally. On the other hand, as the pressure on the discharge side of the high stage compression element 2006 drops sharply in accordance with the switching to the defrosting operation, the pressure in the passage 2023 is higher than the discharge side of the high stage compression element 2006, so that the above-mentioned vanes (2011) (2012) There was an important problem peculiar to the two-stage compressor that the compressor breaks due to the leap phenomenon.

In addition, although the problems with the rotary piston type rotary two-stage compressor have been described above, the slide vane rotary two-stage compressor, the reciprocating two-stage compressor, the vortex two-stage compressor, etc., in which the vanes rotate together with the drive shaft, will be described in detail. As mentioned above, it is apparent that the compression torque of the initial startup is large, and thus the vibration is large, and the present invention is apparent in the problems such as the cost increase due to the enlargement of the electric motor and the limitation of the power supply equipment due to the increase of the starting current.

[Description of the Invention]

The present invention aims to reduce the compressor starting load, vibration and noise in view of the above-described conventional problems.

Specifically, the exhaust gas is discharged from the final compression element by constructing a multi-stage compression mechanism in which the discharge side of the low stage compression element and the suction side of the high compression element are connected in series through a communication path. Compressed gas is discharged into the space and an oil tank is disposed at the bottom thereof to form a bypass passage between the exhaust gas discharge space and the space therebetween, and a communication passage in the middle of the bypass passage. When the pressure of the gas is higher than the pressure of the exhaust gas discharge space, it is arranged in the bypass valve device to allow the opening of the gas from the communication to the exhaust gas discharge space or the space therethrough.

In addition, the present invention is to prevent the vanes of the defrosting operation in the heating operation mode during the initial start or winter period between the piston and the piston to reduce the vibration, noise and improve the durability. It is for the purpose.

Specifically, a multistage compression mechanism is constructed in which the discharge side of the low stage side compression element and the suction side of the high stage side compression element among the multiple compression elements are connected in series through a sequential communication path to discharge the exhaust gas space in the final stage compression element. Discharge the compressed gas at the same time, arrange an oil tank at the bottom thereof, and form a bypass passage between the communication passage and the discharge gas discharge space or the space connected thereto, and the pressure of the communication passage discharges the exhaust gas in the middle of the bypass passage. A vane that divides the suction chamber and the compression chamber while advancing and retracting each cylinder of the compression element while arranging a bypass valve device that allows the opening of the exhaust gas from the communication path to the discharge space or the space connected thereto when the pressure is higher than the space pressure. The vane is discharged from the final compression element and separated from the exhaust gas into the rear chamber of Ke is a back-pressure pressing.

The present invention also aims to prevent lubricating oil from flowing out of the compressor when the gas in the communication path between the low compression element and the high compression element is temporarily bypassed to the discharge side of the high compression element in order to temporarily reduce the compression load. I did it.

Specifically, the exhaust gas from the final stage compression element is constructed by constructing a multistage compression mechanism in which the discharge side of the low stage compression element and the suction side of the high stage compression element among the several compression elements are sequentially connected in series and via a communication path. At the same time the compressed gas is discharged into the discharge space, an oil tank is disposed at the bottom thereof, and a bypass passage is formed between the communication passage and the discharge gas discharge space or the space connected thereto, and the pressure of the communication passage is discharged in the middle of the bypass passage. Bypass valve devices are provided to allow the opening of only the communication path from the communication path to the discharge gas discharge space or the positive communication space when the pressure is higher than the pressure of the gas discharge space, and at the same time, the bypass passage is communicated with the discharge chamber of the high stage compression element.

In addition, the present invention is configured to temporarily bypass the gas in the communication path between the low-stage compression element and the high-stage compression element to the discharge side of the high-stage compression element to temporarily reduce the compression load. It is an object to prevent the deterioration of multistage function.

Specifically, a multistage compression mechanism is formed by serially connecting the discharge side of the low-speed compression element and the suction side of the high-speed compression element among the several compression elements through serial communication paths, and then discharge the exhaust gas from the final compression element. Discharge the compressed gas into the space and place an oil tank at the bottom, and form a bypass passage between the communication passage and the discharge gas discharge space or the space connected thereto so that the pressure of the communication passage discharges the exhaust gas during the bypass passage. The spring device is provided with a pressurizing valve which pressurizes the valve body of the bypass valve device to the valve seat while arranging a bypass valve device allowing opening of the exhaust gas discharge space from the communication path or the space connected thereto when the pressure is higher than the space pressure. Acted upon.

In addition, the present invention is configured to bypass the gas in the communication path between the low stage compression element and the high stage compression element temporarily to the discharge side of the high stage compression element in order to temporarily reduce the compression load, and to reduce the load when starting the compressor during cooling, An object of the present invention is to improve the compression efficiency by improving unnecessary gas leakage from the discharge chamber side at the time of stable operation to the communication path side.

Specifically, a multistage compression mechanism in which the discharge side of the low stage side compression element and the suction side of the high stage side compression element among several compression elements are connected in series through a sequential communication path constitutes a discharge gas from the final stage compression element. At the same time as the discharge gas is discharged into the discharge space, an oil tank is disposed at the bottom to form a bypass passage between the communication path and the discharge gas discharge space or the space therebetween, and the pressure of the communication path in the middle of the bypass passage is the discharge gas. A bypass valve device is provided to allow the opening of only the exhaust gas discharge space from the communication path or the space connected thereto when the pressure is higher than the discharge space pressure, and at the same time, the pressing force for pressing the valve body of the bypass valve device to the valve seat side is applied. Acting as a spring device, which increases its pressing force when its temperature rises, If the temperature is lowered having a shape memory characteristic to decrease the pressing force.

In addition, the present invention is configured to bypass the gas in the communication path between the low stage compression element and the high stage compression element temporarily to the discharge side of the high stage compression element in order to temporarily reduce the compression load to follow the increase in the discharge pressure of the high stage side after starting the compressor. The purpose of the present invention is to improve the durability of the compressor by smoothly controlling the load from the starting to the safe operation area by reducing the load reduction.

Specifically, a multistage compression mechanism is constructed in which the discharge side of the low stage compression element and the suction side of the high stage compression element among the several compression elements are connected in series through a sequential communication path, and the exhaust gas discharge space from the final stage compression element. The discharge tank was discharged and at the same time, an oil tank was disposed at the bottom thereof, and a bypass passage was formed between the communication passage and the discharge gas discharge space or the space connected thereto, and the pressure of the communication passage discharged the discharge gas during the bypass passage. A bypass valve arrangement is arranged to allow the opening of only the exhaust gas discharge space from the communication path or the space therethrough when the pressure is higher than the space pressure, and at the same time, the exhaust gas discharge space or the back side of the valve body of the bypass valve apparatus. The pressure of the space connected thereto is applied to press the valve body toward the valve seat.

In addition, the present invention reduces the expansion sound when the gas is bypassed in the configuration of temporarily bypassing the gas in the communication path between the low-compression element and the high-compression element to the discharge side of the high-compression element in order to temporarily reduce the compression load. At the same time it is intended to prevent the leakage of lubricant on the discharge side.

Specifically, a multi-stage compression mechanism in which the discharge side of the low stage side compression element and the suction side of the high stage side compression element among several compression elements are connected in series through a sequential communication path is configured to discharge the exhaust gas from the final stage compression element. At the same time as the compressed gas is discharged, an oil tank is disposed at the bottom thereof, and a bypass passage is formed between the communication passage and the discharge gas discharge space or the space therebetween, and the pressure of the communication passage is the discharge gas discharge space in the middle of the bypass passage. The bypass valve device is arranged to allow the opening of only the exhaust gas discharge space from the communication path or the space connected thereto when the pressure is higher than the pressure, and the discharge chamber of the high stage compression element is disposed immediately downstream of the bypass valve device. will be.

[Best form for carrying out the invention]

Hereinafter, the rotating piston type rotary two-stage refrigerant compressor according to the first embodiment of the present invention will be described with reference to FIGS.

6 is a rotary piston rotary two-stage refrigerant compressor (1) having an accumulator (2), a condenser (13), a first expansion valve (15), a gas-liquid separator (17), and a second expansion valve. 19 shows a piping system of a two-stage compression expansion refrigeration cycle in which the evaporator 21 is sequentially connected. FIG. 7 is a cross-sectional view of the rotary piston rotary two-stage compressor 1, and FIG. 8 is a two-stage compression mechanism. The main part of the means details.

An electric motor 5 is arranged in the electric motor chamber 8 of the upper space in the sealed container 3, and a two-stage compression mechanism 4 is arranged in the lower part thereof, and the outer peripheral part and the bottom part are comprised as oil tanks 35. .

The stator 5a of the electric motor 5 is fixed to the inner wall of the airtight container 3 so as to contract.

The two stage compression mechanism 4 is composed of a flat intermediate plate 36 disposed between the upper high stage compression element 9 and the lower stage low compression element 7 and the two compression elements 7, 9. The inner cover of the sealed container 3 is welded and fixed at several places (not shown) of the discharge cover A 37 of the low compression element 7 and the outer circumferential portion of the intermediate plate 36.

The cylinder volume of the high stage compression element 9 is set to 45 to 65% of the cylinder volume of the low stage compression element 7.

The upper bearing member 11 attached to the upper side of the second cylinder block 9a of the high stage compression element 9 and the lower bearing member attached to the lower side of the first cylinder block 7a of the low stage compression element 7. The drive shaft 6 supported by 12 is fixed to the rotor 5b of the electric motor 5.

The 1st crankshaft 6a and the 2nd crankshaft 6b of the drive shaft 6 are arrange | positioned so that the eccentric direction may mutually differ 180 degree.

7b and 9b are first pistons and second pistons mounted on the first crankshaft 6a and the second crankshaft 6b of the drive shaft 6, and 38 and 39 are first pistons. (7b), vanes (40) and (41) which contact the outer circumferential surface of the second piston (9b) to partition the inside of each cylinder of the low stage compression element (7) and the high stage compression element (9) into a suction chamber and a compression chamber. Coil springs for pressing the back of the vanes 38 and 39.

The rear end of the coil spring 41 of the high stage compression element 9 is supported on the inner wall of the hermetic container 3, while the rear end of the coil spring 40 of the low stage compression element 7 is connected to the first cylinder block 7a. It is supported by a cap 42 attached to it.

The rear chamber B 43 of the vane 39 of the high stage compression element 9 is opened to the oil tank 35, but the rear chamber A 44 of the vane 38 of the low stage compression element 7 has a cap 42. The end is sealed in order to be cut off from the oil tank 35.

The discharge cover A 37 of the low stage compression element 7 is attached to the first cylinder block 7a together with the lower bearing member 12 to form the low stage discharge chamber 45, and the bottom thereof is the discharge chamber oil tank 46. )to be.

The discharge chamber oil tank 46 is fixed to the discharge cover A 37 and is partitioned from the upper space of the low stage discharge chamber 45 by the partition plate 48 having a plurality of small holes 47. Back chamber A (44) of the vane (38) via an oil return passage (49) consisting of an oil return hole (A) (49a) and an oil return hole (B) (49b) provided in the discharge cover A (37) and the lower bearing (12). It leads to.

The discharge cover B 50 formed with the vibration damping eyes is arranged to surround the outer circumference of the upper bearing member 11 to form a high stage discharge chamber 51.

The silencer 52, which is provided at the end of the rotor 5b of the electric motor 5, is disposed between the protrusion 50a of the discharge cover B 50 surrounding the outer circumference of the protrusion 11a of the upper bearing member 11. While communicating with the high stage discharge chamber 51 via the ring-shaped passage 53 of the rotor, the ring-shaped between the inner surface of the end ring 5c of the rotor 5b and the protrusion 50a of the discharge cover B50. It communicates with the inner space of the sealed container 3 via the upper passage 54.

The low stage discharge chamber 45 and the suction chamber 56 of the high stage compression element 9 are gas passage A 55a provided in the lower bearing member 12, and gas passage B 55b provided in the first cylinder block 7a. The gas passage C 55c provided in the middle steel plate 36 communicates with the communication passage 55 through the communication passage 55.

The bypass passage 57 branched in the middle of the communication passage 55 includes the bypass passage A 57a and the bypass passage provided in the second cylinder block 9a of the high compression element 9 and the bearing member 11. It is formed of B 57b, and its downstream side opens to the high stage discharge chamber 51.

Bypass valve A 57a includes a valve body 58a made of a thin steel plate (not shown in FIG. 9) having a notch in its outer circumference and a coil spring 58b. A 58 is mounted, and the bypass valve device 58 permits fluid flow only from the communication path 55 to the high stage discharge chamber 51.

The coil spring 58b is made of a shape memory alloy that deforms so that the coil pitch becomes wider and its free length increases when the temperature rises, and the coil spring 58b has a shape memory in which the spring constant increases in the assembled state. Since it is equipped with the characteristic, the pressing force to the valve main body 58a becomes strong. On the contrary, since the coil spring 58b has a shape memory characteristic that the coil pitch becomes narrow when the temperature decreases itself, the coil pitch is narrowed, and the free length is deformed to reduce the spring constant in the assembled state. The pressing force becomes weak.

The gas passage B 55b constituting a part of the communication passage 55 communicates with the downstream side of the gas-liquid separator 17 via the communication tube 59 and forms the refrigerant injection passage 72.

The communicating tube 59 was inserted into the first cylinder block 7a, and the outer circumference of the connection portion was sealed with an O-ring 66, and the valve body having a shape similar to that of FIG. 9 between the end portion and the gas passage B 55b. 60 is arrange | positioned and comprises the directional control valve apparatus 71. As shown in FIG.

The direction control device 71 is configured to allow fluid inflow from the gas-liquid separator 17 only to the gas passage B 55b.

The intermediate plate 36 is provided with an oil injection passage 61 provided with a restriction part in the middle of the passage, the upstream side of which is the oil tank 35 and the downstream side of the back chamber A 44 of the vane 38 and the high stage compression element ( They are installed so as to intermittently communicate with the compression chamber of 9).

The downstream passage A 61a and the rear chamber A 44 of the downstream passage 61 of the oil injection passage 61 are opened when the vane 38 advances approximately half or more strokes to the piston 7b side. Otherwise, the opening is opened in the sliced end surface of the vane 44 so as to be blocked.

The downstream passage B (61b) of the oil injection passage (61) and the compression chamber of the high stage compression element (9) are opened when the vanes (39) are advanced to the piston (7b) side until approximately one third stroke. When the stroke of approximately one-third of the stroke is retracted, it is opened at the position at which the interruption is started by the end face of the slide lamp of the piston 9b. (See Figure 10)

The shaft hole 62 which penetrated was provided in the shaft center part of the drive shaft 6, and the pump apparatus 63 is mounted in the lower part.

Peripheral spiral oil grooves 64, 64a of the drive shaft 5 supported by the upper bearing member 11 and the lower bearing member 12 were provided and upstream of the spiral oil groove 64. The side was passed to the downstream side of the pump device 63 via the radial oil hole branched from the shaft hole 62, and the downstream side of the spiral oil groove 64 is not opened to the noise chamber 52.

The downstream side of the accumulator 2 communicates with the suction chamber (not shown) of the low stage compression element 7 and the discharge pipe 7e is provided at the top of the sealed container 3.

A liquid pipe 65 connected to the second expansion valve 19 is connected to the bottom of the gas-liquid separator 17. A polyethylene membrane is coated on the outer body surface of the gas-liquid separator 17, and then heated and foamed to about 5 mm. It is thermally insulated with the foam material 67.

11 shows the opening state of the bypass passage 57 immediately after driving the compressor cooler, the end of the communication tube 59 is closed, and the downstream passage 61a of the oil injection passage 61 and the rear side. The state which cut off between the yarn A 44 with the vane 38 was shown.

FIG. 12 shows that the oil injection passage 61c having a restriction passage portion communicating between the oil tank 35 and the rear chamber A 44 is extremely shallow at the joint surface portion of the intermediate plate 35 and the first cylinder block 7a. In the present invention, a groove is provided to form a restrictive passage and an opening of the oil return hole C 49c from the low stage discharge chamber 45 to the rear chamber A 44 is provided in the upper portion of the rear chamber A 44. Two examples are shown.

Next, a slide vane-type rotary two-stage refrigerant compressor according to a third embodiment of the present invention will be described with reference to FIG. 13 and FIG.

Similar to the first embodiment, the two-stage compression mechanism 104 is configured by sequentially placing the intermediate plate 136 and the low stage compression element 107 on the top of the high stage compression element 109.

In the drive shaft 106 connected to the rotor 5b of the electric motor 5, the high stage compression element 109 performs suction and compression with a phase delay of about 60 to 80 degrees with respect to the suction and compression timing of the low stage compression element 107. The first rotor 107b and the second rotor 109b are disposed and fixed to start, and the vane 138 is disposed in the vane groove 68a accommodated in the first rotor 107b, and the second rotor ( A vane 139 is disposed in the vane groove 68b provided in 109b. The vane groove 68b and the oil tank 35 of the high stage compression element 109 have a shaft hole 162 provided through the drive shaft 106, a radial hole 69 branched from the shaft hole 162, and an intermediate plate. It always communicates via the ring-shaped groove 70 provided on the side surface of the second rotor 109b of 139.

The downstream passage B (161b) of the oil injection passage 161 having the restricting passage portion provided in the intermediate plate 139 was intermittently communicated with the compression chamber of the high stage compression element 109 as in the first embodiment. The position where the passage B 161b opens to the compression chamber corresponds to the position where the tip of the vane 139 is most advanced.

Further, the downstream side passage A 161a of the oil injection passage 161 intermittently communicates with the vane groove 68a as the first rotor 107b of the low stage compression element 107 rotates, and the vane groove An oil return passage 149 consisting of an oil return hole B (149b) provided in the lower bearing member 112 of the low stage compression element 107, and an oil return hole A (49a) provided in the discharge cover A 37. Through the through to the low stage discharge chamber (45).

Other configurations are the same as those in the first embodiment, and thus description thereof is omitted.

Next, the configuration at the time of discharging the front-side compression element of the rolling piston rotary two-stage refrigerant compressor of the fourth embodiment of the present invention, the configuration of the oil supply passage, and the like will be described with reference to FIG.

The inner diameter of the tube is 1.5 times larger than the suction tube of the accumulator used in the conventional single stage compressor, and the supercharging action of the accumulator (following the suction action of the compressor, and the gas pressure in the suction tube causes pulsation phenomenon). And the downstream side of the first accumulator 202 having the suction pipe 202a which suppresses the phenomenon that the gas, which periodically rises in pressure, flows into the suction chamber and is compressed in such a state, the suction efficiency increases. Similarly, it is connected to the suction side of the low stage compression element 207.

The low stage discharge chamber 245 of the low stage compression element 207 has a discharge cover A 237 and a first cylinder attached to the first cylinder block 207a so as to surround the lower bearing member 212 supporting the drive shaft 6. It is formed by the block 207a, and its contents are smaller than the structure of the first embodiment.

The high stage compression element 209 has a low stage compression element 207 which starts suction and compression with a phase delay of about 60 to 80 degrees with respect to the suction and compression timing of the low stage compression element 207. It is arranged to reduce the compression power in the low stage compression element 207 by suppressing the pressure rise.

The low stage discharge chamber 245 communicating with the rear chamber A 244 is connected at its upper end to the suction side of the high stage compression element 209 via the communication passage 255, and connected to the communication passage 255 in the middle thereof. The second accumulator 202b is connected upstream to the gas-liquid separator (not shown) as in the case of the first embodiment, and a valve body 206 similar to the first embodiment is attached to the downstream end thereof. have.

The valve 206 was pressurized to form a directional control valve device 271 by pressing a coil spring 270 for blocking the open end of the connection from the gas-liquid separator 17, and the coil spring 270 raised its own temperature. The spring constant is reduced, and the shape memory characteristic of reducing the pressing force to the valve 206 is provided.

Other configurations are the same as those in the first embodiment, and thus description thereof is omitted.

The operation of the two stage compressor and its refrigeration cycle configured as described above will be described.

6 to 11, when the drive shaft 6 is rotated by the motor 5, first, the low stage compression element 7 starts suction, and the refrigeration gas from the heat accumulator 2 is reduced. Flows into the suction chamber of 7). As the crank angle of the drive shaft 6 advances, the volume of the low stage suction chamber increases, while the compression operation in the low stage compression chamber proceeds simultaneously, and the compressed refrigerant gas pressure gradually increases.

The compressed refrigerant gas is discharged from the discharge port (not shown) installed in the lower bearing member 12 to the low stage discharge chamber 45 at the time when the low stage side crank angle progresses about 170 degrees after the start of the suction operation.

The refrigerant gas discharged into the low stage discharge chamber 45 is stored in the bottom of the discharge chamber oil tank 46 via the oil return passage 49 formed of the oil return hole 49a and the oil return hole B 49b. And back flows into the back chamber A 44, the back surface of the vane 38 is pressurized to the first piston 7b side.

Immediately after starting, the refrigerant gas discharged into the low stage discharge chamber 45 passes through the communication passage 55 consisting of the gas passage A 55a, the gas passage B 55b, and the gas passage C 55c. Is sent to the suction chamber (56).

60 to 80 degrees is delayed from the start of suction of the low stage compression element 7, and the suction and compression action of the high stage compression element 9 is started.

The refrigerant gas in the low stage discharge chamber 45 and the communication passage 55 immediately after starting is condenser 13 and gas-liquid separator which are connected to the internal space of the sealed container 3 or the rotary piston type rotary two-stage compressor 1. It is higher than (17).

Accordingly, as shown in FIG. 11, the valve 60 moves along the pressure difference between the refrigerant gas passing through the communication path 55 and the gas-liquid separator 17, so that the end of the connecting tube 59 of the gas-liquid separator 17 moves. If it is blocked, the refrigerant gas in the communication path 55 is prevented from flowing back to the gas-liquid separator 17.

In addition, the refrigerant gas pressure of the communication path 55 is higher than the pressure of the high stage discharge chamber 51 leading to the interior space of the sealed container 3, and the valve body 58a of the bypass valve device 58 is the coil spring ( Resisting to the pressing force of 58b), it moves to the coil spring 58b to open the bypass passage 57, and a part of the refrigerant gas passing through the communication passage 55 flows out into the high stage discharge chamber 51 to suck the suction chamber ( The refrigerant gas pressure of 56 drops. As a result, the vanes 39 of the high-stage compression element 9, which depend on the pressing force of the coil spring 41 only, can prevent the jumping phenomenon occurring in the case of sudden retreat as the refrigerant gas which has risen in pressure rapidly enters the suction chamber 56. Without causing, retreating following the movement of the outer circumferential surface of the second piston 9b and starting a smooth light load compression operation without generating a collision sound or leakage of compressed gas between the vanes 39 and the second piston 9b. .

In addition, the refrigerant gas discharged from the low stage compression chamber to the low stage discharge chamber 45 by initiating the suction and compression operation of the high stage compression element 9 with a delay of 60-80 degrees from the start of the suction and compression action of the low stage compression element 7. An overdeficiency occurs between the volume and the suction chamber volume of the high stage compression element 9, and the overdeficiency thereof changes with the progress of the crank angle of the drive shaft 6. As a result, a pressure pulsation occurs in the refrigerant gas in the low stage discharge chamber 45 and the communication path 55 because there is a range of crank angles and a range of excess crank angles in which the amount of refrigerant gas discharged to the low stage discharge chamber 45 is insufficient. do.

This pressure pulsation means a tendency to occur violently as the rotational speed of the drive shaft 6 increases.

The discharged refrigerant gas discharged into the high stage discharge chamber 51 flows into the noise chamber 52 through the annular passage 53, and then is discharged into the sealed container 3 via the annular passage 54.

The pressure of the electric motor chamber 8 and the condenser 13 and the gas-liquid separator 17 which rises with the time elapsed after the compressor cools down increases, and the bypass valve device 58 in the bypass passage 57 is increased. The valve main body 58a is pressurized by the coil spring 58b which increases its spring constant as the gas pressure and temperature rise of the high stage discharge chamber 51 close the bypass passage 57, and at the same time the The valve 60 which closed the end part moves to the communication path 55, and the gas liquid separator 17 and the communication path 55 open.

In addition, the lubricating oil of the oil tank 35 to which the back pressure acts presses the back surface of the vane 39 together with the coil spring 41 of the high stage compression element 9 while lubricating the sliding surface of the vane 39. A small amount flows into the suction chamber 56 and the compression chamber via the sliding surface gap. In addition, the lubricating oil is depressurized through the downstream side passage B (61b) of the oil injection passage (61) having the restriction passage portion and intermittently lubricated to the compression chamber to seal the oil film between the poles of the compression chamber, and the slit of the second piston (39). It is provided for lubrication of cotton.

In addition, the lubricating oil of the oil tank 35 is decompressed to the discharge pressure of the low stage compression element 7 via the downstream passage A 61a of the oil injection passage 61 having the restriction passage portion, and then the low stage compression element ( 7) The vane 38 of the downstream side A (61a) to the rear chamber A (44) while the vane 38 is retracted to about one third at the time when the vane 38 is advanced to the first piston (7b) by about one third. The opening opens and flows into the back chamber A 44.

The lubricating oil flowing into the back chamber A (44) lubricates the back surface of the vane (38) and flows into the low stage discharge chamber (45) through the oil return hole (49b) and the oil return hole (A) 49a. The mixture is mixed with the discharged refrigerant gas and flows into the suction chamber 56 of the high stage compression element 9.

The lubricating oil flowing into the suction chamber 56 of the high stage compression element 9 joins the lubricating oil introduced through the rear chamber B 43 and the downstream side passage 61b to lubricate the seal and the back surface of the compression chamber. Is provided for overcooling.

In addition, the lubricating oil of the oil tank 35 has a viscous pump action due to the spiral oil groove 64 provided on the surface of the drive shaft 6 and a pump device 62 provided at the lower end of the drive shaft 6. Lower bearing member 12 for supporting drive shaft 6 via 62 or radial hole 69, bearing surface of upper bearing member 11, first piston 7b, second piston 9b It is lubricated to the inner side of The lubricating oil supplied to the spiral oil groove 64a is discharged from the upper end of the bearing of the upper bearing member 11 to the noise chamber 52 according to the viscosity pump action, and the high pressure of the two-stage compression discharged from the high stage discharge chamber 51. After mixing with the exhaust gas is discharged to the electric motor chamber 8 via the annular passage (54).

The discharge refrigerant gas from which the lubricating oil is separated in the electric motor chamber (8) is sent to the refrigeration cycle outside the compressor via the discharge pipe (7e).

After depressurizing the condenser (13) and the first expansion valve (15), the unevaporated refrigerant expanded to the discharge pressure of the low stage compression element (7) flows into the gas-liquid separator (17), and then gas and liquid. Liquid coolant is collected at the bottom of the gas-liquid separator (17). The unevaporated refrigerant gas in the upper space in the gas-liquid separator 17 passes through a communication tube 59 that opens into the upper space in the gas-liquid separator 17 to the communication path 55 in the rolling piston rotary two-stage compressor 1. It flows in and joins the discharge refrigerant gas of the low stage compression element 7 to lower the low stage discharge refrigerant gas temperature, and then flows into the suction chamber 56 of the high stage compression element 9.

The two-stage compressed discharge refrigerant gas of the high stage compression element 9 suppresses abnormal temperature rise by sucking the unevaporated refrigerant gas of the gas-liquid separator 17. As a result, the shrinkage between the slide lamp poles decreases, and the abnormal temperature rise of the motor 5 is suppressed, thereby reducing the compressor input.

On the other hand, the liquefied refrigerant collected at the bottom of the gas-liquid separator 17 absorbs the second expansion and the second expansion valve 19 and the evaporator 21 sequentially through the liquid pipe 65, and then absorbs it again. It returns to the muulator 2.

Furthermore, since the refrigerant in the gas-liquid separator 17 is insulated and sound-proofed by the polyethylene foam member surrounding the outer circumference of the gas-liquid separator 17, the refrigerant and the inner wall of the gas-liquid separator when the refrigerant flows into the gas-liquid separator 17 At the same time as the impact sound is prevented from being charged to the outside, the refrigerant absorbs little.

Next, the operation of the second embodiment will be described with reference to FIG.

The lubricating oil at the bottom of the electric motor chamber (8) to which the discharge pressure acts is depressurized via the downstream side passage C (61c) provided with the restricting portion, and then the rear chamber A (44) of the vane (38) of the low stage compression element (7). After flowing in, it pressurizes the back of the vane 38 in the foamed state and simultaneously lubricates the sliding surface of the vane 38. The lubricating oil of the rear chamber A (44) flows out into the low stage discharge chamber (45) through the oil return passage (49c) and the oil return hole (A) 49a which are always open, but the oil surface height is always high (during compressor operation). In either stop, the level of the upstream opening of the joy return passage 49c is secured, and the lubricating oil pressure corresponds to the pressure of the low stage discharge chamber 45.

The compressor is stopped and then restarted, and the back chamber A 44 is stopped while the compressor is stopped while the pressure of the lubricant of the oil tank 35 is again supplied to the back chamber A 44 via the downstream side passage 61c. Gas pressure from the low stage discharge chamber 45 acts on the remaining lubricating oil to lubricate the sliding surface of the vane 38.

Other operations are the same as those in the first embodiment, and description thereof is omitted.

Next, the operation of the third embodiment will be described with reference to FIG. 13 and FIG.

Following the rotation of the drive shaft 106, the vanes 138, 139 mounted with the vane grooves 68a, 68b of the first rotor 107b and the second rotor 109b reciprocate in the groove and rotate in rotation. do.

According to the reciprocating motion of the vanes 138 and 139, the lubricating oil of the vane grooves 68a and 68b is pumped. According to the pressure generated at that time, the vanes 138 and 139 are pressurized to the outside in the radial direction so that the inside of the cylinder can be divided into the suction chamber and the compression chamber, and the refrigerant gas is sucked and compressed.

The lubricating oil of the oil tank 35 acting on the discharge pressure is reduced in pressure through the injection passage A 161a downstream of the oil injection passage 161, and then intermittently in the vane groove 68a of the first rotor 107b. Pressure is supplied to the vane groove 68b of the second rotor 109b through the shaft hole 162, the radial hole 69, and the annular groove 70, which are sequentially supplied through the drive shaft 106, It is always supplied, without a problem.

The lubricating oil in the foamed state containing the refrigerant gas supplied to the vane groove 68a of the first rotor 107b intermittently has a low stage discharge chamber via the oil return hole B 149b and the oil return hole A 49a. Although it flows into 45, the vane 138 is moderately pressurized appropriately according to the pump action in the case of reciprocation, and is supplied to the lubrication of the sliding surface of the vane 138.

Moreover, although the lubricating oil supplied to the vane groove 68b of the second rotor 109b is always in communication with the oil tank 35, the degree of pump pressurization is small according to the reciprocating motion of the vane 139.

In addition, the lubricating oil of the oil tank 35 is pressure-reduced through the injection passage B 161b downstream of the oil injection passage 161, and is intermittently pressure-lubricated in the cylinder of the high stage compression element 109, and the compression chamber clearance is performed. It is provided in the sealing and lubrication of the sliding surface.

Since other operations are the same as those in the first embodiment, description thereof is omitted.

Next, the operation of the fourth embodiment will be described with reference to FIG. The refrigerant gas flowing into the first accumulator 202 according to the operation of the two-stage compressor suppresses periodic pressure pulsation and is compressed into the suction chamber of the low stage compression element 207 through the suction pipe 202a and then compressed. It is sent out sequentially to the suction side of 209.

Since the supercharging action of the first heat accumulator 202 is suppressed, the intake gas volume to the low stage compression element 207 per revolution of the drive shaft 6 does not change much even if the compressor operation speed is changed. The exhaust gas is sent out at a substantially constant ratio with respect to the cylinder volume of the high stage compression element 209. As a result, the low stage exhaust gas pressure does not increase abnormal input even when the compressor operation speed is varied, and remains substantially constant to reduce overcompression in the compression chamber of the low stage compression element 207.

Unevaporated refrigerant flowing into the second accumulator 202b from the gas-liquid separator (not shown) flows into the suction side of the high stage compression element 209 together with the low stage exhaust gas via the direction control valve device 271.

On the other hand, the low stage discharge refrigerant gas discharged into the low stage discharge chamber 245 having a small inner volume diffuses without separating the lubricating oil and opens the oil injection passage 261 from the oil tank 35 to the adjacent rear chamber A 244. The lubricating oil introduced through is drawn in to lubricate the sliding surface of the rear chamber A 244 and then sent to the high stage compression element 209.

After the compressor stops, the temperature of the coil spring 270 decreases, and the spring constant thereof increases, thereby moving the valve 206 toward the second accumulator 202b, closing the inflow path, and closing the second accumulator 202b while the compressor stops. The liquid refrigerant is prevented from flowing into the communication path 255 via the filter.

Other operations are similar to those in the first embodiment, and thus description thereof is omitted.

As described above, according to the above embodiment, a two-stage compression mechanism in which the discharge side of the low stage compression element 7 and the suction side of the high stage compression element 9 are connected in series via a communication path 55 constitutes a high stage compression element ( 9, the compressed gas is discharged to the electric motor chamber 8 in the airtight container 3 accommodating the electric motor 5, and the oil tank 35 is arranged at the bottom thereof, and the communication path 55 and the electric motor chamber 8 are discharged. Bypass path 57 is formed between the communication path 55 and the motor chamber (8) only when the pressure of the communication path 55 is higher than the pressure of the motor (8) in the middle of the bypass path (57). By arranging the bypass valve device 58 to allow the opening of the compressor, the refrigerant gas sucked into the low stage compression element 7 is compressed and discharged at the same time as the compressor is started, and the high stage compression element 9 is connected via the communication path 55. When the pressure of the refrigerant gas passing through the communication path 55 is discharged to the suction side of the It flows out into the electric motor chamber 8 in the container 3 and starts the compression in the state where the suction gas of the high stage compression element 9 drops in pressure, so that the initial compression load is light and smooth starting is possible. Can be less

In addition, if frost is attached to the surface of the heat exchanger side heat exchanger during hot water supply operation or air-conditioning heating operation during the two-stage compression and two-stage expansion refrigeration cycle, the pipe to the heat absorber side and the pipe to the radiator side are solenoid valves. For a short time immediately after the defrost operation is started by switching to a light source, a large amount of high-pressure liquid refrigerant on the radiator side flows into the suction side of the two-stage refrigerant compressor 1, and liquid compression occurs in the compression chamber of the low stage compression element 7. Even when the pressure in the communication path 55 rises abnormally and the pressure in the motor chamber 8 suddenly decreases due to the switch to the defrost operation, the pressure in the communication path 55 and the motor chamber 8 reverses. The bypass passage 57 is opened to lower the pressure in the communication passage 55 to avoid damage to the compressor.

According to the above embodiment, a two-stage compression mechanism in which the discharge side of the low stage compression element 7 and the suction side of the high stage compression element 9 are connected in series via a communication path 55 is constructed. The compressed gas is discharged into the electric motor chamber 8 in the sealed container 3 collecting the electric motor 5 from the tank, and an oil tank 35 is disposed at the bottom thereof, and the communication path 55 and the electric motor chamber 8 are discharged. The bypass passage 57 is formed therebetween, and in the middle of the bypass passage 57, when the pressure of the communication passage 55 is higher than the pressure of the motor chamber, opening of the communication passage 55 from the communication passage 55 to the motor chamber 8 is performed. The vanes 38 and 39 which divide the suction chamber and the compression chamber while advancing and retracting each cylinder of the low stage compression element 7 and the high stage compression element 9 while arranging a bypass valve device 58 to be allowed. The back chamber A (44) of the back chamber A (44) and the back chamber B (43) of the oil tank (35) acting on the exhaust gas pressure were introduced under reduced pressure and introduced directly. As the upper discharge pressure is applied to the back chamber B 43, the high stage discharge pressure is pressurized, and the high sugar discharge pressure increases with the time after the compressor is started, thereby lubricating oil in the oil tank 35 at the bottom of the electric motor chamber 8. Since the vanes 38 and 39 introduced into the back divide the cylinder into the suction chamber and the compression chamber, the sealing degree is gradually increased, so that the sealability at the start is poor and the compression chamber pressure at the initial stage is not too high. It can start and reduce vibration and noise.

In addition, when the compressor is started and the refrigerant gas sucked into the low stage compression element 7 is compressed and discharged and is sent to the suction side of the high stage compression element 9 via the communication path 55, the communication path 55 is opened. Since the low stage discharge pressure passing therethrough is higher than the pressure in the motor chamber 8 such as the pressure before the compressor starts, a part of the refrigerant gas in the communication path 55 flows out into the motor chamber 8 via the bypass valve device 58. Thus, the intake gas of the high stage compression element 9 starts compression in the state of the pressure drop, and at the same time, it retreats according to the compression chamber pressure of the small vane 39 of the back pressing force by the lubricating oil, and slightly at the second piston 9b. By lowering the sealing accuracy of the compression chamber, the compression load can be made lighter, and a quieter starting operation can be realized.

According to the above embodiment, the two-stage compression mechanism in which the discharge side of the low stage compression element 7 and the suction side of the high stage compression element 9 are connected in series through a communication path 55 is constructed. Compressed gas was discharged to the electric motor chamber 8 in the airtight container 3 accommodating the electric motor 5 therefrom, and at the same time, an oil tank 35 was disposed at the bottom thereof, and between the communication path 55 and the electric motor chamber 8. The bypass passage 57 is formed in the middle of the bypass passage 57. When the pressure in the communication passage 55 is higher than the pressure in the motor chamber 8, only the communication passage 55 to the motor chamber 8 are formed. The bypass valve device 58 is arranged to allow the opening of the valve and the bypass passage 57 communicates with the discharge chamber 51 of the high stage compression element 9 so that the refrigerant gas of the communication path 55 is abnormal. When the pressure rises, a part thereof flows into the discharge chamber 51 of the high stage compression element 9 via the bypass valve device 57 and the high stage pressure By joining the cylinder of the element 9 with the compressed discharge gas to form a normal discharge gas flow discharged to the electric motor chamber 8, it is possible to reduce the compression load by suppressing the abnormal pressure rise of the communication path 55. At the same time, the refrigerant gas discharged from the bypass passage 57 does not diffuse the lubricating oil in the lower lug 35 of the electric motor chamber 8, and prevents the lubricating oil from leaking into the piping system other than the compressor, so that the sliding part durability due to the lack of lubricating oil Can prevent the degradation.

According to the above embodiment, a two-stage compression mechanism in which the discharge side of the low stage compression element 7 and the suction side of the high stage compression element 9 are connected in series via a communication path 55 is constructed. In addition to discharging the compressed gas into the electric motor chamber (8) in the airtight container (3) for accommodating the electric motor (5), the oil tank (35) is arranged at the bottom thereof, and the communication path (55) and the electric motor chamber (8) are discharged. The bypass passage 57 was formed therebetween, and in the middle of the bypass passage 57, when the pressure of the communication passage 55 is higher than the pressure of the motor chamber 8, the communication passage 55 is connected to the motor chamber 8. By arranging the bypass valve device 58 allowing the opening of the furnace, the pressing force for pressing the valve body 58a of the bypass valve device 58 to the valve seat side acts as the coil spring 58b. By suppressing the abnormal pressure rise of the communication path 55, it is possible to reduce the compression load and at the same time the refrigerant in the communication path 55 Even if some pressure pulsation occurs in the air, due to the unnecessary opening of the bypass passage 57, the discharge refrigerant gas from the electric motor chamber 8 is prevented from flowing back into the communication passage 55, thereby stabilizing the two-stage compression operation. Reduction of noise, true seed and high efficiency operation can be continued.

According to the above embodiment, a two-stage compression mechanism in which the discharge side of the low stage compression element 7 and the suction side of the high stage compression element 9 are connected in series via a communication path 55 is constructed. At 9), the compressed gas was discharged to the electric motor chamber 8 in the sealed container 3 accommodating the electric motor 5, and an oil tank 35 was disposed at the bottom thereof, and the communication path 55 and the electric motor chamber 8 were disposed. The bypass passage 57 is formed between the passageways 57 and in the middle of the bypass passage 57, the pressure in the communication passage 55 is higher than the pressure in the motor chamber 8 in the communication passage 55. The bypass valve device 58 is arranged to allow opening only to the valve), and the pressing force for pressing the valve body 58a of the bypass valve device 58 toward the valve seat is acted on by the coil spring 58b. The coil spring 58b increases its pressing force when its temperature rises, and its temperature drops. Since the surface has a shape memory characteristic that reduces the pressing force, the initial stage during cooling starts when the pressing force of the coil spring 58b for pressing the valve body 58a toward the valve seat is small, and the coil spring 58b rises in temperature. Since the pressing force is large, the opening of the bypass passage 57 in the case where the communication path 55 at the initial start of cooling increases abnormally can speed up the opening of the bypass passage, thereby reducing the compression load. It is possible to prevent leakage of the discharged refrigerant gas into the communication path 55 in the chamber 8 and to prevent a decrease in the compression efficiency.

According to the above embodiment, a two stage compression mechanism is constructed in which the discharge side of the low stage compression element 7 and the suction side of the high stage compression element 9 are connected in series through a communication path 55. (9) discharges the compressed gas into the electric motor chamber (8) in the airtight container (3) for accommodating the electric motor (5), and at the same time arranges an oil tank (35) at the bottom thereof, thereby communicating the communication path (55) and the electric motor chamber ( 8) The bypass passage 57 is formed between the motor passages 8 in the communication passage 55 when the pressure of the communication passage 55 is higher than the pressure of the motor chamber 8 in the middle of the bypass passage 57. The bypass valve device 58 for allowing the opening of the bypass valve 58 to be opened is disposed, and the pressure of the discharge chamber 51 of the high stage compression element 9 is applied to the back surface of the valve body 58a of the bypass valve 58. By actuating the pressure of the discharge chamber 51 of the high stage compression element 9 to the back surface of the valve body 58a, thereby pressurizing the valve body 58a to the valve seat side. Initially, starting pressure was dependent only on the coil spring 58b to pressurize the valve body 58a to the valve seat side, and during stable operation, the pressure in the discharge chamber 51 was applied to the pressure force of the coil spring 58b. (2) acts on the rear surface of the cylinder), so that when the communication path 55 abnormally rises at the beginning of operation, the bypass passage 57 can be opened quickly, and the compression load can be reduced quickly. Following this, the compression load reduction can be gradually weakened, so that smooth load control from starting to stable operation can be achieved, thereby improving durability.

In particular, during high compression non-operation, the high-pressure discharge refrigerant gas strongly presses the back surface of the valve body 58a toward the valve seat to further improve the blocking property of the bypass valve device 58, and the communication passage in the discharge chamber 51. By reducing the amount of leakage gas to 55, the compression efficiency decrease by installing the bypass passage 57 can be prevented.

According to the above embodiment, a two-stage compression mechanism in which the discharge side of the low stage compression element 7 and the suction side of the high stage compression element 9 are connected in series through a communication path 55 is constituted. The compressed gas is discharged to the electric motor chamber 8 in the sealed container 3 accommodating the electric motor 5, and an oil tank 35 is arranged at the bottom thereof, and is connected between the communication path 55 and the electric motor chamber 8. The bypass passage 57 was formed. In the middle of the bypass passage 57, when the pressure in the communication passage 55 is higher than the pressure in the motor chamber 8, the opening only from the communication passage 55 to the motor chamber 8 is opened. The discharge chamber 51 of the high stage compression element 9 is disposed on the downstream side of the bypass passage 57 while the bypass valve device 58 for permitting It is possible to reduce the compression load by suppressing the abnormal pressure rise and to increase the pressure when the refrigerant gas in the communication path 55 is bypassed. The sound gradually decreases while the bypass refrigerant gas passes through the discharge chamber 51, so that the sound propagated to the electric motor chamber 8 is reduced, and as a result, noise generation due to the bypass action for reducing the compression load can be suppressed. .

Moreover, in the above embodiment, a two-stage compressor has been described. However, the same operation and effect can be expected in a configuration in which the embodiment drawings are applied to a compressor having three or more compressions.

In the above embodiment, the lubricating oil acting on the high stage discharge gas pressure is collected in the sealed container, but the lubricating oil is collected in the oil separation device on the discharge side installed outside the compressor according to the size of the sealed container or the circumstances of the oil separation ability. And an oil supply passage introduced into the compressor from there.

In addition, in the above embodiment, the refrigerant compressor has been described, but the same effect and effect are generated in the case of a multi-stage gas compressor that compresses other gases (for example, oxygen, nitrogen, helium, air, etc.).

Industrial availability

As is evident from the above embodiment, the present invention constitutes a multistage compression mechanism in which the discharge side of the low stage side compression element and the suction side of the high stage side compression element among the multiple compression elements are connected in series through a sequential communication path, thereby compressing the final stage. Compressed gas was discharged from the urea to the discharge gas discharge space, and an oil tank was disposed at the bottom thereof to form a bypass passage between the communication path and the discharge gas discharge space or the space connected thereto, and in the middle of the bypass passage. When the compression of the gas is higher than the pressure of the exhaust gas discharge space, the bypass valve device is provided to allow the opening of only the communication gas from the communication path to the discharge gas discharge space or the space connected thereto. When gas is compressed and discharged and sent to the suction side of the high-stage compression element through the communication path Since the pressure of the gas passing through the communication path is higher than the pressure of the discharge gas discharge space such as the pressure before starting the compressor or the space therethrough, a part of the gas in the communication path passes through the bypass valve device or the discharge gas discharge space through the bypass valve device. Since the inlet gas of the high-stage compression element flows out and starts compression in a state where the pressure drops, the initial compression load is light, smooth starting, vibration and noise can be reduced.

In addition, the present invention constitutes a multi-stage compression mechanism in which the discharge side of the low-stage compression element and the suction side of the high-stage compression element among the multiple compression elements are connected in series via a sequential communication path to discharge the exhaust gas from the final compression element. At the same time as the compressed gas is discharged into the space, an oil tank is arranged at the bottom, and a bypass passage is formed between the communication passage and the discharge gas discharge space or the space connected thereto, and the pressure of the communication passage is discharged in the middle of the bypass passage. When the gas discharge space pressure is higher than that, the bypass valve device is provided to allow the opening of the communication gas from the communication path to the discharge gas discharge space or the space connected thereto, and is divided into the suction chamber and the compression chamber while advancing and retracting each cylinder of the compression element. Into the vane's rear chamber, lubricant is discharged from the final compression element and separated from the exhaust gas. As the phosphorus is pressurized, the maximum discharge pressure increases with the passage of time after the compressor is started, and each vane that introduces the oil of the oil tank at the bottom of the exhaust gas discharge space into the back of the cylinder divides the cylinder into a suction chamber and a compression chamber. Since the accuracy is gradually increased, the sealing part at the time of starting is made worse, and smooth starting can be performed without raising the compression chamber pressure of the starting time too much, and vibration and noise can be reduced.

When the gas sucked into the low stage compression element is compressed and discharged at the same time as the compressor vibration, and is sent to the suction side of the high stage compression element via the communication path, the low stage discharge pressure passing through the communication path is the pressure before the compressor starts. Since the gas in the communication path is higher than the pressure in the exhaust gas discharge space, such as a part of the gas flows into the exhaust gas discharge space through the bypass valve device, the intake gas of the high-stage compression element starts to compress while the pressure drops. At the same time, the compression load can be made lighter by retreating according to the pressure of the compression chamber of the small vane of the back pressing force by the lubricating oil, and the compression load can be made lighter, and a more quiet starting operation can be realized.

In addition, the present invention constitutes a multi-stage compression mechanism in which the discharge side of the low-stage compression element and the suction side of the high-stage compression element among the multiple compression elements are connected in series through a communication path, and exhaust gas is discharged from the final compression element. At the same time as the discharge of compressed gas into the space, an oil tank was placed at the bottom and a bypass passage was formed between the communication passage and the discharge gas discharge space or the space connected thereto, and the compression of the communication passage discharged the discharge gas during the bypass passage. By placing a bypass valve device to allow the opening of the exhaust gas from the communication path to the discharge gas space or the space connected to it when the pressure is higher than the space pressure, the bypass passage is connected to the discharge chamber of the high stage compression element. When the gas has an abnormal pressure rise, part of the high stage compression element Reduces the compression load by suppressing the abnormal pressure rise in the communication path by forming a normal discharge gas flow into the exit and joining the discharge gas compressed in the cylinder of the high-stage compression element to discharge to the discharge gas discharge space or the space therethrough. At the same time, the gas discharged from the bypass passage does not diffuse the lubricating oil from the bottom of the discharge gas discharge space, and prevents the lubricating oil from leaking from the piping system outside the compressor, thereby reducing the durability of the sliding part due to the lack of lubricating oil. Can be prevented.

In addition, the present invention constitutes the other end compression mechanism in which the discharge side of the low end side compression element and the suction side of the high end side compression element among the multiple compression elements are connected in series through a sequential communication path, and the exhaust gas from the final stage compression element. Compressed gas is discharged into the discharge space and an oil tank is disposed at the bottom thereof, and a bypass passage is formed between the communication passage and the discharge gas discharge space or the space connected thereto, and the compression of the communication passage is discharged in the middle of the bypass passage. When the pressure is higher than the pressure of the gas discharge space, a bypass valve device is provided to allow opening only from the communication path to the discharge gas discharge space or the space connected thereto, and at the same time, pressurizes the pressing force to press the valve of the bypass valve device to the valve seat side. By acting as a device, it is possible to reduce the compression load by reducing abnormal pressure rise in the communication path and at the same time Even if some pressure pulsation occurs in the gas, the exhaust gas is prevented from flowing back to the communication path in the exhaust gas discharge space due to the unnecessary opening of the bypass passage, thereby stabilizing the multistage compression operation to reduce noise and vibration and high efficiency. You can continue driving.

In addition, the present invention comprises a multi-stage compression mechanism in which the discharge side of the low-stage compression element and the suction side of the high-stage compression element among the multiple compression elements are sequentially connected via a communication path, and the exhaust gas from the final compression element. Compressed gas was discharged into the discharge space and an oil tank was disposed at the bottom thereof, and a bypass passage was formed between the communication path and the discharge gas discharge space or the space connected thereto, so that the pressure of the communication path was discharged during the bypass passage. The spring device is provided with a pressurizing valve which pressurizes the valve of the bypass valve device to the valve seat while arranging a bypass valve device allowing opening only from the communication path to the discharge gas discharge space or the space connected thereto when the pressure is higher than the discharge space pressure. The spring device increases its pressing force when its temperature rises, When it is lowered, it has a shape memory characteristic that decreases the pressing force.In the initial stage of cooling, the pressing force of the spring device that presses the valve to the valve seat side is small, and the spring device rises in temperature so that the pressing force is high. When the communication path is abnormally increased in the initial stage, the bypass passage can be quickly opened to reduce the compression load, and during stable operation, it is compressed by supporting the leakage of the discharge gas into the communication path in the exhaust gas discharge space. The fall of efficiency can be prevented.

In addition, the present invention constitutes a multi-stage compression mechanism in which the discharge side of the low-stage compression element and the suction side of the high-stage compression element among the several compression elements are connected in series through a sequential communication path, and the exhaust gas is discharged from the final compression element. Compressed gas was discharged into the space and an oil tank was arranged at the bottom thereof, and a bypass passage was formed between the communication passage and the discharge gas discharge space or the space connected thereto, and the pressure of the communication passage was discharged in the middle of the bypass passage. A bypass valve arrangement is provided to allow the opening of the exhaust passage to or from the communication path only when the gas discharge pressure is higher than the pressure. When the valve was pressed to the valve seat side by actuating the pressure of the space passing through, When the pressurization pressure applied to the lateral side depends only on the spring device, and during stable operation, when the pressure in the exhaust gas discharge space or the space connected thereto is applied to the back of the valve during the stable operation, the communication path abnormally rises at the beginning of startup. It is possible to speed up the opening of the bypass passage quickly and to reduce the compression load and to gradually reduce the compression load by following the maximum discharge pressure increase after the compressor is started. It becomes possible and can improve durability. Particularly during high compression non-operation, the high pressure exhaust gas presses the back of the valve firmly to the valve seat to improve the blocking property of the bypass valve device, thereby reducing the amount of leakage gas from the exhaust gas discharge space or the communication channel to the communication path. Compression efficiency can be prevented by installing a path.

In addition, the present invention constitutes a multi-stage compression mechanism in which the discharge side of the low-stage compression element and the suction side of the high-stage compression element among the several compression elements are connected in series through a sequential communication path, and the exhaust gas discharged from the final compression element. Compressed gas was discharged into the space and an oil tank was disposed at the bottom thereof, and a bypass passage was formed between the communication passage and the discharge gas discharge space or the space connected thereto, and the compression of the communication passage was performed during the bypass passage. A bypass valve arrangement is provided to allow the opening of only the exhaust gas discharge space from the communication path or the space connected thereto when the pressure is higher than the discharge space pressure, and at the same time, a high stage compressed element discharge chamber is immediately downstream of the bypass valve device. According to the arrangement, the abnormal pressure rise in the communication path can be suppressed to reduce the compressive load and at the same time, In the case of bypassing, the expansion sound gradually decays while the bypass gas passes through the discharge chamber, so that the sound of direct propagation to the exhaust gas discharge space is less. As a result, the noise generated by the bypass action for reducing the compression load is reduced. It can be suppressed.

Claims (7)

Compression gas is discharged from the final stage compression element to the discharge gas discharge space by constructing a multistage compression mechanism in which the discharge side of the low stage compression element and the suction side of the high stage compression element are connected in series through a sequential communication path. At the same time as the discharge, an oil tank was disposed at the bottom thereof, and a bypass passage was formed between the middle of the communication passage and the discharge gas discharge space or the space therebetween. A multi-stage gas compressor with a bypass valve device, characterized in that allowing opening only from the communication path to the exhaust gas discharge space or the space therethrough when higher. The vane is pressurized by introducing a lubricating oil discharged from the final stage compression element and separated from the discharge gas into the rear chamber of the vane which divides each cylinder of the compression element into the suction chamber and the compression chamber while advancing and retracting each cylinder of the compression element. A vane-type rotary multistage gas compressor having a bypass valve device. 2. The multistage gas compressor having a bypass valve device according to claim 1, wherein the bypass passage communicates with the discharge chamber of the high stage compression element. The multi-stage gas compression provided with a bypass valve device according to claim 1, wherein a pressing force for pressing the valve of the bypass valve device to the valve seat side is acted on as a spring device. 5. The bypass device according to claim 4, wherein the spring device has a shape memory characteristic that increases the pressing force when its own temperature rises and decreases the pressing force when its own temperature decreases. Multi-stage gas compressor. The bypass valve device according to claim 1, wherein a pressure is applied to the valve seat side by applying a pressure of a discharge gas discharge space in the sealed container or a space connected thereto to the rear surface of the valve of the bypass valve device. Multi-stage gas compressor. The multi-stage gas compressor provided with a bypass valve device according to claim 1, wherein a discharge chamber of a high stage compression element is disposed immediately downstream of the bypass valve device of the bypass passage.