KR100557373B1 - Closed and Rotary Type Compressor - Google Patents

Abstract

Intake heating loss or discharge flow rate due to internal leakage due to insufficient flow in the cylinder in the low speed region, poor lubrication of the sliding part, and excessive oil supply into the cylinder in the high speed region It aims at preventing an increase.

A rotary compressor comprising a motor controlled at a different rotational speed, having a suction pressure in a sealed container, and a front portion into which a lubricating oil supplied to an inner surface of a roller portion flows, and a front portion and a suction side reciprocate with each other. An end plate for closing the roller in the cylinder is provided for the rear portion which temporarily holds the negative lubricant.

Description

Hermetic Rotary Compressor {Closed and Rotary Type Compressor}

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a longitudinal sectional view of a horizontally mounted rocking piston compressor according to a first embodiment of the present invention.

2 is a cross-sectional view taken along line A-A of FIG.

3 is an explanatory view of the operation of the compression element of FIG.

4 is an explanatory view of essential parts of a swinging piston compressor according to the first embodiment of the present invention;

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

Fig. 6 is an explanatory diagram of a main part of a swinging piston type compressor according to a second embodiment of the present invention.

FIG. 7 is a cross-sectional view taken along the line C-C in FIG.

8 is an explanatory diagram of a main part of a swinging piston type compressor according to a third embodiment of the present invention;

9 is a cross-sectional view taken along the line C-C in FIG.

Figure 10 is an enlarged view around the recess in Figure 9;

Fig. 11 is an explanatory diagram of a main part of a swinging piston type compressor according to a fourth embodiment of the present invention.

12 is an explanatory diagram of a main part of a swinging piston type compressor according to a fifth embodiment of the present invention;

Fig. 13 is a configuration diagram of a refrigeration cycle of a refrigeration apparatus according to the sixth embodiment of the present invention.

Fig. 14 is a longitudinal sectional view of the horizontal mounting rocking piston type two stage compressor according to the seventh embodiment of the present invention.

Fig. 15 is an enlarged view of the oil supply mechanism of the horizontally mounted swing piston type two-stage compressor shown in Fig. 14;

<Explanation of symbols for the main parts of the drawings>

1 cylinder 1a cylindrical inner peripheral surface

1b: cylindrical hole 1c: hole

1d: suction port 2: main bearing

2a: bearing part 3: secondary bearing

3a: bearing part 3b: discharge port

3c: discharge chamber 4: drive shaft

4a: eccentric 4b: gas bleed hole

4c: gas discharge hole 4e: communication hole

5: rotor 6: sealed container

7: stator 8: rocking piston

8a: roller portion 8b: vane portion

8c: notch 8d: annular groove

9: no activity 10: compression chamber

11: suction chamber 12: suction pipe

13: suction passage 14: discharge cover

15 discharge pipe 16 lubricating oil

17: suction fluid diode 18: discharge fluid diode

19: refueling pipe 20: spiral groove

21: oil pocket 22, 23: recess

24 condenser 24a fan for the condenser

25 expansion valve 26 evaporator

26a: Fan for evaporator 27: Hermetic rotary compressor

The present invention relates to hermetically sealed rotary accumulators and refrigeration or air conditioning systems and heat pump apparatuses, in particular to devices with hermetically sealed rotary compressors and refrigeration systems with high performance and high reliability under a wide range of rotational speed conditions.

BACKGROUND ART Rotary compressors, which are rotary compressors used in conventional refrigeration or air conditioning systems, are housed in a hermetically sealed container with a power element having a stator and a rotor, and a compression element driven by the power element. The compression element rotates eccentrically in the cylinder by the rotation of the drive shaft which is rotationally fitted to the eccentric part of the drive shaft by the rotation of the drive shaft which transmits a rotational force from the transmission element, and compresses the refrigerant which is a working fluid.

In other words, in the compression stroke, the refrigerant gas sucked into the suction chamber from the suction pipe is compressed from the compression chamber by dividing the inside of the cylinder into the suction chamber and the compression chamber by vanes compressed by the rollers. The compressed refrigerant gas is discharged into the sealed container and discharged to the external refrigerant cycle from the discharge pipe.

In such a rotary compressor, in order to make the back pressure of the vane which compresses a roller into high pressure, the inside of a sealed container is made into discharge pressure in many cases. The supply of the lubricating oil into the cylinder is usually supplied into the cylinder from the lubricating oil supply portion provided inside the roller via the roller and the end plate. The end plate is a plate-like member disposed opposite to the end of the roller having a cylindrical shape, and forms a suction chamber or a compression chamber in cooperation with the cylinder and the roller.

When back pressure is applied to the vanes when the sealed container is discharged, if the above-described lubricating oil supply mechanism is used, the lubricating oil leaked by the differential pressure into the suction chamber may be excessive. When the supply of lubricating oil into the suction chamber becomes excessive, problems of deterioration of the compressor due to heating loss or the like and deterioration of reliability due to an increase in the coil temperature of the transmission element occur.

In the case of intermittent operation of the compressor, there is also a problem of intermittent loss in which high temperature and high pressure gas in the sealed container flows back into the evaporator when the compressor is stopped, thereby raising the temperature of the evaporator, thereby degrading the performance of the refrigeration and air conditioning system.

In addition, natural refrigerants are promising as future refrigerants from the viewpoint of preventing global warming. However, natural refrigerants have a small global warming coefficient but are flammable (for example, isobutane). When using this flammable refrigerant | coolant, it is highly likely that the sealing amount (refrigerant use amount) to an apparatus is limited from a stability standpoint.

In general, the higher the atmospheric pressure in the hermetic container, the greater the amount of refrigerant dissolved in the lubricating oil stored under the hermetic container. For this reason, the amount of refrigerant encapsulated into the device increases as much as the amount of dissolved refrigerant is compensated for.

Accordingly, there is a problem that it is difficult to apply a natural refrigerant having a flammability since the compressor of the type having the discharge pressure in the hermetic container is a direction in which the refrigerant filling amount into the device is increased.

In view of the above problems, there is a rotary compressor disclosed in Japanese Patent Application Laid-Open No. 07-72547 as a low pressure vessel-type rotary compressor having a pressure inside the sealed container at the same pressure (suction pressure) as the low pressure side of the compressor.

Here, in the inner surface (cylinder side) of the bearing plate of the rotary compressor disclosed herein, a section in which the rolling piston (roller) is in full communication with the low pressure chamber in the cylinder while one rotation of the rolling piston (roller), the section occluded in the end plate of the rolling piston And a large oil storage concave portion having a position consisting of three sections in a section communicating with the inside of the rolling piston in full contact. According to this configuration, the lubricant having a flow rate proportional to the volume of the concave portion can always supply a certain amount of lubricant to the low pressure chamber per rotation of the rotating shaft regardless of the pressure condition between the rotation of the rotating shaft accompanying the operation of the compressor. It is described that it is possible to suppress a large amount of lubricating oil flowing out of the device at the start and the like.

The oil supplied to the oil storage recess is fed to the following mechanism. First, the oil lubricating the active surface of the eccentric portion of the drive shaft is supplied to the inside of the rolling piston, and then the lubricating oil supplied to the inside of the rolling piston is pushed in the eccentric direction by the centrifugal action of the rotating shaft to form an oil film inside the rolling piston. This oil film thickness depends on the oil supply amount inside the rolling piston. Therefore, the oil film thickness becomes thinner on the condition that the oil supply amount becomes small, that is, the condition that the motor rotation speed in the apparatus becomes low. In particular, when the rotary compressor is of the horizontal installation type, it is possible to consider that the area covering the opening of the oil storage recess of the lubricating oil is small, and the volumetric efficiency of blowing the lubricating oil of the oil storage recess is lowered.

As mentioned above, in the said well-known example, the volumetric efficiency of the oil storage recessed part which blows in lubricating oil falls only as much as the low speed condition of the motor which becomes thinner. In addition, if the volume of the oil storage recess is set to a volume capable of supplying the flow rate required for internal lubrication under the low speed condition of the motor, the flow rate of the oil storage recess is increased under the high speed condition of the motor rotation speed, which becomes a condition that the oil film becomes thick. do. As a result, the amount of oil supply into the cylinder becomes excessive, there is a problem that the intake heating loss or the flow rate discharged to the outside of the compressor increases, resulting in a decrease in compressor performance and cycle performance.

In addition, if the volume of the oil storage recess is set so that the oil discharge amount does not decrease the cycle performance under the high speed condition of the motor, the flow rate to be blown into the oil storage recess is insufficient at low speed condition where the oil film becomes thin, and the internal leakage and vanes Problems with poor lubrication between rolling pistons will occur.

An object of the present invention is to provide a certain amount of oil per one revolution to the suction chamber even when the oil supply amount inside the roller portion is changed due to the variation of the rotational speed of the hermetic rotary compressor, even at low speed or high speed. It is.

In order to achieve the above object, the hermetic rotary compressor of the present invention operates by a drive shaft having a stator and a rotor in an airtight container, an eccentric portion for transmitting rotation by the drive element, and rotation of the eccentric portion of the drive shaft. A compression element for compressing fluid, the compression element having a cylindrical inner circumferential surface with open ends, a roller fitted into an eccentric portion of a drive shaft in the cylinder, and a suction chamber into the cylinder with an eccentric motion of the roller; A vane partitioned into the compression chamber, an end plate to block the opening of the cylinder, a lubrication mechanism for supplying lubricating oil into the roller via the drive shaft, a front part for introducing the lubricating oil supplied into the roller, and a space inside the roller; A lubricating oil supply mechanism having a rear portion communicating with the suction chambers with each other to hold the lubricating oil from the front portion; Ratio is accomplished by.

<Example>

EMBODIMENT OF THE INVENTION Hereinafter, each embodiment of this invention is described using drawing. In addition, in embodiment below, a part of structure common to 1st embodiment is abbreviate | omitted, and the overlapping description is abbreviate | omitted.

First, the first embodiment of the present invention will be described with reference to FIGS. The hermetic rotary compressor of this embodiment arranges the drive shaft 4 which connects a transmission element, a compression element, and both in the hermetic container 6. In the present embodiment, the inside of the sealed container 6 is a suction pressure lower than the discharge pressure.

The transmission element has a stator 7 and a rotor 5. The compression element has a compression mechanism and an oil supply mechanism. The compression mechanism includes a cylinder (1) having a cylindrical inner circumferential surface (1a), a swinging piston (8) rotatably disposed in the cylinder (1), and a main bearing (2) for closing openings at both ends of the cylinder (1). And the secondary bearing 3. The drive shaft 4 is fixed to the rotor 5 of the transmission element and transmits a driving force to the compression element. As the eccentric portion 4a of the drive shaft 4 is eccentrically rotated, the swinging piston 8 is eccentrically rotated inside the cylinder 1.

The oil supply mechanism will be described later, but with the change in the volume of the hole portion 1c of the cylinder 1 as the end of the vane portion 8b enters and exits, the lubricating oil introduced from the suction fluid diode 17 is discharged to the fluid diode 18. It is conveyed to the refueling pipe 19 through. The lubricating oil supplied through the oil supply pipe 19 enters into the sub bearing 3 and is supplied into each bearing by a spiral groove 20 provided on the surface of the drive shaft 4.

The structure of a compression mechanism is explained in full detail. The main bearing 2 and the sub bearing 3 close at least the openings at both ends of the cylindrical inner circumferential surface 1a of the cylinder 1. In the present embodiment, the cylinder 1 is fixed to the main bearing 2. The main bearing 2 and the sub bearing 3 are provided with bearing parts 2a and 3a in the center of the part corresponding to the cylindrical inner peripheral surface 1a of the cylinder 1, respectively, and the drive shaft 4 is rotatable. I support it. In addition, the main bearing 2 and the sub bearing 3 have a cylinder (so that the rotation axis (parts other than the eccentric portion 4a) of the drive shaft 4 coincides with the central axis of the cylindrical inner circumferential surface 1a of the cylinder 1). It is fixed to 1). The outer circumferential portion of the main bearing 2 is fixed to the sealed container 6, and the stator 7 of the transmission element is fixed to the sealed container 6.

The eccentric part 4a is provided in the drive shaft 4 in the part located in the cylindrical inner peripheral surface 1a of the cylinder 1. That is, the cylindrical inner peripheral surface of the roller part 8a of the rocking piston 8 is rotatably inserted in the cylindrical outer peripheral surface of this eccentric part 4a. Each part dimension is determined so that the space | interval between the cylindrical outer peripheral surface of the roller part 8a and the cylindrical inner peripheral surface 1a of the cylinder 1 may become small.

Moreover, the vane part 8b is provided in the cylindrical outer peripheral surface of the roller part 8a. On the outer side of the cylindrical inner peripheral surface 1a of the cylinder 1, the cylindrical hole part 1b which has a central axis parallel to the central axis of the cylindrical inner peripheral surface 1a is provided. The cylinder 1 center side of the cylindrical hole 1b and the opposite side thereof communicate with the cylindrical inner peripheral surface 1a of the cylinder 1 and the other hole 1c provided outside the cylindrical hole 1b, respectively. . Although the vane part 8b is inserted in the cylindrical hole part 1b and the hole part 1c, it can slide between the vane part 8b and the cylindrical hole part 1b in the flat part of the vane part 8b. An active member 9 having a cylindrical surface portion in sliding contact with the cylindrical surface portion of the cylindrical hole portion 1b and the cylindrical surface portion in contact with each other is assembled by fitting the vane portion 8b. As a result, the vane 8a performs the forward and backward movement toward the central axis of the cylindrical hole 1b and the swinging motion around the central axis. The tip portion of the vane portion 8b moves at the center of the hole portion 1c and does not come out of the cylindrical hole portion 1b and interfere with the cylinder 10.

By having the above structure, when the drive shaft 4 rotates by the transmission element, the oscillation piston 8 will perform the idle movement accompanying oscillation in the cylinder 1 with the eccentric part 4a.

3 shows the motion of the swinging piston 8 when the drive shaft 4 is rotated by 60 degrees. The roller part 8a accompanies the rotational motion of the eccentric 4a, and the center of it performs an orbital motion. The vane 8b is usually directed toward the central axis of the cylindrical hole 1b, and oscillates by a slight angle around the central axis of the eccentric 4a. Sealing of the gap between the vane portion 8b and the cylindrical hole portion 1b during the movement of the vane portion 8b, that is, the retreat movement toward the central axis of the cylindrical hole portion 1b and the swinging motion around the central axis. The retaining member 9 is inserted by sealing between the vane portion 8b and the cylindrical hole portion 1b.

Therefore, by combining with the cylinder 1, the oscillating piston 8, the main bearing 2, the sub bearing 3, and the active member 9, the compression chamber 10 (Fig. 3 oblique part) and the suction space, which are sealed spaces, are sealed. The phosphorus suction chamber 11 is comprised. With the rotation of the drive shaft 4 by the transmission element, the increase and decrease of the volume is repeated as shown in FIG. In Fig. 3, the compression chamber 10 is formed in the whole of Figs. 3A to 3F.

According to this configuration, the refrigerant gas as the working fluid is compressed as described later. First, the refrigerant gas is sucked into the sealed container 6 from the suction pipe 12 attached to the sealed container 6, passes through the suction passage 13, and is sucked into the suction chamber 11. [The suction chamber 11 is in a state where the suction port 1d is blocked by the roller portion 8a as shown in (a) θ = 0 degrees in FIG. 3 (b) θ = 60 degrees, f) Beyond θ = 300 degrees (a) Exhaust port 3b remains closed as θ = 0 degrees.] The refrigerant gas is compressed at the same time as the volume of the compression chamber 10 decreases. The refrigerant gas discharged from the discharge port 3b provided in the sub bearing 3 is discharged to the discharge chamber 3c provided by the sub bearing 3 and the discharge gas 14. Then, the compressed refrigerant gas is discharged out of the sealed container 6 from the discharge pipe 15 passing through the sealed container 6.

As described above, in the present embodiment, in particular, the refrigerant gas that has penetrated the suction pipe 12 is first sucked into the sealed container, and the inside of the sealed container 6 becomes the suction pressure. At this time, the refrigerant gas compressed in the compression chamber 10 is discharged out of the sealed container 6 through the discharge pipe 15 via the discharge chamber 3c without being directly discharged into the sealed container 6.

By setting the inside of the closed container 6 to the suction pressure, there are the following advantages.

(1) Since the heating of the electric element by the compressed high-temperature refrigerant gas is reduced and cooled by the low-temperature refrigerant gas, the temperatures of the rotor 5 and the stator 7 are lowered, and the motor efficiency is improved, thereby improving performance. Improvement can be aimed at.

(2) Since the inside of the roller part 8a becomes a suction pressure, supply of excess oil by the differential pressure from the inner surface of the roller part 8a to the suction chamber 11 is eliminated, and the performance of a compressor can be improved.

(3) In refrigerants such as fron compatible with lubricating oil, the compression is low, so that the proportion of refrigerant gas dissolved in the oil is reduced, and foaming of the refrigerant gas in the bearing or the like is unlikely to occur, thereby improving reliability. In addition, in the natural refrigerants (isobutane, propane, etc.) which have potential flammability as new refrigerants in the future, the amount of refrigerant used is small, and stability can be improved.

(4) The internal pressure of the airtight container 6 can be reduced, and thickness and weight can be reduced.

Moreover, the rocking piston type compressor shown in this embodiment is easy to apply to the structure which made suction pressure into the sealed container. Because the roller and the vane are integrated, the vane is pushed by the roller like a rotary compressor having the roller and the vane as separate members, so that it is not necessary to apply high pressure back pressure to the vane.

Next, the oil supply mechanism of a compression mechanism part is explained in full detail. In Fig. 1, the vane 8b moves forward and backward in the hole 1c as the drive shaft 4 rotates, and the volume of the hole 1c changes. The lubricating oil 16 stored at the bottom of the sealed container 6 by the pumping action according to this volume change (hereinafter referred to as vane oil feed pump) is sucked from the suction fluid diode 17, and the discharge fluid diode 18, Through the oil supply pipe 19, it is pulled up to the drive shaft 4. In addition, the pulled up lubricant 16 lubricates the sub bearing 3, the eccentric portion 4a, and the main bearing 2 through the spiral groove 20 provided on the outer circumference of the drive shaft 4, and then closes the sealed container 6 Come back inside.

The lubricating oil 16 lubricating the eccentric portion 4a flows out to the inner surface side of the roller portion 8a. For example, even when the refrigerant gas is foamed from the lubricating oil 16 through the spiral groove 20, the foamed refrigerant gas is a gas extraction hole opened in the outer peripheral surface of the eccentric portion 4a opposite to the inner surface of the roller portion 8a. It discharges from the gas discharge hole 4c provided in the drive shaft 4 from 4b.

In addition, the high-pressure refrigerant gas leaking into the roller portion 8a from the compression chamber 10 has an opening on a surface of the eccentric portion 4a opposite the main bearing 2 and the sub bearing 3 to discharge the gas. Through the communication hole 4e which communicates with the hole 4c, it is discharged | emitted to the airtight container 6 by the gas discharge hole 4c provided in the drive shaft 4 inside.

Here, the structure in which the lubricating oil 16 supplied on the inner surface of the roller part 8a is stably supplied into the cylinder 1 is demonstrated. In FIG. 3, the notch part 8c opened inside the roller part 8a is provided in the end surface of the roller part 8a. The plane of the end plate is recessed at the position where the cutout part 8c of the end face of the roller part 8a and the suction chamber mutually communicate with the space inside the roller part 8a on the end plate of the sub bearing 3 mutually. The oil pocket 21 which is a fine recess is provided. The position on the end plate of the notch 8c of the end face of the roller part 8a and the sub bearing 3 which mutually reciprocates the suction chamber is not the discharge port 3d side in the cylinder 1, but the suction port 1d. Side. That is, the position on the end plate of the sub bearing 3 is the position which communicates with the space inside the roller part 8a and the suction chamber 11.

The lubricating oil 16 supplied on the inner surface of the roller portion 8a is led to a blowing portion, for example, a notch 8c, and is held at a position opposite to the notch 8c, for example, a sub-bearing ( It is supplied to the oil pocket 21 of 3). Thereafter, when the oil pocket 21 is opened into the suction chamber 11, the lubricating oil 16 in the oil pocket 21 is supplied to the suction chamber 11.

4 and 5 will be described in detail. The lubricating oil 16 supplied between the roller portion 8a and the eccentric portion 4a of the drive shaft 4 not only covers the inner surface of the roller portion 8a, but also the surface on which the eccentric portion 4a faces the sub bearing. The lubricant 16 is also accumulated by centrifugal action accompanying the rotation of the drive shaft 4. The cutout portion 8c guides the collected lubricating oil 16 to the oil pocket 21. The state in which the cutout part 8c covers the oil pocket 21 changes with the range of the cutout part 8c.

With the above configuration, since the oil pocket 21 is supplied with the lubricating oil 16 by communicating with the notch 8c provided on the end face of the roller portion 8a, the lubricating oil 16 supplied to the inner circumference of the roller portion 8a is provided. Even if the flow rate is small, the oil pocket 21 is entirely covered by the lubricating oil 16 that is collected and guided to the cutout portion 8c that reaches the front part thereof, so that the lubricating oil 16 is smoothly blown into the oil pocket 21. Thus, the volumetric efficiency at which the oil pocket 21 blows in lubricating oil increases. As a result, even when the flow rate in the roller portion 80 is changed by the rotational speed, a certain amount of lubricant oil can be supplied to the absorption chamber per revolution. That is, it is possible to prevent internal leakage due to insufficient flow rate in the cylinder 1 in the low speed region, poor lubrication of the active member and the cylindrical hole member, and increase intake air heating loss or discharge flow rate due to excessive supply amount into the suction chamber in the high speed region. It is possible to provide a hermetic rotary compressor having high performance and high reliability over a wide range of rotation speed conditions.

The notch 8c communicates with the oil pocket 21 when the pressure in the compression chamber is not rising (almost suction pressure), so that the sealability of the end face of the roller 8a is not deteriorated.

Next, a second embodiment of the present invention will be described with reference to FIGS. 6 and 7. In this embodiment, the corner part of the surface which opposes the eccentric part 4a which is the end surface of the roller part 8a is recessed over the perimeter, and the step-shaped annular groove 8d is provided. The annular groove 8d reduces the contact area with respect to the eccentric part 4a of the roller part 8a, and has the effect | action which reduces contact resistance. As shown in Fig. 7, the contact resistance, for example, the annular groove 8d, is provided not only on the side of the sub bearing 3 side of the roller portion 8a but also on the main bearing 2 side. Decreases.

The lubricating oil 16 supplied to the inner surface of the roller portion 8a by the annular groove 8d is guided and collected in the eccentric direction in the annular groove 8d according to the centrifugal action accompanying the rotation of the drive shaft 4. The oil pocket 21 provided on the end plate of the sub bearing 3 and reciprocated between the annular groove 8d and the suction chamber 11 is led to the annular groove 8d when it communicates with the annular groove 8d. The lubricating oil 16 is supplied to the oil pocket 21. After that, when the oil pump 21 is opened into the suction chamber 11, the lubricating oil 16 in the oil pocket 21 is supplied to the suction chamber 11.

With the above structure, even if the flow rate of the lubricating oil 16 supplied to the inner periphery of the roller part 8a is small, the oil pocket 21 collects in the cutout part 8c which touches the front part, and is full-faced by the lubricating oil 16 guided. The volume efficiency at which the oil pocket 21 blows in the lubricating oil is increased by being covered with. Moreover, since the annular groove 8d is provided in the both sides of the end surface of the roller part 8a, and the contact area with the main and sub bearing end surfaces is made small, the thickness of the cylindrical part of the roller part 8a becomes thick ( For example, in the case of the same cylindrical shape in which the inner and outer diameters of the roller portion and the eccentric portion of the drive shaft and the eccentricity are changed to reduce the compression volume of the compressor), the same effect as that of the first embodiment can be obtained. The sliding loss of the end surface of the roller part 8a can be reduced.

Next, a third embodiment of the present invention will be described with reference to Figs. In this embodiment, the recessed part 22 is opened in the position which opens inside the roller part 8a on the end plate of the sub bearing 3, and becomes a part of the suction chamber with the eccentric motion of the roller part 8a. Install it. The recess 22 has a shape in which the depth h decreases from the outside in the radial direction of the cylinder 1 toward the center direction as seen from the cross section (see FIG. 9) of the sub bearing 3.

By providing such a recessed part 22, the lubricating oil 16 supplied in the roller part 8a inside can be made to the inside of the roller part 8a on the cylinder 1 side end surface of the sub bearing 3, and the suction chamber 11. When the concave portion 22 provided at positions reciprocating with each other communicates with the inside of the roller portion 8a, it is supplied to the concave portion 22. After that, when the recessed part 22 opens in the suction chamber 11, the lubricating oil 16 in the recessed part 22 is supplied to the suction chamber 11.

Here, the recessed part 22 is provided with the oil storage part whose depth h changes with respect to the front part into which the lubricating oil 16 enters. The thickness of the oil film in the roller portion 8a becomes thick and the depth h becomes thin. That is, the thickness h decreases in the direction in which the thickness of the lubricating oil 16 in the roller portion 8a gathered by the centrifugal action of the roller portion 8a becomes thicker. As a result, when the flow rate in the roller 8a increases and the oil film thickness becomes thick, the change in the flow rate supplied to the recess 22 can be made smaller than the recess in which the depth h does not change.

The action of this oil reservoir is that the inner surface of the roller portion 8a and the bottom portion of the recess 22 (surface outside in the radial direction of the cylinder 1 in Fig. 9) are in the radial direction of the cylinder 1. The location is almost the same location. The shape of the end face of the oil storage portion (the portion recessed from the end plate surface of the sub-bearing portion 3), which becomes the rear portion, is larger than the opening portion, which is the front portion of the recess portion 22, so that the opening portion is largely advantageous for oil injection. The oil reservoir may be installed in a volume corresponding to the thickness of the oil film. In the concave portion having a narrow opening and having a large depth h, the amount of lubricant remaining in the concave portion increases, and the original object cannot be achieved. Therefore, by changing the volume of the oil storage part in the film thickness direction of the lubricating oil with respect to the opening as in the present embodiment, the cycle performance is reduced due to the intake heating loss due to the excessive amount of oil supply to the suction chamber in the high speed region or the increase in the discharged flow rate. Can be prevented.

By setting the volume of the recess 22 to the minimum required oil supply amount for internal lubrication of the low speed region, the internal leak caused by the lack of flow rate in the suction chamber 11 in the low speed region or the active member 9 and the cylindrical hole Poor lubrication with the part 1b can be avoided.

As mentioned above, the hermetic compressor to which this embodiment is applied can improve reliability with high performance in a wide range of rotational speed conditions.

The concave portion 22 described above has a shape in which the cross-sectional area is changed in the depth direction, but if the cross-sectional area is changed in the direction perpendicular to the other depths, the oil film becomes thick and the increase rate of the flow rate supplied to the concave portion is small. The same effect can be obtained.

Next, a fourth embodiment of the present invention will be described with reference to FIG. In Fig. 11, the concave portion 23 having an elongated shape in the inner circumferential direction of the roller portion 8a at a position on the end plate of the sub bearing 3 that mutually reciprocates the inside of the roller portion 8a and the suction chamber 11. Is installed.

The lubricating oil 16 supplied inside the roller 8a is supplied to the recess 23. Then, when the front part of the recessed part 23 is opened to the suction chamber 11, the lubricating oil 16 in the recessed part 23 is supplied to the suction chamber 11.

The width b of the front portion, which is the opening of the recess 23, is equal to or less than the thickness of the oil film of the lubricating oil collected in the roller 8a in the low speed region which is equal to or lower than the rotation speed in the rated operation of the hermetic compressor. The width b optimally sets the volume of the recess 23 by appropriately setting the angle α with respect to the center of the eccentric portion 4a.

Since the width b of the opening portion of the recess 23 is equal to or less than the thickness of the oil film in the low speed region of the hermetic compressor, even if the electric motor of the compressor rotates at a low speed, the recess 23 is entirely in contact with the lubricating oil 16. It is covered and the volumetric efficiency which blows in the lubricating oil of the recessed part 23 improves. As a result, even when the flow rate in the roller portion 8a changes depending on the rotational speed, the refrigerant gas leaks inside the cylinder due to insufficient flow rate in the cylinder 1 in the low speed region, or lubrication failure between the active member and the cylindrical hole portion. It is possible to prevent this.

Moreover, the front part opening part which injects a fixed quantity of lubricating oil per revolution in accordance with rotation of the compressor at low speed area | region is provided, and the front part becomes a flow path resistance at the rotational speed of a high speed area | region, It is possible to prevent heat loss or increase in the amount of lubricating oil discharged. Therefore, the hermetic rotary compressor to which the present embodiment is applied can obtain high reliability at high performance in a wide range of rotational speed conditions.

Next, a fifth embodiment of the present invention will be described with reference to FIG. In this embodiment, the oil pocket 21 which becomes an oil storage part is provided in the position on the end plate of the sub bearing 3 which mutually reciprocates inside the roller part 8a and the suction chamber 11, In the front part, the eccentric part 4a is located in the space | interval (delta) at the side of the sub bearing 3, and has a front supply part which consists of the eccentric part 4a and the roller 8a.

The lubricating oil 16 supplied into the roller portion 8a is separated from the sub bearing 3 by the eccentric portion 4a and the roller when the oil pocket 21 communicates with the roller portion 8a. It is supplied to the oil pocket 21 from the front supply part by the part 8a. When the oil pocket 21 is opened into the suction chamber 11, the lubricating oil 16 in the oil pocket 21 is supplied to the suction chamber 11.

The position of the surface of the eccentric portion 4a opposite the sub bearing 3 is located at the oil pump 21 side with respect to the height center line of the roller portion 8a. For example, the space δ between the eccentric portion 4a and the sub bearing 3 and the depth h of the oil pump 21 are made substantially equal.

Since the volume of the space of the oil pump 21 side inside the roller part 8a becomes small, and the oil surface of the lubricating oil supplied inward of the roller part 8a becomes high toward the center of the eccentric part 4a, the roller part 8a The oil pocket 21 is covered with the lubricating oil 16 even if the lubricating oil 16 on the side of the oil pocket 21 is supplied little by little. Therefore, the volumetric efficiency which blows in the lubricating oil of the oil pocket 21 improves.

As a result, even when the flow rate in the roller part 8a is changed by rotation speed, a fixed amount of lubricating oil can be supplied to a suction chamber per one revolution. In other words, when the electric motor of the hermetic compressor rotates in the low speed region, the flow rate shortage in the cylinder 1 is alleviated, and the leakage of the refrigerant gas compressed inside the cylinder 1 and the lubrication member and the poor lubrication of the cylindrical hole can be prevented. Can be. In addition, by absorbing the excessive amount of supply to the suction chamber when operating in the high speed region, it is possible to prevent intake heating loss or increase in the amount of lubricating oil discharged into the suction chamber and the compression chamber. Therefore, the hermetic rotary compressor to which the present embodiment is applied can obtain high reliability at high performance in a wide range of rotational speed conditions.

In the above embodiment, although the oil pocket 21, the recessed part 22, and the recessed part 23 were provided in the end surface of the sub bearing 3 in the 1st cylinder type compressor, the main bearing 2 was carried out. The same effect can be obtained even if it is installed in the side. Moreover, it is easy to apply by providing a structure common to the 2nd cylinder type hermetic rotary compressor.

Next, a sixth embodiment of the present invention will be described with reference to FIG. This cycle is a refrigeration (cooling) cycle. By starting the hermetic rotary compressor 27 to which the embodiment of the present invention is applied, the compressed high-temperature, high-pressure working gas (refrigerant gas) flows into the condenser 24 from the discharge pipe 15 as indicated by the solid arrows. The heat is liquefied by the blowing action of the condenser fan 24a. The liquefied refrigerant is throttled by the expansion valve 25, is adiabaticly expanded, and becomes low temperature and low pressure. The low temperature, low pressure liquid refrigerant is absorbed by heat from the air supplied from the evaporator 26 to the evaporator fan 26a, gasified, and then sucked into the hermetic rotary compressor 27 via the suction pipe 12. .

Here, since the refrigeration system shown in FIG. 13 is equipped with the hermetic rotary compressor which applied one Embodiment of this invention, the refrigeration system excellent in energy efficiency can be obtained over the whole operation range. It describes in detail below.

In Fig. 13, the speed control circuit 50 determines the temperature targeted by the refrigeration system with respect to the temperature detected by the temperature sensor 51, and the rotational temperature of the electric motor provided in the compressor 27 according to the target temperature. To control. When this refrigeration system is applied to refrigeration apparatuses, such as a refrigerator, the temperature sensor 51 installs in the place which can detect the temperature in the refrigerator which you want to detect temperature. Moreover, when this refrigeration system is applied to air conditioners, such as an air conditioner, it is installed next to the heat exchanger arrange | positioned indoors. In the case of the air conditioner, it is also effective to install a temperature sensor in the system, and the speed control circuit 50 controls the rotational speed of the motor by adding the output value of the temperature sensor. In addition, when this refrigeration system is applied to a hot water supply device, a temperature sensor is installed in order to measure the temperature of the water heated by heat exchange.

The temperature control circuit 50 controls the rotational speed of the electric motor of the compressor 27 of the system in order to control the system to the target temperature of the refrigeration system. In the case of controlling the rotational speed of the compressor in order to increase the energy efficiency of the system, the compressor needs to ensure that the efficiency does not decrease with respect to other rotational speeds.

By using the hermetic rotary compressor 27 according to the embodiment of the present invention as a refrigeration system as a component, even if the rotational speed is changed and the amount of lubricating oil supplied to the inside of the roller portion is changed, a certain amount of oil is always sucked in one revolution. Can be supplied as a thread.

Under conditions that do not require the capacity for the target temperature, it is not necessary to rotate the motor (motor) of the compressor at high speed, and the refrigeration system performs control to rotate the compressor at low speed. In this case, the hermetic rotary compressor to which the embodiment of the present invention is applied does not cause internal leakage due to lack of flow rate in the cylinder in the low speed region or poor lubrication of the active member and the cylindrical hole.

In addition, under the condition that the capacity is required for the target temperature, it is necessary to rotate the motor of the compressor at high speed, and the refrigeration system performs control to rotate the compressor at high speed. In this case, the hermetic rotary compressor to which the embodiment of the present invention is applied can prevent intake heating loss or increase in discharge flow rate due to excessive oil supply amount into the cylinder in the high speed region.

In particular, in the hermetic rotary compressor to which the embodiment of the present invention is applied, since the inside of the hermetic container 6 is set to the discharge pressure or less, the amount of the high-temperature and high-pressure refrigerant flowing into the evaporator during the intermittent operation can be reduced, and Energy loss can be reduced.

Here, even if the embodiment is appropriately modified according to the refrigerating system or the air conditioning system, it is obvious that it is within the range of the embodiment of the present invention. In addition, although demonstrated using the single compressor, embodiment of this invention is applicable also to a two stage compressor. An example thereof is described in detail below.

Next, a seventh embodiment of the present invention will be described with reference to Figs. Here, the same reference numerals as in Figs. 1 to 13 are the same parts and have the same function.

14 and 15, the compression element 28 has a low pressure compression element 28a and a high pressure compression element 28b. The main bearing 30, the sub bearing 31, and the partition plate 32, which serve as the shaft support of the drive shaft 29, close the openings at both ends of each compression element cylinder. The compression operation of the swinging piston type compressor of this embodiment is the same as that of the swinging piston type compressor shown in Figs. 1 and 3, but the flow of refrigerant gas is different.

The refrigerant gas enters and is compressed into the cylinder 1 'of the low pressure compression element 28a through the suction pipe 33 attached to the sealed container 6, and the compressed refrigerant gas is discharge port (formed in the main bearing 30) ( Through 34a), it is discharged into the sealed container 6 through the discharge silencer 35.

The refrigerant gas discharged into the sealed container 6 is discharged from the discharge pipe 36 to the outside, radiated and cooled by the intermediate cooler 37, and then the cylinder of the compression element 28b for compression through the suction pipe 38. Once inside (1 ''), the compressed refrigerant gas enters the discharge chamber 39 through the discharge port 34b disposed in the sub bearing 31, and flows out through the discharge pipe 40 from there.

Next, the oil supply mechanism of the compression mechanism portion will be described. 14 and 15, by the rotation of the drive shaft 29, the vane portion 8b '' of the high-pressure compression element 28b moves forward and backward in the hole portion 1c, so that the volume of the hole portion 1c. Is changed. By the pumping action according to this volume change, the lubricating oil 16 stored in the bottom of the sealed container 6 is sucked from the fluid diode 41 and is pulled up to the drive shaft 29 through the oil supply pipe 19. The sub bearing 31, the eccentric portions 41a and 41b, and the main bearing 30 are lubricated through the spiral groove 20 provided on the outer circumference of the drive shaft 29 and returned to the sealed container again.

A part of the lubricating oil 16 lubricating the eccentric portion 42a of the low pressure compression element 28a is supplied to the suction chamber by the pressure difference between the inner surface of the roller portion 8a 'and the suction chamber, so that the high pressure compression element 28b A part of the lubricating oil 16 lubricating the eccentric portion 42b is supplied to the suction chamber in the same manner as the oil pocket method as shown in FIG.

Here, even if the oil pocket is provided in any one of the end surface of the sub bearing 31 and the end surface of the partition plate 32, the same effect can be acquired.

The refrigerant gas foamed from the lubricating oil 16 passing through the spiral groove 20 leaks from the compression chambers of the high-pressure compression element 28b from the gas bleed holes 43a and 43b to the inner surface of the roller portion 8a ''. The high-pressure refrigerant gas which has entered is discharged to the sealed container 6 by the gas discharge hole 4c formed in the drive shaft 29 through the gas releasing hole 43b.

Here, the inner surface of the roller portion 8a '' of the high-pressure compression element 28b coexists with the refrigerant gas leaking out of the compression chamber 10 and the lubricating oil 16 lubricating the eccentric portion 42b. Due to the centrifugal force caused by the rotation of 29, from the difference in density between the lubricating oil and the refrigerant gas, the highly lubricating oil is positioned to the outside and the less dense refrigerant gas is to the inside. It can discharge from the gas discharge hole 4c formed in the inside of the drive shaft 29 through the through-hole. In addition, the internal leak can be suppressed without inhibiting the oil supply by the oil pocket to the suction chamber required for the inner seal.

As described above, the horizontally mounted rocking piston-type two-stage compressor of the present embodiment includes the oil pocket 21 and the cutout portion 8c shown in FIG. 4, thereby ensuring high performance and high reliability under a wide range of rotation speed conditions. have.

As described in detail above, the hermetic rotary compressor in the present invention can obtain high reliability at high performance in a wide range of rotation speed conditions.

Claims (10)

A drive shaft having a stator and a rotor in an airtight container, a drive shaft having an eccentric for transmitting rotation by the drive element, and a compression element for compressing a working fluid by rotation of the eccentric of the drive shaft, The compression element includes a cylinder having a cylindrical outer circumferential surface with open ends, a roller fitted into an eccentric portion of the drive shaft within the cylinder, and vanes for partitioning the cylinder into a suction chamber and a compression chamber with an eccentric motion of the roller; The end plate which closes the opening of the cylinder, a lubrication mechanism for lubricating oil in the roller via the drive shaft, a blowing portion for injecting the lubricating oil lubricated into the roller, and a space inside the roller and the suction chamber to communicate with each other. A closed rotary compressor comprising a lubricating oil supply mechanism having a holding holding portion for holding lubricating oil from the portion. The closed type rotary type according to claim 1, wherein the working fluid compressed by the compressor has a discharge pipe passing through the sealed container to the outside of the sealed container, and the inside of the sealed container is set to a pressure lower than the discharge pressure. compressor. The hermetic rotary compressor according to claim 1, wherein the blowing portion is a cutout portion provided on an end face of the roller, and the holding portion is a recess portion provided in the end plate. The hermetic rotary compressor according to claim 1, wherein the blowing portion is an annular groove provided in the end face of the roller, and the holding portion is a recess provided in the end plate. The said blowing part is a space which consists of the said roller part, an end plate, and an eccentric part, The center of the axial direction of the said eccentric part is located in the said holding | maintenance part side with respect to the center of the rotation axis direction of the said roller. Hermetic rotary compressor. 6. The holding portion according to claim 5, wherein the holding portion is a recess provided in the end plate, and the width of the gap between the eccentric portion of the blowing portion and the end plate provided with the holding portion is substantially the same as the depth of the recessed portion of the holding portion. Sealed rotary compressor, characterized in that. The said blowing part is a space which consists of the said roller, an end plate, and an eccentric part, The said holding | maintenance part is a recessed part provided in the said end plate, The recessed part whose cross-sectional area changes in the depth direction of the recessed recess is characterized by the above-mentioned. Hermetic rotary compressor. The said blowing part is a space which consists of the said roller, an end plate, and an eccentric part, The said holding | maintenance part is a recessed part provided in the said end plate, and is a recessed part whose cross-sectional area changes in the direction perpendicular to the recessed depression depth direction. Hermetic rotary compressor, characterized in that. The hermetic rotary compressor according to claim 1, wherein the blowing portion is an opening having a shape along the inner circumferential direction of the roller, and the holding portion is a recess provided in the end plate. A hermetic rotary compressor for compressing the working fluid sucked through the suction pipe with the driving force of the electric motor, a condenser for taking in and condensing the compressed working fluid through the discharge pipe, and an expansion mechanism for adiabatic expansion of the working fluid condensed in the condenser; And a speed control circuit for determining a target temperature based on the information detected by the sensor and controlling the rotational speed of the motor of the hermetic rotary compressor according to the target temperature. Equipped, The hermetic rotary compressor includes a drive element having an electric element having an electric motor in which a rotational speed is changed under the control of the speed control circuit in a closed container, a drive shaft having an eccentric portion for transmitting rotation of the motor, and an eccentric rotation of the drive shaft. Has a compression element for compressing the working fluid by The compression element includes a cylinder having a cylindrical inner circumferential surface with open ends, a roller fitted into an eccentric portion of the drive shaft in the cylinder, and vanes for partitioning the cylinder into a suction chamber and a compression chamber with an eccentric motion of the roller; An end plate which closes the opening of the seal cylinder, an oil supply mechanism for lubricating oil into the roller via the drive shaft, a blowing portion for injecting the lubricating oil lubricated into the roller, and a space inside the roller and the suction chamber, and are in communication with each other. A lubricating oil supply mechanism having a holding holding portion for holding a lubricating oil from the portion.

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