JP2003206877A - Closed rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent an internal leakage from occurring due to insufficient oil volume in a cylinder in a low speed range and a suction air heating loss and an increase in discharge oil volume from occurring due to defective lubrication of sliding parts and an excessive amount of oil supplied to the cylinder in a high speed range, even when the volume of supply oil in a roller part is varied by a rotational speed. <P>SOLUTION: This rotary compressor comprises motors controlled at different rotational speeds. The inside of a closed container is under a suction pressure. A front part allowing lubricating oil supplied to the inner surface of the roller part to flow therein and a rear part alternately reciprocating between the front part and a suction side and temporarily holding the lubricating oil in the front part are provided on an end plate closing a roller in the cylinder. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hermetic rotary compressor, a refrigerating or air conditioning system and a heat pump system, and in particular, a hermetic rotary compressor having high performance and high reliability under a wide range of rotation speed conditions. It is suitable for an apparatus including a machine and a refrigeration system.

[0002]

2. Description of the Related Art A rotary compressor, which is a rotary compressor conventionally used in a refrigeration or air-conditioning system, is driven by an electric element having a stator and a rotor in a hermetic container, and the electric element. A compression element is stored. In the compression element, a roller that is rotatably fitted to the eccentric portion of the drive shaft eccentrically rotates in the cylinder by the rotation of the drive shaft that transmits the rotational force from the electric element, and compresses the refrigerant that is the working fluid.

To further describe the compression process, the inside of the cylinder is divided into a suction chamber and a compression chamber by a vane pressed by a roller, so that the refrigerant gas sucked into the suction chamber by the suction pipe is compressed in the compression chamber. The compressed refrigerant gas is discharged into the closed container and then discharged from the discharge pipe to the external refrigeration cycle.

The rotary compressor configured as described above is
In order to increase the back pressure of the vane that presses the roller, it is often the case that the discharge pressure is set in the closed container. Lubricating oil is normally supplied into the cylinder from a lubricating oil supply portion provided inside the roller through a gap between the roller and the end plate. The end plate is a plate-shaped member that is arranged to face the end of a roller having a tubular shape, and forms a suction chamber or a compression chamber in cooperation with the cylinder and the roller.

When the back pressure is applied to the vane when the pressure in the closed container is changed to the discharge pressure, if the above-mentioned lubricating oil supply mechanism is used, the lubricating oil leaking into the suction chamber due to the differential pressure may be excessive. . If the supply of lubricating oil into the suction chamber becomes excessive, there will be problems such as deterioration of compressor performance due to heat loss and the like, and deterioration of reliability due to a rise in coil temperature of the electric element.

Further, when the compressor is operated intermittently, when the compressor is stopped, the high-temperature, high-pressure gas in the closed container flows back into the evaporator, raising the temperature of the evaporator and degrading the performance of the refrigeration / air-conditioning system. There was also the problem of intermittent loss.

Further, from the viewpoint of preventing global warming, natural refrigerants are considered to be promising as future refrigerants. However, some natural refrigerants have a low global warming potential but are flammable (eg, isobutane). When this flammable refrigerant is used, there is a high possibility that the amount enclosed in the device (the amount of refrigerant used) will be limited in terms of safety.

In general, the higher the atmospheric pressure in the closed container, the greater the amount of the refrigerant dissolved in the lubricating oil stored in the lower part of the closed container. Therefore, the amount of the refrigerant to be sealed in the device increases in order to compensate for the melting amount of the refrigerant.

As described above, in the compressor of the type in which the discharge pressure is in the closed container, the amount of refrigerant to be enclosed in the device tends to increase, so that there is a problem that it is difficult to apply a natural refrigerant having flammability. Exists.

In order to solve the above problems, a rotary compressor disclosed in Japanese Patent Publication No. 07-72547 as a low-pressure container type rotary compressor in which the pressure in the hermetically sealed container is substantially the same as the low-pressure side (suction pressure) of the compressor. There is a compressor.

The inner surface (cylinder side) of the bearing plate of the rotary compressor disclosed therein has a section in which the rolling piston (roller) fully communicates with the low pressure chamber in the cylinder while the eccentric rotation of the rolling piston makes one rotation. It is provided with an oil sump concave portion having a position and a size which are three sections of a section closed by the end plate of the rolling piston and a section which is in full communication with the inside of the rolling piston. With this configuration, during one rotation of the rotating shaft due to the operation of the compressor, the lubricating oil having an oil amount proportional to the volume of the recess is always a constant amount per one rotation of the rotating shaft regardless of the pressure condition. It is described that the oil can be supplied to the low-pressure chamber, and a large amount of lubricating oil can be prevented from flowing out of the machine at the time of starting.

[0012]

The oil supplied to the oil sump recess is supplied by the following mechanism. First, oil that lubricates the sliding surface of the eccentric part of the drive shaft is supplied to the inside of the rolling piston, and then the lubricating oil that is supplied to the inside of this rolling piston is eccentrically moved by the centrifugal action of the rotating shaft and inside the rolling piston. An oil film is formed on. This oil film thickness depends on the amount of oil supplied to the inside of the rolling piston. Therefore, the oil film thickness becomes thinner under the condition that the amount of oil supply decreases, that is, the condition that the motor rotation speed in the device decreases. In particular, when the rotary compressor is a horizontal type, it is considered that the area covering the opening of the oil sump recess of the lubricating oil becomes small and the volumetric efficiency of taking in the lubricating oil in the oil sump recess becomes low.

From the above, in the above-mentioned known example, the volume efficiency of the oil sump concave portion for taking in the lubricating oil becomes lower as the speed of the motor becomes lower when the oil film becomes thinner. Also, if the volume of the oil sump recess is set to a volume that can supply the amount of oil required for internal lubrication under the low speed condition of the motor, the oil taken into the oil sump recess under the high speed condition of the motor rotation speed will be the condition that the oil film becomes thick. The amount increases. Then, there is a problem that the amount of oil supplied to the cylinder becomes excessive, the intake heating loss and the amount of oil discharged to the outside of the compressor increase, and the compressor performance and cycle performance deteriorate.

Further, if the volume of the oil sump recess is set so that the amount of oil discharged does not deteriorate cycle performance under high speed conditions of the motor, the amount of oil taken into the oil sump recess is insufficient under low speed conditions where the oil film becomes thin. However, problems such as internal leakage and poor lubrication between the vane and the rolling piston occur.

The object of the present invention is to maintain a constant value per revolution even when the amount of oil supplied to the inside of the roller portion changes due to fluctuations in the rotation speed of the hermetic rotary compressor, regardless of whether the electric element of the compressor is low speed or high speed. To allow a quantity of oil to be delivered to the suction chamber.

[0016]

In order to achieve the above object, a hermetic rotary compressor according to the present invention includes an electric element having a stator and a rotor in a hermetic container, and rotation by the electric element. A drive shaft having an eccentric part for transmitting, and a compression element for compressing the working fluid by rotation of the eccentric part of the drive shaft,
This compression element includes a cylinder having a cylindrical inner peripheral surface with both ends open, a roller fitted into the eccentric portion of the drive shaft in the cylinder, and the eccentric movement of the roller into a suction chamber and a compression chamber inside the cylinder. A partitioning vane, an end plate that closes the opening of the cylinder, an oil supply mechanism that supplies lubricating oil into the roller via the drive shaft, and a front part that takes in the lubricated oil inside the roller and the inside of the roller. And a rear part that holds the lubricating oil from the front part and that alternately communicates the spaces and the suction chambers.

[0017]

DETAILED DESCRIPTION OF THE INVENTION Each embodiment of the present invention will be described below with reference to the drawings. In addition, in the second and subsequent embodiments, a part of the configuration common to the first embodiment will be omitted, and redundant description will be omitted.

First, a first embodiment of the present invention will be described with reference to FIGS. In the hermetic rotary compressor of this embodiment, an electric element, a compression element, and a drive shaft 4 that connects the electric element and the compression element are arranged in a hermetic container 6. Further, in the present embodiment, the suction pressure in the closed container 6 is lower than the discharge pressure.

The electric element has a stator 7 and a rotor 5. The compression element has a compression mechanism and an oil supply mechanism. The compression mechanism is a cylinder 1 having a cylindrical inner peripheral surface 1a.
And a swinging piston 8 rotatably arranged in the cylinder 1, and a main bearing 2 and a sub bearing 3 that close the openings at both ends of the cylinder 1. The drive shaft 4 is fixed to the rotor 5 of the electric element and transmits the drive force to the compression element. When the eccentric portion 4a of the drive shaft 4 rotates eccentrically, the swing piston 8 rotates eccentrically inside the cylinder 1.

The oil supply mechanism will be described in detail later, but the hole portion 1 of the cylinder 1 due to the end portion of the vane portion 8b coming in and out.
The lubricating oil flowing from the suction fluid diode 17 is sent to the oil supply pipe 19 through the discharge fluid diode 18 as the volume of c changes. The lubricating oil supplied through the oil supply pipe 19 enters the auxiliary bearing 3 and is supplied into each bearing by the spiral groove 20 provided on the surface of the drive shaft 4.

The configuration of the compression mechanism will be described in detail. The main bearing 2 and the sub bearing 3 have at least the cylindrical inner peripheral surface 1a of the cylinder 1.
The openings at both ends are closed. In this embodiment, the cylinder 1 is fixed to the main bearing 2. The main bearing 2 and the sub bearing 3 are respectively provided with bearing portions 2a and 3a at the centers of the portions corresponding to the cylindrical inner peripheral surface 1a of the cylinder 1, and rotatably support the drive shaft 4. Further, the main bearing 2 and the sub bearing 3 are fixed to the cylinder 1 such that the rotary shaft of the drive shaft 4 (a portion other than the eccentric portion 4a) coincides with the central axis of the cylindrical inner peripheral surface 1a of the cylinder 1. . The outer peripheral portion of the main bearing 2 is fixed to the closed container 6, and the stator 7 of the electric element is fixed to the closed container 6.

The drive shaft 4 is provided with an eccentric portion 4a at a portion located inside the cylindrical inner peripheral surface 1a of the cylinder 1.
That is, the cylindrical inner peripheral surface of the roller portion 8a of the swing piston 8 is rotatably fitted into the cylindrical outer peripheral surface of the eccentric portion 4a. The dimensions of each part are determined so that the gap between the cylindrical outer peripheral surface of the roller portion 8a and the cylindrical inner peripheral surface 1a of the cylinder 1 is very small.

A vane portion 8b is provided on the cylindrical outer peripheral surface of the roller portion 8a. A cylindrical hole portion 1b having a central axis parallel to the central axis of the cylindrical inner peripheral surface 1a is provided outside the cylindrical inner peripheral surface 1a of the cylinder 1. Cylindrical hole 1
The center side and the opposite side of the cylinder 1 of b communicate with the cylindrical inner peripheral surface 1a of the cylinder 1 and another hole portion 1c provided outside the cylindrical hole portion 1b, respectively. The vane portion 8b is inserted into the cylindrical hole portion 1b and the hole portion 1c, but between the vane portion 8b and the cylindrical hole portion 1b, a flat portion slidably abutting on the flat portion of the vane portion 8b and a cylinder are provided. A sliding member 9 having a cylindrical surface portion slidably abutting on the cylindrical surface portion of the hole portion 1b is incorporated with the vane portion 8b sandwiched therebetween. As a result, the vane portion 8b performs a forward / backward movement toward the central axis of the cylindrical hole portion 1b and a swinging movement around the central axis. The tip of the vane 8b moves in the hole 1c and does not come out of the cylindrical hole 1b and interfere with the cylinder 1.

With the above structure, when the drive shaft 4 is rotated by the electric element, the oscillating piston 8 moves the eccentric portion 4a.
At the same time, an orbital motion involving rocking is performed in the cylinder 1. FIG. 3 shows the swing piston 8 when the drive shaft 4 rotates by 60 °.
It is a figure showing the exercise of. The roller portion 8a includes the eccentric portion 4a.
Along with the rotational movement of, the center makes an orbital movement. The vane portion 8b always faces the central axis direction of the cylindrical hole portion 1b and swings around the central axis of the eccentric portion 4a by a slight angle.
When the movement of the vane portion 8b, that is, the forward / backward movement toward the central axis of the cylindrical hole portion 1b and the swinging movement around the central axis, are performed, the seal of the gap between the vane portion 8b and the cylindrical hole portion 1b is The sliding member 9 inserted between the vane portion 8b and the cylindrical hole portion 1b is kept by sealing.

Therefore, the combination of the cylinder 1, the oscillating piston 8, the main bearing 2, the auxiliary bearing 3 and the sliding member 9 makes the compression chamber 10 (hatched portion in FIG. 3) which is a closed space and the suction chamber 11 which is a suction space. Is configured. As the drive shaft 4 is rotated by the electric element, its volume is repeatedly increased and decreased as shown in FIG. In FIG. 3, the compression chamber 10 is formed in all of FIGS.

With such a configuration, the refrigerant gas as the working fluid is compressed as described below. First, the refrigerant gas is supplied from the suction pipe 12 attached to the closed container 6 to the closed container 6
After being sucked in and passing through the suction passage 13, the suction chamber 11
Is sucked into. (The suction chamber 11 is (a) θ in FIG.
= 0 ° (b) θ = 60 ° As shown in θ = 60 °, from the state where the suction port 1d is blocked by the roller portion 8a,
(F) Exceeds θ = 300 °, and exists until the discharge port 3b is closed as in (a) θ = 0 °. ) Compression chamber 10
The refrigerant gas is compressed at the same time as the volume of the refrigerant decreases. Secondary bearing 3
The refrigerant gas discharged from the discharge port 3b provided in the discharge port 3b is discharged into the discharge chamber 3c provided by the auxiliary bearing 3 and the discharge cover 14. Then, the compressed refrigerant gas is discharged to the outside of the closed container 6 through the discharge pipe 15 penetrating the closed container 6.

As described above, particularly in this embodiment, the refrigerant gas having passed through the suction pipe 12 is temporarily sucked into the closed container, and the closed container 6 has a suction pressure. At this time, the refrigerant gas compressed in the compression chamber 10 is not directly discharged into the closed container 6 but is discharged to the outside of the closed container 6 through the discharge pipe 3 through the discharge chamber 3c.

The following advantages can be obtained by setting the suction pressure in the closed container 6. (1) Since the electric element is less heated by the compressed high-temperature refrigerant gas and is cooled by the low-temperature refrigerant gas, the temperatures of the rotor 5 and the stator 7 are lowered, the motor efficiency is improved, and the performance is improved. Can be achieved. (2) Since the suction pressure is applied to the inside of the roller portion 8a, excess oil is not supplied from the inner surface of the roller portion 8a to the suction chamber 11 due to the differential pressure, and the performance of the compressor can be improved. (3) Refrigerant that is compatible with lubricating oil, such as CFC, has a low pressure, so the proportion of the refrigerant gas that dissolves in the oil is small, and the foaming phenomenon of the refrigerant gas in bearings etc. is unlikely to occur, improving reliability. can do. In addition, the use of flammable natural refrigerants (isobutane, propane, etc.), which are promising new refrigerants in the future, will reduce the amount of refrigerant used and improve safety. (4) The pressure resistance of the closed container 6 can be lowered, and the thin wall and light weight can be achieved. Further, the oscillating piston type compressor shown in the present embodiment can be easily applied to a structure in which the closed container has a suction pressure. Because the roller and the vane are integrated, it is not necessary to apply a high back pressure to the vane in order to press the vane against the roller unlike a rotary compressor in which the roller and the vane are provided separately. Next, the oil supply mechanism of the compression mechanism section will be described in detail. In FIG. 1, by the rotation of the drive shaft 4,
The vane 8b moves back and forth in the hole 1c, and the volume of the hole 1c changes. Due to the pumping action due to this volume change (hereinafter referred to as a vane oil supply pump), the lubricating oil 16 stored in the bottom portion of the closed container 6 is sucked from the suction fluid diode 17, passes through the discharge fluid diode 18, and the oil supply pipe 19, Pumped up to the drive shaft 4. Further, the pumped lubricating oil 16 passes through the spiral groove 20 provided on the outer periphery of the drive shaft 4, lubricates the sub bearing 3, the eccentric portion 4a, and the main bearing 2, and returns to the sealed container 6 again.

The lubricating oil 16 that has lubricated the eccentric portion 4a flows out to the inner surface side of the roller portion 8a. Even if the refrigerant gas foams from the lubricating oil 16 passing through the spiral groove 20, the foamed refrigerant gas is discharged from the drive shaft 4 through the gas vent hole 4b opening on the outer peripheral surface of the eccentric portion 4a facing the inner surface of the roller portion 8a. The gas is exhausted through the gas exhaust hole 4c provided inside.

The high-pressure refrigerant gas leaking from the compression chamber 10 to the inside of the roller portion 8a has an opening on the surface of the eccentric portion 4a facing the main bearing 2 and the sub bearing 3, and the gas discharge hole 4c.
The gas is discharged into the closed container 6 through a gas discharge hole 4c provided inside the drive shaft 4 through a communication hole 4e communicating with the.

Here, a structure in which the lubricating oil 16 supplied on the inner surface of the roller portion 8a is stably supplied into the cylinder 1 will be described. In FIG. 3, a cutout portion 8c that opens inside the roller portion 8a is provided on the end surface of the roller portion 8a. On the end plate of the sub-bearing 3, at the position where the notch portion 8c of the end surface of the roller portion 8a communicating with the space inside the roller portion 8a and the suction chamber alternate, there is a recess in which the plane of the end plate is depressed. An oil pocket 21 is provided. The position on the end plate of the auxiliary bearing 3 which alternates between the cutout portion 8c of the end face of the roller portion 8a and the suction chamber is determined by the discharge port 3 in the cylinder 1.
It is not the d side but the suction port 1d side. That is, the position of the sub bearing 3 on the end plate is a position where the space inside the roller portion 8 a communicates with the suction chamber 11.

Lubricating oil 1 supplied on the inner surface of the roller portion 8a
6 is supplied to the oil pocket 21 of the sub bearing 3 at a position facing the notch 8c. After that, when the oil pocket 21 opens into the suction chamber 11, the oil pocket 21
The lubricating oil 16 therein is supplied to the suction chamber 11.

Further description will be given with reference to FIGS. 4 and 5. 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 lubricates the surface of the eccentric portion 4a that faces the sub bearing 3. The oil 16 is accumulated by the centrifugal action associated with the rotation of the drive shaft 4. The cutout portion 8c guides the accumulated lubricating oil 16 to the oil pocket 21. The state in which the cutout portion 8c covers the oil pocket 21 changes depending on the range of the cutout portion 8c.

With the above structure, the oil pocket 21 communicates with the notch 8c provided on the end face of the roller portion 8a to supply the lubricating oil 16, and thus the roller portion 8a.
Even if the amount of the lubricating oil 16 supplied to the inner circumference is small, the oil pocket 21 is entirely covered with the lubricating oil 16 which is collected and guided in the notch 8c corresponding to the front portion thereof, so that the oil pocket 21 The lubricating oil 16 is smoothly taken into the oil pocket 21, and the volumetric efficiency of taking the lubricating oil into the oil pocket 21 is improved. As a result, even when the amount of oil in the roller portion 8a changes depending on the rotation speed, a certain amount of lubricating oil can be supplied to the suction chamber per one rotation. That is, cylinder 1 in the low speed range
It is possible to prevent internal leakage due to insufficient oil amount in the interior, lubrication failure between the sliding member and the cylindrical hole, and intake heat loss and increase in discharge oil amount due to excessive oil supply to the suction chamber in the high speed range. It is possible to provide a high performance and highly reliable hermetic rotary compressor.

Since the notch portion 8c communicates with the oil pocket 21 when the pressure in the compression chamber does not rise (almost suction pressure), the sealability of the end face of the roller portion 8a is not deteriorated.

Next, a second embodiment of the present invention will be described with reference to FIGS. 6 and 7. In the present embodiment, the roller portion 8a
The stepped annular groove 8d is provided by denting the corner portion of the end surface of the surface facing the eccentric portion 4a over the entire circumference. Annular groove 8d
Has the effect of reducing the contact area of the roller portion 8a with respect to the eccentric portion 4a and reducing the contact resistance. As shown in FIG. 7, not only the sub bearing 3 side of the roller portion 8a but also the main bearing 2
The contact resistance is further reduced by providing the annular groove 8d on the side as well.

By the annular groove 8d, the lubricating oil 16 supplied to the inner surface of the roller portion 8a is guided and gathered in the eccentric direction in the annular groove 8d by the centrifugal action accompanying the rotation of the drive shaft 4. On the end plate of the auxiliary bearing 3, the annular groove 8d and the suction chamber 11
When the oil pockets 21 provided at positions that alternately come and go communicate with the annular groove 8d, the lubricating oil 16 guided to the annular groove 8d is supplied to the oil pocket 21. After that, when the oil pocket 21 opens into the suction chamber 11, the lubricating oil 16 in the oil pocket 21 is supplied to the suction chamber 11.

With the above configuration, the roller portion 8
Even if the amount of the lubricating oil 16 supplied to the inner periphery of the a is small, the oil pocket 21 is entirely covered with the lubricating oil 16 that is collected and guided in the notch 8c corresponding to the front portion of the oil pocket 21. 21 improves the volumetric efficiency of taking in the lubricating oil. Further, since the annular groove 8d is provided on both sides of the end face of the roller portion 8a to reduce the contact area with the end faces of the main and auxiliary bearings, the roller portion 8a is of a type having a large wall thickness (for example, the same cylinder). In the compressor of which the inner and outer diameters of the roller portion, the outer diameter of the eccentric portion of the drive shaft, and the eccentric amount are changed to reduce the displacement volume of the compressor), the same effects as those of the first embodiment can be obtained. The sliding loss on the end face of the roller portion 8a can be reduced.

Next, a third embodiment of the present invention will be described with reference to FIGS. In the present embodiment, the roller portion 8a is opened inside the roller portion 8a on the end plate of the auxiliary bearing 3, and
With the eccentric movement of a, the concave portion 22 is formed at a position which becomes a part of the suction chamber.
To provide. The recess 22 has a shape in which the depth h is reduced from the outside toward the center in the radial direction of the cylinder 1 when viewed from the cross section of the sub bearing 3 (see FIG. 9).

By providing such a concave portion 22, the lubricating oil 16 supplied to the inside of the roller portion 8a alternates between the inside of the roller portion 8a and the suction chamber 11 on the end surface of the auxiliary bearing 3 on the cylinder 1 side. The concave portion 22 provided at the position is supplied to the concave portion 22 when communicating with the inside of the roller portion 8a. Then, when the recess 22 opens into the suction chamber 11, the lubricating oil 16 in the recess 22 is supplied to the suction chamber 11.

Here, the concave portion 22 is provided with an oil storage portion whose depth h changes with respect to the front portion into which the lubricating oil 16 enters.
As the oil film thickness in the roller portion 8a increases, the depth h decreases, that is, the depth h increases in the direction in which the thickness of the lubricating oil 16 in the roller portion 8a collected by the centrifugal action of the roller portion 8a increases. Has a function to be described below. Therefore, when the amount of oil in the roller portion 8a increases and the oil film thickness increases due to the increase in rotation speed, the change in the amount of oil supplied to the recess 22 is reduced to the depth h. It can be made smaller than the concave portion in which is constant.

The function of this oil storage portion is that the inner surface of the roller portion 8a and the bottom portion of the recess 22 (the outer surface in the radial direction of the cylinder 1 in FIG. 9) are located at substantially the same radial position of the cylinder 1. Is. By changing the cross-sectional shape of the oil storage portion (the portion recessed from the end plate surface of the auxiliary bearing 3) that is the rear portion of the recessed portion 22 as compared to the opening portion that is the front portion, the opening portion is provided large in favor of oil intake, and The part can be provided in a volume corresponding to the thickness of the oil film. In a recess having a narrow opening and a large depth h, a large amount of lubricating oil remains in the recess, failing to achieve the original purpose. Therefore, by changing the volume of the oil reservoir in the film thickness direction of the lubricating oil with respect to the opening as in the present embodiment, the intake heating loss and the discharged oil due to an excessive amount of oil supplied to the suction chamber in the high speed range. It is possible to prevent deterioration of cycle performance due to an increase in the amount.

By setting the volume of the concave portion 22 to the minimum required oil supply amount for performing internal lubrication in the low speed region, internal leakage due to insufficient oil amount in the suction chamber 11 in the low speed region and the sliding member 9 and the cylindrical hole. Poor lubrication with the portion 1b can be avoided.

As described above, the hermetic compressor to which this embodiment is applied can have high performance and high reliability under a wide range of rotation speed conditions.

Although the above-described recess 22 has a shape in which the cross-sectional area changes in the depth direction, in addition to this, the cross-sectional area changes in the direction perpendicular to the depth, and the oil film becomes thicker and the amount of oil supplied to the recess is increased. The same action and effect can be obtained if the shape is such that the rate of increase of is small.

Next, a fourth embodiment of the present invention will be described with reference to FIG. In FIG. 11, a recess 23 having a shape elongated in the inner circumferential direction of the roller portion 8a is provided at a position on the end plate of the sub bearing 3 which alternates between the inside of the roller portion 8a and the suction chamber 11.

Lubricating oil 16 supplied to the inside of the roller portion 8a
Is supplied to the recess 23. Then, when the front part of the recess 23 opens into the suction chamber 11, the lubricating oil 16 in the recess 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 oil film thickness of the lubricating oil accumulated in the roller portion 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 appropriately sets the angle α with respect to the center of the eccentric portion 4a to optimally set the volume of the recess 23.

Since the width b of the opening of the recess 23 is equal to or smaller than the oil film thickness in the low speed range of the hermetic compressor, even if the electric motor of the compressor is rotated at a low speed, the recess 23 is filled with the lubricating oil 16.
The entire volume of the recess 23 is covered, and the volumetric efficiency of taking in the lubricating oil in the recess 23 is improved. As a result, even when the amount of oil in the roller portion 8a changes depending on the rotation speed, leakage of refrigerant gas inside the cylinder and poor lubrication between the sliding member and the cylindrical hole portion due to insufficient amount of oil in the cylinder 1 in the low speed range can be prevented. Will be able to.

Further, by providing a front opening portion for taking in a fixed amount of lubricating oil per one rotation in accordance with the rotation of the compressor in the low speed region, the front portion becomes a flow path resistance at the rotation speed in the high speed region. In addition, it is possible to prevent intake heating loss and increase in the amount of lubricating oil discharged due to an excessive amount of oil supply into the suction chamber. Therefore, the hermetic rotary compressor to which the present embodiment is applied can obtain high performance and high reliability under a wide range of rotation speed conditions.

Next, a fifth embodiment of the present invention will be described with reference to FIG. In the present embodiment, an oil pocket 21 serving as an oil storage portion is provided at a position on the end plate of the sub bearing 3 which alternates between the inside of the roller portion 8a and the suction chamber 11, and the eccentric portion 4a is provided at the front portion of the oil pocket 21. Has a front supply portion located on the side of the sub bearing 3 with a gap δ and including an eccentric portion 4a and a roller portion 8a.

Lubricating oil 16 supplied to the inside of the roller portion 8a
When the oil pocket 21 communicates with the inside of the roller portion 8a, the eccentric portion 4a and the roller portion 8 which are separated from the sub bearing 3 by a gap δ.
The oil is supplied to the oil pocket 21 from the front supply part by a. When the oil pocket 21 opens in the suction chamber 11, the lubricating oil 16 in the oil pocket 21 is supplied to the suction chamber 11.

Regarding the position of the surface of the eccentric portion 4a facing the sub bearing 3, the center line of the thickness of the eccentric portion 4a is located on the oil pocket 21 side with respect to the center line of the height of the roller portion 8a. , The gap δ between the eccentric portion 4a and the auxiliary bearing 3 and the oil pocket 2
The depth h of 1 is almost equal.

The oil pocket 21 inside the roller portion 8a
Since the volume of the space on the side becomes smaller and the oil surface of the lubricating oil supplied to the inside of the roller portion 8a becomes higher toward the center of the eccentric portion 4a, the lubricating oil 16 on the inside of the roller portion 8a and on the oil pocket 21 side is Oil pocket 21 even if only a small amount is supplied
Are covered with the lubricating oil 16. Therefore, the volumetric efficiency of taking in the lubricating oil in the oil pocket 21 is improved.

As a result, depending on the rotation speed, the roller portion 8a
Even if the amount of oil inside changes, a certain amount of lubricating oil can be supplied to the suction chamber per one rotation. In other words, the cylinder 1 when the electric motor of the hermetic compressor operates in the low speed range
The shortage of the amount of oil in the inside can be reduced, and the leakage of the compressed refrigerant gas inside the cylinder 1 and the poor lubrication between the sliding member and the cylindrical hole can be prevented. Further, the intake air heating loss and the increase in the amount of lubricating oil discharged into the suction chamber and the compression chamber can be prevented by the front supply portion absorbing an excessive amount of oil supply to the suction chamber when operating in the high speed range. Therefore, the hermetic rotary compressor to which the present embodiment is applied can obtain high performance and high reliability under a wide range of rotation speed conditions.

In the above embodiment, in the one-cylinder type compressor, the oil pocket 21 and the recess 2 are formed on the end surface of the auxiliary bearing 3.
2, the concave portion 23 is provided, but it is needless to say that the same effect can be obtained by providing the concave portion 23 on the main bearing 2 side.
Further, it can be easily applied to a two-cylinder type hermetic rotary compressor by providing a common configuration.

Next, a sixth embodiment of the present invention will be described with reference to FIG. This cycle is a cycle dedicated to freezing (cooling). By activating 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 from the discharge pipe 15 to the condenser 24 as indicated by the solid arrow. And is radiated and liquefied by the blowing action of the condenser fan 24a. The liquefied refrigerant is throttled by the expansion valve 25 and adiabatically expanded to a low temperature and low pressure. The low-temperature, low-pressure liquid refrigerant absorbs heat from the air supplied by the evaporator fan 26a in the evaporator 26, is gasified, and then passes through the suction pipe 12 to the hermetic rotary compressor 27. Inhaled.

Since the refrigeration system shown in FIG. 13 is equipped with the hermetic rotary compressor to which the embodiment of the present invention is applied, a refrigeration system excellent in energy efficiency can be obtained over the entire operating range. The details will be described 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 compressor 2 according to the target temperature.
7 controls the rotation speed of the electric motor. When this refrigeration system is applied to refrigeration equipment such as refrigerators,
The temperature sensor 51 is provided at a place where the temperature inside the refrigerator whose temperature is desired to be detected can be detected. Further, when this refrigeration system is applied to an air conditioner such as an air conditioner, the refrigeration system is installed near a heat exchanger arranged indoors. In the case of an air conditioner, it is also effective to provide a humidity sensor in the system and control the rotation speed of the electric motor by taking the output value of the humidity sensor into consideration by the speed control circuit 50. Furthermore, when this refrigeration system is applied to a hot water supply device, a temperature sensor is provided to measure the temperature of water that has been heat exchanged and heated.

The speed control circuit 50 controls the system compressor 2 in order to control the system to the target temperature of the refrigeration system.
7 controls the rotation speed of the electric motor. When controlling the rotational speed of the compressor in order to increase the energy efficiency of the system, the compressor should not lose efficiency for different rotational speeds.

When the refrigeration system having the hermetic rotary compressor 27 to which the embodiment of the present invention is applied as a constituent element is used to change the rotational speed and change the amount of lubricating oil supplied to the inside of the roller portion. However, a constant amount of oil can always be supplied to the suction chamber per revolution.

Under the condition that the capacity is not required with respect to the target temperature, it is not necessary to rotate the electric motor (motor) of the compressor at high speed, and the refrigeration system performs control to rotate the compressor at low speed. In such a case, the hermetic rotary compressor to which the embodiment of the present invention is applied does not cause internal leakage or insufficient lubrication between the sliding member and the cylindrical hole due to insufficient oil amount in the cylinder in the low speed range.

Further, 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 such a case, the hermetic rotary compressor to which the embodiment of the present invention is applied can prevent an intake heating loss and an increase in the discharge oil amount due to an excessive amount of oil supply to the cylinder in the high speed range.

Particularly, in the hermetic rotary compressor to which the embodiment of the present invention is applied, since the pressure inside the hermetic container 6 is set to be equal to or lower than the discharge pressure, the amount of the high temperature / high pressure refrigerant flowing into the evaporator during the intermittent operation. Can be reduced, and intermittent energy loss can be reduced.

Here, it is obvious that even if the embodiment is modified appropriately according to the refrigeration system or the air conditioning system, it is within the scope of the embodiment of the present invention. Further, although the description has been given using the single-stage compressor, it goes without saying that the embodiment of the present invention can be applied to the two-stage compressor. An example will be described below.

Next, a seventh embodiment of the present invention will be described with reference to FIGS. 14 and 15. Here, the components denoted by the same reference numerals as those in FIGS. 1 to 13 are the same components and have the same operation.

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

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

The refrigerant gas discharged into the airtight container 6 is discharged from the discharge pipe 36 to the outside, radiated by the intercooler 37 to be cooled, and then passes through the suction pipe 38 to the cylinder 1 of the high pressure compression element 28b. '', The compressed refrigerant gas enters the discharge chamber 39 through the discharge port 34b provided in the auxiliary bearing 31, and the discharge pipe 40 is taken from there to flow out.

Next, the oil supply mechanism of the compression mechanism section will be described. 14 and 15, the rotation of the drive shaft 29 causes the vane portion 8b ″ of the high pressure compression element 28b to move into the hole portion 1c.
It moves back and forth in the space, and the volume of the hole 1c changes. Due to the pumping action due to this volume change, the lubricating oil 16 stored at the bottom of the closed container 6 is sucked from the fluid diode 41,
The auxiliary bearing 31, the eccentric portions 41a and 41b, and the main bearing 3 are bitten up to the drive shaft 29 through the oil supply pipe 19 and pass through the spiral groove 20 provided on the outer periphery of the drive shaft 29.
Lubricate 0 and return to the closed container again.

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

Here, the same effect can be obtained regardless of whether the oil pocket is provided on the end surface of the sub bearing 31 or the end surface of the partition plate 32.

The refrigerant gas foamed from the lubricating oil 16 passing through the spiral groove 20 is discharged through the gas vent holes 43a and 43b from the compression chamber of the high pressure compression element 28b to the inner surface of the roller portion 8a ''. The vent hole 43b is taken and the gas is discharged into the closed container 6 through the gas discharge hole 4c formed inside the drive shaft 29.

Here, the refrigerant gas leaking from the compression chamber 10 and the lubricating oil 16 lubricating the eccentric portion 42b coexist on the inner surface of the roller portion 8a '' of the high-pressure compression element 28b, and the drive shaft 29 Due to the difference in density between the lubricating oil and the refrigerant gas due to the centrifugal force caused by the rotation, the lubricating oil having a high density is located on the outside and the refrigerant gas having a low density is located on the inside, so that only the refrigerant gas is driven through the gas vent hole 43b. The gas can be discharged from the gas discharge hole 4c formed inside the shaft 29. Also, internal leakage can be suppressed without obstructing oil supply by the oil pocket to the suction chamber, which is necessary for the internal seal.

As described above, the horizontal oscillating piston type two-stage compressor of this embodiment is provided with the oil pocket 21 and the cutout portion 8c shown in FIG. 4, so that it is high in performance and high in a wide range of rotational speed conditions. The reliability can be secured.

[0076]

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

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a horizontal oscillating piston compressor according to a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is an operation explanatory diagram of the compression element in FIG. 1.

FIG. 4 is an explanatory view of a main part of the oscillating piston type compressor according to the first embodiment of the present invention.

5 is a sectional view taken along line BB of FIG.

FIG. 6 is an explanatory view of a main part of an oscillating piston type compressor according to a second embodiment of the present invention.

7 is a sectional view taken along line CC of FIG.

FIG. 8 is an explanatory view of a main part of a swing piston compressor according to a third embodiment of the present invention.

9 is a sectional view taken along line CC of FIG.

FIG. 10 is an enlarged view around the recess of FIG.

FIG. 11 is an explanatory view of a main part of a swing piston compressor according to a fourth embodiment of the present invention.

FIG. 12 is an explanatory view of a main part of a swing piston compressor according to a fifth embodiment of the present invention.

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

FIG. 14 is a vertical cross-sectional view of a horizontal oscillating piston type two-stage compressor according to a seventh embodiment of the present invention.

FIG. 15 is an enlarged view of an oil supply mechanism of the horizontal oscillating piston type two-stage compressor shown in FIG.

[Explanation of symbols]

1 ... Cylinder, 1a ... Cylindrical inner peripheral surface, 1b ... Cylindrical hole,
1c ... hole, 1d ... suction port, 2 ... main bearing, 2a ... bearing part, 3 ... sub bearing, 3a ... bearing part, 3b ... discharge port,
3c ... Discharge chamber, 4 ... Drive shaft, 4a ... Eccentric part, 4b ... Gas vent hole, 4c ... Gas discharge hole, 4e ... Communication hole, 5 ... Rotor, 6 ... Sealed container, 7 ... Stator, 8 ... Shake Dynamic piston, 8
a ... roller portion, 8b ... vane portion, 8c ... notch portion, 8d ...
Annular groove, 9 ... sliding member, 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 ... Oil supply pipe, 20 ... Spiral groove, 21 ... Oil Pocket, 22 ...
Recesses, 23 ... Recesses, 24 ... Condenser, 24a ... Condenser fan, 25 ... Expansion valve, 26 ... Evaporator, 26a ... Evaporator fan, 27 ... Hermetic rotary compressor.

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Akihiko Ishiyama             800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi             Hitachi Co., Ltd., Cooling & Heat Division (72) Inventor Yugo Mukai             800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi             Hitachi Co., Ltd., Cooling & Heat Division F term (reference) 3H029 AA01 AA15 AB03 BB01 BB08                       BB41 CC04 CC05 CC33 CC35

Claims (10)

[Claims] 1. An electric element having a stator and a rotor, a drive shaft having an eccentric portion for transmitting rotation by the electric element, and a rotation of the eccentric portion of the drive shaft compresses a working fluid. A compression element, the compression element including a cylinder having a cylindrical inner peripheral surface with both ends open, a roller fitted in the eccentric portion of the drive shaft in the cylinder, and an eccentric movement of the roller. A vane that partitions the inside of the cylinder into a suction chamber and a compression chamber, an end plate that closes the opening of the cylinder, an oil supply mechanism that supplies lubricating oil into the roller via the drive shaft, and an oil supply inside the roller. A hermetically sealed rotary system including a lubricating oil supply mechanism having an intake portion for taking in the lubricating oil, a holding portion for alternately communicating with the space inside the roller and the suction chamber for holding the lubricating oil from the intake portion. Compressor. 2. A discharge pipe for discharging the working fluid compressed in the compression chamber to the outside of the closed container by penetrating the closed container, wherein the pressure in the closed container is lower than the discharge pressure. The hermetic rotary compressor according to claim 1. 3. The hermetic rotary compressor according to claim 1, wherein the intake portion is a notch provided in an end surface of the roller, and the holding portion is a recess provided in the end plate. 4. The hermetic rotary compressor according to claim 1, wherein the intake portion is an annular groove provided on the end surface of the roller, and the holding portion is a recess provided on the end plate. 5. The take-in portion is a space composed of the roller portion, the end plate and an eccentric portion, and the center of the eccentric portion in the axial direction is on the side of the holding portion with respect to the center of the roller in the rotational axis direction. The hermetic rotary compressor according to claim 1, wherein the hermetic rotary compressor is located at. 6. The holding portion is a recess provided in the end plate, and a width of a gap between the eccentric portion of the intake portion and the end plate provided with the holding portion is a recess of the holding portion. The hermetic rotary compressor according to claim 5, which has substantially the same depth. 7. The take-in portion is a space composed of the roller, the end plate and an eccentric portion, and the holding portion is a concave portion provided in the end plate and has a sectional area in the depth direction of the concave portion. The hermetic rotary compressor according to claim 1, wherein the hermetic rotary compressor is a concave portion that changes. 8. The take-in portion is a space composed of the roller, the end plate, and an eccentric portion, and the holding portion is a recess provided in the end plate, the direction being perpendicular to the depth direction of the recess. The hermetic rotary compressor according to claim 1, wherein the hermetically sealed rotary compressor is a recess whose cross-sectional area changes. 9. The hermetic rotary compression system according to claim 1, wherein the intake portion is an opening having a shape along the inner peripheral direction of the roller, and the holding portion is a recess provided in the end plate. Machine. 10. A hermetic rotary compressor for compressing a working fluid sucked through a suction pipe by a driving force of an electric motor, a condenser for taking in and condensing the compressed working fluid through a discharge pipe, and a condenser for condensing the condenser. Expansion mechanism that adiabatically expands the working fluid, an evaporator that takes in the working fluid from the expansion mechanism, the target temperature is determined based on the information detected by the sensor, and the sealed rotary type is selected according to the target temperature. And a speed control circuit for controlling the rotation speed of the electric motor of the compressor, wherein the hermetic rotary compressor is an electric element including an electric motor in a hermetic container whose rotational speed changes based on the control of the speed control circuit. And a drive shaft having an eccentric part for transmitting the rotation of the electric motor, and a compression element for compressing the working fluid by the rotation of the eccentric part of the drive shaft. The compression element has both ends opened. A cylinder having a cylindrical inner peripheral surface,
A roller that fits into the eccentric portion of the drive shaft in the cylinder, a vane that partitions the inside of the cylinder into a suction chamber and a compression chamber due to the eccentric movement of the roller, an end plate that closes the opening of the cylinder, and the drive An oil supply mechanism for supplying lubricating oil into the roller via a shaft, an intake part for taking in the lubricating oil supplied to the inside of the roller, and an intake part for alternately communicating with the space inside the roller and the suction chamber A lubricating oil supply mechanism having a holding portion for holding the lubricating oil from the refrigeration system.