JP2006125365A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor capable of separating oil in return refrigerant gas without using an accumulator and preventing refrigerant gas from leaking from a minute clearance between a shaft hole of a supporting member and a rotary shaft in a compression element. <P>SOLUTION: A driving element 2 and the compression element 3 are arranged in a lower part and an upper part inside a sealed vessel 1, respectively. The rotary shaft 5 is fixed by passing through a rotor 6 of the driving element 2, an auxiliary rotary shaft 5a is coaxially fixed to its upper end, and an oil pump 20 is attached to a lower end part. The supporting member 7 of the compression element 3 is fixed to the sealed vessel 1, the inside of the sealed vessel 1 is divided into an upper part region on a high pressure side and a lower part region on a low pressure side, and a vane 11 is mounted through a coil spring 18. A compression space is provided in a central part of a cylinder 8, and a swash member 9 fixed to the auxiliary rotary shaft 5a at the same shaft axis is rotatably arranged. An upper end part of the auxiliary rotary shaft 5a does not pass through the supporting member 7. Refrigerant gas is supplied into the lower part region to separate oil, and high pressure refrigerant gas compressed in the compression space is discharged into the upper part region. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention is a hermetic compressor that compresses and discharges a fluid such as a refrigerant gas, and particularly has a compression member that rotates concentrically with a rotating shaft to compress the refrigerant gas or the like in a cylinder. It is about.

  Various types of compressors have been known in the past. Among them, a rotary compressor (rotary compressor) has a drive element and a compression element arranged in a hermetic container, and an electric motor in the drive element. The stator is energized to rotate the shaft of the rotor, the rotation shaft mounted on the rotor rotates the roller eccentrically in the cylinder of the compression element, and the vane that is always in contact with the outer peripheral surface of the roller causes the inside of the cylinder to It is divided into a low-pressure chamber and a high-pressure chamber. The refrigerant gas gas sucked into the low-pressure chamber is compressed and discharged into the sealed container, and the high-pressure refrigerant gas is discharged from the sealed container and supplied to the refrigerant circuit. (For example, Patent Document 1).

  In the conventional rotary compressor described above, an eccentric disc portion eccentric to the rotary shaft is provided in the vicinity of the end of the rotary shaft pivotally attached to the rotor of the drive element, and a roller is freely rotatable on the outer periphery of the eccentric disc portion. It is arranged. When the rotating shaft rotates as described above, the roller slides and rotates along the inner circumferential surface of the circular space (compression space) of the cylinder with the eccentric rotation of the eccentric disk portion, and the refrigerant gas in the cylinder is discharged. It is compressed while moving from the low pressure chamber to the high pressure chamber.

  In the rotary compressor having such a structure, an eccentric disk portion must be formed on the rotation shaft, and a roller must be rotatably provided on the outer periphery of the eccentric disk portion. In addition, the number of parts increases, which is one of the causes of cost increase. Further, since the roller rotates eccentrically via the eccentric disk portion, vibration and torque fluctuation tend to increase.

  In order to prevent deterioration in workability, increase in parts, and increase in vibration and torque fluctuation in the conventional rotary compressor, the combination of the eccentric disk portion and the roller of the rotary shaft is not used, but concentric with the rotary shaft. There is known a compressor in which a compression member is attached to a shaft and the refrigerant gas sucked by compressing the compression member in a compression space of a cylinder can be compressed (for example, Patent Document 2).

The compressor provided with the compression member that rotates concentrically with the rotation shaft uses an inclined plate as the compression member. In order to compress the refrigerant gas on both sides of the inclined plate, the suction refrigerant gas is injected into the compression space of the cylinder. It is necessary to provide two intake paths each for leading the intake path and for discharging the compressed refrigerant gas. Therefore, since the high pressure chamber and the low pressure chamber are adjacent to each other above and below the compression member, the difference between the high pressure and the low pressure becomes large, resulting in a problem of efficiency deterioration due to refrigerant leakage. In order to prevent this, the present applicant has developed a compressor in which the compression member is formed of a relatively thick member and the refrigerant gas is compressed on one side, and a patent application has been filed earlier (Japanese Patent Application No. 2004). -003142).
JP-A-6-307363 Japanese Patent Application No. 2004-003142

  The compressor according to the above-mentioned prior application can compress the refrigerant gas by providing a substantially cylindrical compression member on the concentric shaft with respect to the rotation shaft of the drive mechanism and forming an inclined surface on the upper surface of the compression member. In this way, the stator of the drive element is energized to rotate the rotor, and the compression member is rotated concentrically within the cylinder of the compression element by the rotation shaft pivotally attached to the rotor, and the inclined surface of the compression member is The cylinder is divided into a low-pressure chamber and a high-pressure chamber through vanes that are always in contact. The refrigerant gas sucked into the low-pressure chamber is compressed and discharged into the sealed container. Is discharged and supplied to the refrigerant circuit.

  In the compressor according to the prior application, the compression element is fixed to the hermetic container and supports the shaft that passes through the rotation shaft fixed to the rotor of the drive element, and is fixed to the support member to form a compression space. Cylinder and concentric shaft fixed to the rotating shaft, rotate in the compression space of the cylinder, and return to the top dead center through the bottom dead center that becomes the lowest from the top dead center when one surface makes a round around the rotating shaft. A compression member formed on a wave-shaped inclined surface, and a vane slot provided on the support member via a spring, and a tip is always in contact with the inclined surface of the compression member so that the inside of the compression space is a low pressure chamber and a high pressure chamber. And vanes.

  In this case, the return refrigerant gas from the refrigerant circuit is sucked into the compression space of the cylinder from the suction port through the passage provided in the compression element from the suction pipe attached to the sealed container, and thus is included in the return refrigerant gas. The oil is not separated and compressed in a mixed state of oil. When the refrigerant gas is compressed in a state where the oil is mixed, the compression efficiency is lowered and the performance of the compressor is lowered. In order to prevent such a situation, for example, the return refrigerant from the refrigerant gas is passed through an accumulator to separate the oil, and the refrigerant gas is supplied from the accumulator to the suction pipe. However, the accumulator must be attached to the side portion of the sealed container via the mounting bracket, and the accumulator and the suction pipe must be connected via the connection pipe, resulting in a problem of an increase in cost.

  In addition, the sliding portion of the compression element is pumped up by an oil pump from an oil reservoir provided at the inner bottom of the sealed container and supplied through the shaft hole of the rotating shaft. On the other hand, since the rotating shaft penetrates, there occurs a situation in which oil flows out from a slight gap between the shaft hole of the supporting member and the rotating shaft. When such a situation occurs, there is a problem that the refrigerant gas compressed in the compression space of the cylinder leaks from a slight gap between the shaft hole of the support member and the rotating shaft, thereby reducing the compression efficiency.

  The present invention has been made to solve the above-described problems, and can separate the oil in the return refrigerant gas without using an accumulator, and can rotate and rotate the shaft hole of the support member in the compression element. An object of the present invention is to provide a compressor in which refrigerant gas does not leak from a slight gap between the shaft.

  In order to achieve the above object, according to the compressor of claim 1 of the present invention, a driving element and a compression element driven by the driving element are arranged in a sealed container, and the compression element is the sealed container. A support member that pivotally supports a rotating shaft fixed to the rotor of the drive element, a cylinder that is fixed to the support member to form a compression space, a concentric shaft fixed to the rotation shaft, and a compression space of the cylinder A compression member formed on a substantially sinusoidal inclined surface that rotates inside and returns to the top dead center through the bottom dead center that is the lowest from the highest top dead center when one surface makes a round around the rotation axis; A vane slot that is attached to a vane slot provided in the support member via a spring, and has a tip that always abuts against an inclined surface of the compression member and divides the compression space into a low pressure chamber and a high pressure chamber; Inhaled fluid A compressor that compresses by a compression member and discharges from the high-pressure chamber, wherein the support member partitions the sealed container into a high-pressure side and a low-pressure side, and the fluid is supplied to the low-pressure side via a suction pipe A passage and a suction port for guiding the fluid to the low pressure chamber are provided in the compression element; a discharge port and a passage for guiding the fluid discharged from the high pressure chamber to the high pressure side are provided in the compression element; and The fluid is discharged to the outside through a discharge pipe.

  A compressor according to a second aspect of the present invention is the compressor according to the first aspect, wherein the compression element is disposed in an upper portion of the sealed container and the drive element is disposed in a lower portion, and is fixed to a rotor of the drive element. The rotating shaft has an extending portion extending downwardly rotatably supported by a sub-bearing member attached to the sealed container, and an oil pump is attached to the lower end of the extending portion. Oil is pumped up from an oil reservoir provided at the inner bottom of the hermetic container, and is supplied to the sliding portion of the compression element through the shaft hole of the rotary shaft, and the upper end of the rotary shaft is not in contact with the compression element. The shaft is supported in a penetrating state.

  According to the first aspect of the present invention, the inside of the sealed container is partitioned into the high pressure side and the low pressure side by the support member, and the return refrigerant (fluid) from the refrigerant circuit is supplied from the suction pipe to the low pressure side. . For this reason, most of the oil contained in the return refrigerant is separated on the low-pressure side of the sealed container, and the refrigerant gas containing almost no oil is compressed from the suction port through the passage provided in the compression element. Inhaled into the low pressure chamber of the space. Thereby, the compression efficiency of the refrigerant gas is remarkably improved, and the performance of the compressor can be enhanced. Further, since the inside of the low-pressure side of the sealed container has an oil separation function, an accumulator is not required, and attachment of the accumulator to the sealed container and connection between the accumulator and the suction pipe are not required. As a result, cost can be reduced.

  According to the second aspect of the present invention, the oil is pumped up from the oil reservoir provided in the inner bottom portion of the sealed container by the oil pump, and the oil is raised through the shaft hole of the rotating shaft, and the oil is put on the sliding portion of the compression element. However, since the upper end of the rotary shaft is pivotally supported in a non-penetrating state with respect to the compression element, the oil supplied to the sliding portion of the compression element is slightly spaced between the rotary shaft and the support member. Does not flow out from the outside. Thereby, the leak of the refrigerant gas compressed in the sealed space of the compression element can be suppressed, and the compression efficiency can be increased and the performance of the compressor can be improved.

[Example 1]
Next, a first embodiment of a compressor according to the present invention will be described with reference to the accompanying drawings. FIG. 1 is a schematic longitudinal sectional view through a vane portion in a first embodiment of a compressor according to the present invention. FIG. 2 is a schematic longitudinal sectional view passing through a suction portion in the first embodiment of the compressor according to the present invention. FIG. 3 is a schematic longitudinal sectional view passing through a discharge portion in the first embodiment of the compressor according to the present invention. FIG. 4 is a schematic cross-sectional view of the first embodiment of the compressor according to the present invention. In each figure, 1 is an iron sealed container, and includes a cylindrical body 1a, a cap 1b welded to the upper end of the body 1a, and a bottom 1c welded to the lower end of the body 1a. It is configured. A driving element 2 is disposed in the lower part of the sealed container 1, and a compression element 3 driven by the driving element 2 is disposed in the upper part.

  The drive element 2 includes an electric motor that includes a stator 4 fixed to the inner wall of the body 1 a of the hermetic container 1 and a rotor 6 disposed inside the stator 4. The rotary shaft 5 is pivotally attached to the part. A plurality of terminals 2a are mounted on the cap portion 1b of the hermetic container 1 via mounting members 2b. These terminals 2a and the stator 4 are connected by internal lead wires (not shown), and the terminals 2a are externally connected. An external lead wire (not shown) from the power source is connected to energize the stator 4. Note that a passage (not shown) through which the internal lead wire passes is provided in the outer peripheral portion of the compression element 3, and the terminal 2a and the mounting member 2b are omitted in FIGS. Further, a plurality of gaps 10 are formed between the outer peripheral portion of the stator 4 of the driving element 2 and the body portion 1 a of the sealed container 1.

  The compression element 3 includes a support member 7 fixed to the inner wall of the body 1 a of the sealed container 1, a cylinder 8 attached under the support member 7, and a main bearing member 13 attached under the cylinder 8. A compression member 9 (referred to as a swash member in the present embodiment) disposed in the cylinder 8, a substantially rectangular plate-like vane 11 mounted on the support member 7 so as to be movable up and down, It is comprised from the discharge valve 12 etc. which were attached to the side surface of the notch part 8b (FIG. 4).

  The support member 7 is composed of a first member R and a second member S. As shown in FIG. 2, a protrusion is formed in a concentric columnar shape at the center of the upper surface of the first member R, and a concentric columnar shape at the center of the lower surface. A recess 15 is formed inwardly, and the upper end of the second member S is fitted and fixed to the recess 15. Further, the first member R is provided with a non-penetrating first shaft hole 7a extending from the bottom surface of the recessed portion 15 to a position slightly below the upper surface of the projecting portion, and the second member S is provided with a first hole penetrating from the lower surface to the upper surface. A biaxial hole 7b is provided. The second axial hole 7b is coaxial with the first axial hole 7a and has an inner diameter that is the same as that of the first axial hole 7a.

  As shown in FIG. 1, a vane slot 16 and a spring mounting hole 17 are provided in the first member R and the second member S so as to communicate in the vertical direction, and the vane 11 is interposed via a coil spring 18. It is mounted so that it can move up and down. The coil spring 18 is inserted into the spring mounting hole 17, the lower end is fixed to the upper end portion of the vane 11, and the upper end is fixed to the spring receiving portion 14 above the spring mounting hole 17 to constantly bias the vane 11 downward. is doing. The inner end portion of the vane slot 16 opens into the first shaft hole 7a and the second shaft hole 7b.

  The rotary shaft 5 is rotatably supported by the main bearing member 13, and an auxiliary rotary shaft 5 a is coaxially fixed to the upper end, and this auxiliary rotary shaft 5 a is the first member R of the support member 7. The shaft hole 7a and the shaft hole 7b of the second member S are rotatably supported. The swash member 9 is coaxially fixed to the lower end portion of the auxiliary rotating shaft 5a. Further, the lower end portion of the rotating shaft 5 extends below the rotor 6, and the lower end of the extending portion is rotatably supported by a sub-bearing member 19 attached to the sealed container 1, and the extending portion An oil pump 20 is attached to the lower end of the cylinder. The oil pump 20 pumps up oil from an oil reservoir 21 provided at the inner bottom of the sealed container, and compresses the oil through the shaft hole of the rotating shaft 5 and the shaft hole of the auxiliary rotating shaft 5a. It is configured to be supplied to the sliding part of the element 3.

  As shown in FIG. 2, the cylinder 8 is provided with a space penetrating vertically in the central portion, and the upper end portion of the space is closed by the second member S of the support member 7 fitted therein. The compression space 22 is configured by the lower end portion being closed by the main bearing member 13. The swash member 9 is rotatably disposed in the compression space 22.

  The cylinder 8 is provided with a passage 8c. One end of the passage 8c opens into the sealed container 1, and the other end communicates with a suction port 7c provided in the second member S of the support member 7. The suction port 7 c opens into the compression space 22. A suction pipe 23 is fixed to the body portion 1 a of the sealed container 1, and the refrigerant gas supplied from the suction pipe 23 passes through the passage 8 c of the cylinder 8 and is compressed from the suction port 7 c of the second member S. 22 is sucked into.

  As shown in FIGS. 3 and 4, the lower end edge of the second member S of the support member 7 is provided with a discharge port 7d that passes from the lower surface side to the outer peripheral surface side. Opening to the compression space 22, the outer peripheral surface side communicates with a passage 8 a provided inside the cylinder 8, and this passage 8 a opens to a notch 8 b of the cylinder 8. The discharge valve 12 is attached to the side surface of the notch 8 b of the cylinder 8, and the passage 8 a is opened and closed by the discharge valve 12. As a result, the high-pressure refrigerant gas compressed in the compression space 22 passes through the passage 8a of the cylinder 8 from the discharge port 7d of the second member S in the support member 7, opens the discharge valve 12, and is discharged toward the notch 8b. The

  The first member R of the support member 7 is provided with a notch 7e corresponding to the notch 8b of the cylinder 8 as shown in FIG. 3, and a through hole that leads from the notch 7e to the upper region in the sealed container 1 is provided. 7f is provided. As a result, the high-pressure refrigerant gas discharged to the notch 8b of the cylinder 8 is discharged to the upper region in the sealed container 1 through the notch 7e and the through hole 7f of the first member R. Further, a partition plate 24 is attached to the lower end portion of the notch portion 8b of the cylinder 8, and the notch portion 8b of the cylinder 8, the notch portion 7e of the first member R, the partition plate 24, and the body portion 1a of the sealed container 1 are used. A muffler 25 is formed by the enclosed space. Therefore, the high-pressure refrigerant gas compressed in the compression space 22 is discharged into the muffler 25 by opening the discharge valve 12, and after being silenced, is discharged from the through hole 7f to the upper region in the sealed container 1. Will be.

  As shown in FIGS. 1 to 3, a discharge pipe 26 is attached to the upper end of the cap portion 1 b in the sealed container 1. As described above, the high-pressure refrigerant gas discharged to the upper region in the sealed container 1 is discharged from the discharge pipe 26 to the outside. The high-pressure refrigerant gas discharged from the discharge pipe 26 is supplied to a refrigerant circuit (not shown), and the refrigerant gas circulated through the refrigerant circuit and having a low pressure is returned from the suction pipe 23 to the compressor.

  The swash member 9 will be described in detail. As shown in FIGS. 5 and 6, the swash member 9 has a substantially cylindrical shape as a whole, and includes a thick part 9a on one side and a thin part 9b on the other side facing the thick part 9a. The upper surface 9c along the circumferential direction is formed as a continuous inclined surface that is high at the thick portion 9a and low at the thin portion 9b. The swash member 9 is fixed by axially attaching the auxiliary rotating shaft 5a to a shaft hole provided in the center. As the fixing means, for example, a fixing tool such as a pin can be used via a radial mounting hole 9d provided in the swash member 9.

  The upper surface 9c of the swash member 9 has a substantially sine wave shape that returns from the highest dead center P to the highest dead center Q through the lowest dead center Q when it makes a round in the circumferential direction around the auxiliary rotating shaft 5a. ing. The vertical cross section of the upper surface 9c passing through the auxiliary rotating shaft 5a is all horizontal (see FIG. 6) at the cut surface of any angle of 360 degrees, and the upper surface 9c and the lower surface of the second member S in the support member 7 The space is the compression space 22. The top dead center P of the swash member 9 is movably opposed to the lower surface of the second member S of the support member 7 via a slight clearance. This clearance is sealed by the oil enclosed in the sealed container 1.

  The vane 11 is located between the suction port 7c and the discharge port 7d. Although not shown, the lower end is formed in a cross-sectional R shape, and is always in contact with the upper surface 9c of the swash member 9, so that the compression space in the cylinder 8 is provided. 22 is divided into a low pressure chamber and a high pressure chamber. The coil spring 18 biases the vane 11 downward to hold the lower end ridge line portion of the vane 11 so as not to be separated from the upper surface 9 c of the swash member 9, and the vane 11 extends along the vane slot 16 of the support member 7. To control the smooth up and down movement.

  Further, a minute clearance is formed between the outer peripheral surface of the swash member 9 and the inner wall surface of the cylinder 8 constituting the sealed space 22, so that the swash member 9 is rotatable. The clearance between the outer peripheral surface of the swash member 9 and the inner wall surface of the cylinder 8 is also sealed with oil. This is for suppressing the leakage of the refrigerant gas. A concave groove 9e for fitting the seal member is provided on the outer peripheral surface of the swash member 9 along the circumferential direction, and the lower surface side of the swash member 9 corresponds to the thick portion 9b. An appropriately sized recess 9f (see FIG. 6) is provided. The concave portion 9f reduces the weight of the thick portion 9b to suppress fluctuations in the rotational torque of the swash member 9.

  In the above-described embodiment, the example in which the rotating shaft 5 and the auxiliary rotating shaft 5a are configured separately has been described. However, the rotating shaft 5 and the auxiliary rotating shaft 5a may be implemented with a single rotating shaft formed in advance. In addition, a predetermined amount of carbon dioxide, R134a, or HC-based refrigerant gas, for example, is sealed in the sealed container 1.

  The operation of the compressor according to the first embodiment configured as described above will be described. In this compressor, when the coil of the stator 4 of the drive element 2 is energized, the rotor 6 rotates, and the rotation of the rotor 6 is transmitted to the swash member 9 via the rotating shaft 5 and the auxiliary rotating shaft 5a. The refrigerant gas starts to be compressed by rotating in the compression space 22.

  In this case, the inside of the sealed container 1 is partitioned by the compression element 3 into an upper region above the compression element 3 and a lower region below the compression element 3. Since the compressed high-pressure refrigerant gas is discharged to the upper region as described above, a differential pressure is generated between the upper region and the lower region, and the upper region becomes the high-pressure side and the lower region becomes the low-pressure side.

  Since the refrigerant gas returned from the suction pipe 23 to the compressor is supplied to the lower region on the low pressure side in the hermetic container 1, the refrigerant gas is rapidly decompressed in this lower region and is contained in the refrigerant gas. Oil is separated. Thereby, since the lower area | region in the airtight container 1 exhibits the function of an accumulator, the accumulator normally used becomes unnecessary. Further, it is not necessary to attach the accumulator to the sealed container 1 and to connect the accumulator to the suction pipe 23. Therefore, cost can be reduced.

  The oil separated in the lower region in the hermetic container 1 falls on the sub-bearing member 19 through a slight gap 10 between the stator 4 and the rotor 6 in the driving element 2, and the sub-bearing member 19 It is returned to the oil sump 21 through the plurality of formed through holes 19a.

  The refrigerant gas from which the oil has been separated in the lower region in the sealed container 1 passes through the passage 8c of the cylinder 8 and is sucked into the compression space 22 from the suction port 7c of the second member S in the support member 7, and the swash member 9 Compressed by

  Here, the top dead center P of the upper surface 9c of the swash member 9 is on the discharge side with the vane 11 as a boundary, and the space surrounded by the cylinder 8, the support member 7, the swash member 9, and the vane 11 on the suction side (low pressure chamber) ) It is assumed that the refrigerant gas is sucked in. When the swash member 9 is rotated from this state, the volume of the low pressure chamber is reduced by the inclination of the upper surface 9c of the swash member 9 from the stage where the top dead center P passes the vane 11 and the suction port 7c, and the high pressure chamber is reduced. The refrigerant gas is compressed. The compressed high-pressure refrigerant gas is discharged from the discharge port 7d until the top dead center P passes through the discharge port 7d of the support member 7. After the top dead center P passes through the suction port 7c of the support member 7, the volume of the low-pressure chamber increases on the suction side, so that the refrigerant gas is sucked into the low-pressure chamber. Such an operation is repeatedly performed to compress the refrigerant gas.

  In the compression operation of the refrigerant gas, the oil pumped up from the oil reservoir 21 by the oil pump 20 ascends the shaft hole of the rotating shaft 5 and ascends the shaft hole of the auxiliary rotating shaft 5a. The oil is supplied to the sliding portion of the compression element 3 through an oil hole provided at a point of the auxiliary rotating shaft 5a. Thereby, the minute clearance between the auxiliary | assistant rotating shaft 5a and the 1st shaft hole 7a of the support member 7, and the 2nd shaft hole 7b is sealed with oil. Further, a minute clearance between the rotating shaft 5 and the main bearing member 13 is also sealed with oil.

  As described above, since the upper end of the auxiliary rotation shaft 5a is not penetrating the first member R of the support member 7, the auxiliary rotation shaft 5a and the first shaft hole 7a and the second shaft hole 7b of the support member 7 are arranged. The oil supplied to the minute clearance in the meantime does not rise and flow out from the upper end of the auxiliary rotating shaft 5a. Thereby, the minute clearance between the auxiliary rotating shaft 5a and the first shaft hole 7a and the second shaft hole 7b of the support member 7 is always sealed with oil and no gap is formed. Leakage of the refrigerant gas compressed at can be suppressed. As a result, it is possible to improve the compression performance of the compressor.

  The high-pressure refrigerant gas compressed in the compression space 22 of the cylinder 8 passes through the passage 8a of the cylinder 8 from the discharge port 7d of the second member S in the support member 7 as described above, opens the discharge valve 12, and becomes the muffler 25. Discharged. The high-pressure refrigerant gas silenced in the muffler 25 is discharged from the through hole 7f of the first member R in the support member 7 to the upper region of the hermetic container 1, and is discharged to the outside from the discharge pipe 26 to be a refrigerant circuit (not shown). To be supplied.

  In the above embodiment, the hermetic container 1 is partitioned by the support member 7 of the compression element 3 so that only the upper region has a high pressure and the lower region has a low pressure, that is, an internal low pressure type. For this reason, unlike the internal high-pressure type, it is not necessary to make the entire sealed container 1 high-pressure specification, and only the upper region on the high-pressure side (specifically, only the cap portion 1b) needs to be high-pressure specification. The lower region (specifically, the body portion 1a and the bottom portion 1c) may have a low pressure specification. Thereby, the cost of the airtight container 1 can be reduced.

[Example 2]
Next, 2nd Embodiment of the compressor based on this invention is described based on FIG. In the second embodiment, the members denoted by the same reference numerals as those in the first embodiment indicate substantially the same members although the same members or shapes are somewhat different. The compressor of the second embodiment has almost the same configuration as the compressor of the first embodiment, but is characterized by a configuration in which the support member and the cylinder are reversed upside down and the vane faces upward. .

  In FIG. 7, reference numeral 1 denotes an iron sealed container, which includes a cylindrical body 1a, a cap 1b welded to the upper end of the body 1a, and a bottom 1c welded to the lower end of the body 1a. It is configured. A driving element 2 is disposed in the lower part of the sealed container 1, and a compression element 3 driven by the driving element 2 is disposed in the upper part.

  The drive element 2 includes an electric motor that includes a stator 4 fixed to the inner wall of the body 1 a of the hermetic container 1 and a rotor 6 disposed inside the stator 4. The rotary shaft 5 is pivotally attached to the part. A plurality of terminals 2a are mounted on the cap portion 1b of the hermetic container 1 via mounting members 2b. These terminals 2a and the stator 4 are connected by internal lead wires (not shown), and the terminals 2a are externally connected. An external lead wire (not shown) from the power source is connected to energize the stator 4. Note that a passage (not shown) through which the internal lead wire passes is provided in the outer peripheral portion of the compression element 3. Further, a plurality of gaps are formed between the outer peripheral portion of the stator 4 of the driving element 2 and the body portion 1 a of the sealed container 1.

  The compression element 3 includes a support member 7 fixed to the inner wall of the body 1a of the sealed container 1, a cylinder 8 attached on the support member 7, and a swash member 9 disposed in the cylinder 8. The vane 11 has a substantially rectangular plate shape mounted on the support member 7 so as to be movable up and down, and a discharge valve or the like attached to the side surface of the notch portion of the cylinder 8 (not shown).

  The support member 7 is composed of a first member R and a second member S. A main bearing member 13 is formed in a concentric columnar shape at the center of the lower surface of the first member R, and a concentric columnar shape is formed at the center of the upper surface. A recessed portion 15 is formed by being recessed in the direction, and the lower end portion of the second member S is fitted and fixed to the recessed portion 15. The first member R is provided with a first shaft hole 7a penetrating from the bottom surface of the recessed portion 15 to the main bearing member 13, and the second member S is provided with a second shaft hole 7b penetrating from the upper surface to the lower surface. The second shaft hole 7b is coaxial with the first shaft hole 7a and has the same inner diameter and communicates therewith.

  A vane slot 16 and a spring mounting hole 17 are provided in the first member R and the second member S so as to communicate in the vertical direction, and the vane 11 is mounted via a coil spring 18 so as to be movable up and down. ing. The coil spring 18 is inserted into the spring mounting hole 17, the upper end is fixed to the lower end portion of the vane 11, and the lower end is fixed to the spring receiving portion 14 below the spring mounting hole 17 to constantly bias the vane 11 upward. is doing. The inner end portion of the vane slot 16 opens into the first shaft hole 7a and the second shaft hole 7b.

  The rotating shaft 5 is rotatably supported through the main bearing member 13, the first shaft hole 7 a and the second shaft hole 7 b of the support member 7, and the upper end portion is coaxially fixed to the swash member 9. Yes. Further, the lower end portion of the rotating shaft 5 extends below the rotor 6, and the lower end of the extending portion is rotatably supported by a sub-bearing member 19 attached to the sealed container 1, and the extending portion An oil pump 20 is attached to the lower end of the. The oil pump 20 is configured to pump oil from an oil reservoir 21 provided at the inner bottom of the hermetic container 1 and supply the oil to the sliding portion of the compression element 3.

  The cylinder 8 is provided with a space penetrating vertically in the central portion, and the lower end portion of the space is closed by fitting the second member S of the support member 7, and the upper end portion of the space is covered with a cover plate. The compression space is configured by being blocked by the member 27. The swash member 9 is rotatably arranged in the compression space.

  The cylinder 8 is provided with a passage 8c. One end of the passage 8c communicates with a passage 7g provided in the first member R of the support member 7, and the other end is provided in the second member S of the support member 7. It communicates with the suction port 7c. The passage 7g opens into the sealed container 1, and the suction port 7c opens into the compression space 22. Further, a suction pipe 23 is fixed to the body 1 a of the sealed container 1, and the refrigerant gas supplied from the suction pipe 23 flows into the lower region of the sealed container 1, and the first member in the support member 7. The air is sucked into the compression space 22 from the suction port 7c of the second member S through the passage 8g of the cylinder 8 from the passage 7g of R.

  Although not shown in the drawings, the upper end edge of the second member S of the support member 7 is provided with a discharge port that passes from the upper surface side to the outer peripheral surface side, and the upper surface side of the discharge port opens into the compression space, The surface side communicates with a passage provided inside the cylinder 8, and this passage opens in a notch portion of the cylinder 8. The discharge valve is attached to the side surface of the cutout portion of the cylinder 8, and the passage 8a of the cylinder 8 is opened and closed by the discharge valve. Thereby, the high-pressure refrigerant gas compressed in the compression space passes through the passage of the cylinder 8 from the discharge port of the second member S in the support member 7, opens the discharge valve, and is discharged to the notch portion side.

  Although not shown, a muffler is formed on the side of the compression element 3 as in the first embodiment, and the high-pressure refrigerant gas discharged to the notch side of the cylinder 8 is silenced by the muffler. After that, it is discharged from the through hole to the upper region in the sealed container 1.

  A discharge pipe 26 is attached to the upper end of the cap portion 1b in the closed container 1, and the high-pressure refrigerant gas discharged to the upper region in the closed container 1 as described above is discharged to the outside from the discharge pipe 26. To the refrigerant circuit (not shown). The refrigerant gas that has been circulated through the refrigerant circuit and has a low pressure is returned from the suction pipe 23 to the compressor.

  Since the main components of the swash member 9 are the same as those in the first embodiment, detailed description thereof will be omitted. In this case, a cylindrical protrusion 9g is provided at the center of the upper surface. The portion 9g is rotatably fitted to a receiving portion 27a provided at the center of the lower surface of the cover plate member 27. For this reason, the upper end part of the rotating shaft 5 is in a non-penetrating state with respect to the swash member 9. The protrusion 9 g of the swash member 9 is also non-penetrating with respect to the cover plate member 27, and the shaft hole of the protrusion 9 g communicates with the shaft hole of the rotating shaft 5.

  The operation of the compressor according to the second embodiment configured as described above will be described. Also in this compressor, the inside of the sealed container 1 is partitioned by the compression element 3 into an upper region above the compression element 3 and a lower region below the compression element 3. Since the compressed high-pressure refrigerant gas is discharged to the upper region as described above, a differential pressure is generated between the upper region and the lower region, and the upper region becomes the high-pressure side and the lower region becomes the low-pressure side.

  Since the refrigerant gas returned from the suction pipe 23 to the compressor is supplied to the lower region on the low pressure side in the sealed container 1, the oil contained in the refrigerant gas is separated. Thereby, since the lower area | region in the airtight container 1 exhibits the function of an accumulator, the accumulator normally used becomes unnecessary. Further, it is not necessary to attach the accumulator to the sealed container 1 and to connect the accumulator to the suction pipe 23. Therefore, cost can be reduced.

  The oil separated in the lower region in the hermetic container 1 falls on the auxiliary bearing member 19 through a slight gap between the stator 4 and the rotor 6 in the driving element 2 and is formed in the auxiliary bearing member 19. The plurality of through holes are returned to the oil sump 21.

  The refrigerant gas from which the oil has been separated in the lower region in the sealed container 1 is sucked into the compression space from the suction port 7c of the support member 7 through the passage 7g of the support member and the passage 8c of the cylinder 8, and the swash member 9 Compressed by The high-pressure refrigerant gas compressed in the compression space of the cylinder 8 passes through the passage of the cylinder 8 from the discharge port of the support member 7 as described above, and is discharged to the muffler by opening the discharge valve. The high-pressure refrigerant gas silenced in the muffler is discharged from the through hole to the upper region of the hermetic container 1, discharged from the discharge pipe 26 to the outside, and supplied to the refrigerant circuit.

  In such a refrigerant gas compressing operation, the oil pumped up from the oil reservoir 21 by the oil pump 20 ascends the shaft hole of the rotating shaft 5 and from the oil hole provided at the upper part of the rotating shaft 5. It is supplied to the sliding part of the compression element 3. Thereby, the minute clearance between the rotating shaft 5 and the first shaft hole 7a and the second shaft hole 7b of the support member 7 is sealed with oil. In addition, minute clearances between the rotating shaft 5 and the main bearing member 13 and between the protruding portion 9g of the swash member 9 and the receiving portion 27a of the cover plate member 27 are also sealed with oil.

  As described above, since the upper end of the rotating shaft 5a is not penetrating the swash member 9, the clearance between the rotating shaft 5a and the first shaft hole 7a and the second shaft hole 7b of the support member 7 is small. The supplied oil does not rise and flow out from the upper end of the rotating shaft 5. As a result, the minute clearance between the rotary shaft 5 and the first shaft hole 7a and the second shaft hole 7b of the support member 7 is always sealed with oil and no gap is formed. Leakage of the refrigerant gas that is generated can be suppressed. As a result, it is possible to improve the compression performance of the compressor. Further, since the protruding portion 9g of the swash member 9 is also non-penetrating with respect to the cover plate member 27, the oil supplied to the minute clearance between the protruding portion 9g and the receiving portion 27a is from the upper end of the protruding portion 9g. There is no leakage.

  In addition, although the said 1st Embodiment and 2nd Embodiment both demonstrated the vertical compressor, this invention is not limited to a vertical compressor, It can fully apply also to a horizontal compressor. Is possible. In the above embodiment, the compressor used for the refrigerant circuit of the refrigerator to compress the refrigerant gas has been described. However, the present invention is not limited to this, and the present invention is also effective for, for example, an air compressor that sucks and compresses air. Can be applied to.

  Especially this invention can be optimally utilized as a compressor for compressing refrigerant gas and supplying it to refrigerant circuits, such as a refrigerator.

It is a schematic longitudinal cross-sectional view which passes along the vane part in 1st Embodiment of the compressor which concerns on this invention. It is a schematic longitudinal cross-sectional view which passes along the suction part in 1st Embodiment of the compressor which concerns on this invention. It is a schematic longitudinal cross-sectional view which passes along the discharge part in 1st Embodiment of the compressor which concerns on this invention. 1 is a schematic cross-sectional view of a compressor according to a first embodiment of the present invention. It is a perspective view of the swash member in 1st Embodiment of the compressor which concerns on this invention. It is a side view of the swash member attached to the rotating shaft in 1st Embodiment of the compressor which concerns on this invention. It is a schematic longitudinal cross-sectional view in 2nd Embodiment of the compressor which concerns on this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Airtight container 2 Drive element 3 Compression element 4 Stator 5 Rotating shaft 5a Auxiliary rotating shaft 6 Rotor 7 Support member 7c Suction port 7d Discharge port 8 Cylinder 8a, 8c Passage 9 Swash member (compression member)
DESCRIPTION OF SYMBOLS 10 Clearance 11 Vane 12 Discharge valve 13 Main bearing member 14 Spring receiving part 15 Recessed part 16 Vane slot 17 Spring mounting hole 18 Coil spring 19 Sub bearing member 20 Oil pump 21 Oil reservoir 22 Compression space 23 Suction piping 24 Partition plate 25 Muffler 26 Discharge Piping 27 Cover plate member

Claims (2)

  A driving element and a compression element driven by the driving element are disposed in the sealed container, and the compression element is fixed to the sealed container and supports a rotation shaft fixed to the rotor of the driving element; A cylinder that is fixed to the support member to form a compression space, and a top dead center that is concentrically fixed to the rotation shaft and rotates in the compression space of the cylinder, and becomes highest when one surface makes a round around the rotation shaft. A compression member formed on an inclined surface having a substantially sinusoidal shape that returns to the top dead center after passing through the lowest bottom dead center, and a vane slot provided in the support member is attached via a spring, and a tip of the compression member A compressor that includes a vane that constantly contacts an inclined surface and divides the compression space into a low-pressure chamber and a high-pressure chamber, and compresses the fluid sucked into the low-pressure chamber by the compression member and discharges the fluid from the high-pressure chamber. Ah The support member partitions the sealed container into a high-pressure side and a low-pressure side, and the fluid is supplied to the low-pressure side via a suction pipe, and a passage and suction port for guiding the fluid to the low-pressure chamber serve as a compression element. A discharge port and a passage provided in the compression element for guiding the fluid discharged from the high-pressure chamber to the high-pressure side, and the high-pressure side fluid being discharged to the outside through a discharge pipe. Features compressor.   The compression element is disposed in the upper part of the sealed container, the drive element is disposed in the lower part, and the rotating shaft fixed to the rotor of the drive element is attached to the sealed container by the extending part extending downward. The sub-bearing member is rotatably supported, and an oil pump is attached to the lower end of the extending portion. The oil pump pumps oil from an oil reservoir provided at the inner bottom of the hermetic container. 2. The compression according to claim 1, wherein the compression element is configured to be supplied to a sliding portion of the compression element through a hole, and an upper end of the rotating shaft is pivotally supported in a non-penetrating state with respect to the compression element. Machine.

Images