JP2006097628A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor capable of increasing a reliability by improving the durability of a compression member and securing excellent sliding property even when a compression element is not lubricated. <P>SOLUTION: This compressor comprises a compression member 9 having one surface (upper surface 33) crossing the axial direction of the rotating shaft 5 continuously tilted between a top dead center 33A and a bottom dead center 33B, disposed in the cylinder 8 and rotatingly driven by the rotating shaft 5, and compressing a fluid (medium) sucked from the suction port 27 and discharging it from the discharge port 28, and a vane 11 disposed between the suction port 27 and the discharge port 28 and abutting on the upper surface 33 of the compression member 9 and dividing the compression space 21 in the cylinder 8 into a high pressure compartment LR and a low pressure compartment HR. A difference in hardness is given between the vane 11 and one surface (upper surface 33) of the compression member 9. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a compressor that compresses and discharges fluid such as refrigerant and air.

  Conventionally, for example, a refrigerator employs a method of compressing a refrigerant using a compressor and circulating the refrigerant in a circuit. As a compressor system in this case, there are a rotary compressor called a rotary compressor (see, for example, Patent Document 1), a scroll compressor, a screw compressor, and the like.

  Although the rotary compressor has an advantage that the structure is relatively simple and the production cost is low, there is a problem that vibration and torque fluctuation are increased. Moreover, although the scroll compressor and the screw compressor have small torque fluctuations, there is a problem that the processability is poor and the cost is increased.

Therefore, a system has been developed in which a swash plate is provided as a compression member that rotates in a cylinder, and a fluid is compressed by dividing a compression space formed above and below the swash plate with vanes (see, for example, Patent Document 2). .) According to the compressor of this type, there is an advantage that a compressor having a relatively simple structure and less vibration can be configured.
JP-A-5-99172 Special table 2003-532008 gazette

  However, in the case of the structure described in Patent Document 2, the high pressure chamber and the low pressure chamber are adjacent to each other above and below the compression member (swash plate) in the entire area of the cylinder. Deterioration becomes a problem.

  In addition, the cylinder and the compression member that rotates in the cylinder are made of the same material with the same treatment, and since they have the same hardness, they are easily worn by friction due to rotation. There was a problem of poor durability. Further, there is no so-called non-lubricated type compressor that does not use oil such as lubricating oil in the compressor having the structure as in Patent Document 2.

  The present invention has been made to solve the conventional technical problems, and an object of the present invention is to improve the durability of the compression member and improve the reliability of the compressor. It is another object of the present invention to provide a compressor that can ensure good slidability even when the compression element is not lubricated.

  The compressor according to the first aspect of the present invention intersects with the compression element composed of a cylinder having a compression space therein, the suction port and the discharge port communicating with the compression space in the cylinder, and the axial direction of the rotary shaft. One surface is continuously inclined between the top dead center and the bottom dead center, and is a compression member that is disposed in the cylinder and is rotationally driven by a rotating shaft to compress the fluid sucked from the suction port and discharge it from the discharge port. And a vane that is disposed between the suction port and the discharge port and abuts against one surface of the compression member and divides the compression space in the cylinder into a low pressure chamber and a high pressure chamber, and the compression element is non-lubricated, A compressor characterized by providing a hardness difference between the vane and one surface of the compression member.

  A compressor according to a second aspect of the present invention is the compressor according to the second aspect, wherein the vane is made of a carbon-based material, a ceramic-based material, a fluororesin-based material, or a polyether ether ketone-based material.

  According to a third aspect of the present invention, in the above-described invention, the hardness of one surface of the compression member is higher than that of the receiving surface at the top dead center.

  According to the compressor of the present invention, when the compression element is non-lubricated, a difference in hardness is provided between the vane and one surface of the compression member. In addition, by using a fluororesin-based material or a polyetheretherketone-based material, the wear resistance of the compression member and the vane is improved, and the durability can be increased.

  As a result, even when the compression element is unlubricated, it is possible to maintain good slidability and improve the reliability of the compressor.

  Further, if the hardness of one surface of the compression member is made higher than the receiving surface of the top dead center as in claim 3, the compression member is compressed even when the top dead center of the compression member contacts the receiving surface of the top dead center. One surface of the member is less likely to be worn, and the durability of the compression member can be further enhanced.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In addition, the compressor C of each Example demonstrated hereafter comprises the refrigerant circuit of a refrigerator, for example, plays the role which sucks in and compresses a refrigerant | coolant and discharges it in a circuit.

  1 is a longitudinal side view of a compressor C according to a first embodiment of the present invention, FIG. 2 is another longitudinal side view, FIG. 3 is a perspective view of a compression element 3 of the compressor C, and FIG. FIG. 5 is a plan view of the compression element 3 of the compressor C, and FIG. 6 is a bottom view of the compression element 3 of the compressor C. In each figure, 1 is an airtight container, and in this airtight container 1, the drive element 2 is accommodated in the upper side, and the compression element 3 driven by the rotating shaft 5 of this drive element 2 is accommodated in the lower side, respectively.

  The drive element 2 is fixed to the inner wall of the hermetic container 1 and is constituted by a stator 4 around which a stator coil is wound, and a rotor 6 having a rotation shaft 5 at the center inside the stator 4. It is a motor. Note that gaps 10 are formed between the outer periphery of the stator 4 of the drive element 2 and the sealed container 1 so as to communicate with each other vertically.

  The compression element 3 includes a support member 7 fixed to the inner wall of the hermetic container 1, a cylinder 8 attached to the lower side of the support member 7 with bolts, and a compression member 9 described later disposed in the cylinder 8. The vane 11, the discharge valve 12, and the auxiliary support member 22 attached to the lower side of the cylinder 8 with bolts. A central portion of the upper surface of the support member 7 projects concentrically upward, and a main bearing 13 of the rotary shaft 5 is formed there. Further, a concentric columnar projecting member 14 is fixed by a bolt at the center of the lower surface, and the lower surface 14A of the projecting member 14 is a smooth surface. That is, the support member 7 includes a main member 15 fixed to the inner wall of the sealed container 1, a main bearing 13 protruding above the main member 15, and a protruding member 14 fixed below the main member 15 with bolts. ing.

  A slot 16 is formed in the protruding member 14 of the support member 7, and the vane 11 is inserted into the slot 16 so as to be capable of reciprocating up and down. A back pressure chamber 17 for applying the high pressure in the sealed container 1 as a back pressure to the vane 11 is formed in the upper portion of the slot 16, and an urging force for pressing the upper surface of the vane 11 downward in the slot 16 is formed. A coil spring 18 is disposed as a means.

  The upper opening of the cylinder 8 is closed by the support member 7, whereby a compression space 21 is formed inside the cylinder 8 (inside the cylinder 8 between the compression member 9 and the protruding member 14 of the support member 7). Composed. In addition, a suction passage 24 is formed in the cylinder 8, and a suction pipe 26 is attached to the sealed container 1 and connected to the suction passage 24. The cylinder 8 is formed with a suction port 27 and a discharge port 28 that communicate with the compression space 21, the suction passage 24 communicates with the suction port 27, and the discharge port 28 communicates with the inside of the sealed container 1 at the side surface of the cylinder 8. is doing. The vane 11 is located between the suction port 27 and the discharge port 28.

  The rotating shaft 5 rotates while being supported by a main bearing 13 formed on the support member 7 and a sub-bearing 23 formed on the sub-support member 22. That is, the rotary shaft 5 is inserted through the center of the support member 7, the cylinder 8, and the sub support member 22, and the central portion in the vertical direction is rotatably supported by the main bearing 13, while the lower portion is the sub support member 22. The sub bearing 23 is rotatably supported. The compression member 9 is formed integrally with the lower portion of the rotating shaft 5 and is disposed in the cylinder 8.

  The above-described compression member 9 is disposed in the cylinder 8 as described above, is driven to rotate by the rotating shaft 5, compresses the fluid (in this embodiment, refrigerant) sucked from the suction port 27, and compresses the fluid from the discharge port 28. 1 as a whole, and has a substantially cylindrical shape concentric with the rotating shaft 5 as a whole. FIG. 7 is a side view of the rotary shaft 5 including the compression member 9 of the compressor C, and FIGS. 8 to 13 are perspective views of the compression member 9. As shown in FIGS. 7 to 13, the compression member 9 has a shape in which a thick portion 31 on one side and a thin portion 32 on the other side are continuous, and an upper surface 33 (crossing the axial direction of the rotary shaft 5). One surface) is high at the thick portion 31 and is low at the thin portion 32. That is, the upper surface 33 has a shape that continuously inclines between the top dead center 33A and the bottom dead center 33B that returns from the highest top dead center 33A to the top dead center 33B via the lowest bottom dead center 33B. Yes.

  The upper surface 33 of the compression member 9 includes first curved surfaces 34 and 34 having a predetermined range centered on an intermediate point 33C between the top dead center 33A and the bottom dead center 33B, and the top dead center 33A and the bottom dead center 33A. The second curved surface 35, 35 connecting the first curved surfaces 34, 34 through the point 33B.

  Here, the shape of the upper surface 33 of the compression member 9 will be described. FIG. 14 is a developed view of the line from the top dead center 33A to the bottom dead center 33B connecting the points 80 having the same distance from the center of the rotating shaft 5. FIG. As shown in FIG. 14, a line 80 connecting points having the same distance from the center of the rotation shaft 5 becomes a straight line 82 on the first curved surface 34, and a top dead center 33 </ b> A and a bottom dead center on the second curved surface 35. A curve 84 asymptotically approaches the point 33B. The line 80 connecting the points having the same distance from the center of the rotating shaft 5 becomes steeper as the distance from the center of the rotating shaft 5 is closer, and becomes gentler as the distance is further away. Are formed of a group of lines 80.

  The curve 84 has a sinusoidal shape (curve 84A) in the vicinity of the top dead center 33A and the bottom dead center 33B, and a curve 84B smoothly connecting the straight line 82 and the sinusoidal curve in the vicinity of the connection point with the straight line 82. It is said that. That is, the upper surface of the compression member 9 according to the present embodiment is from a sinusoidal curve 84A from 325 ° to 35 ° and 145 ° to 215 ° symmetrical to the rotation angle with the bottom dead center 33B being 0 °. The first curved surface 34 consisting of a straight line 82 at a symmetrical angle of 60 ° to 120 ° and 240 ° to 300 ° which is symmetrical to this, and 35 ° to 60 °, 120 ° to 145 °, and 215 ° connecting them. The range of ˜240 ° and 300 ° to 325 ° is constituted by a curved surface composed of a curve 84B that smoothly connects the sine wave shaped curve 84A and the straight line 82. In addition, the upper surface 33 of the compression member 9 of the present embodiment has a curved surface constituted by a sinusoidal curve 84A at 325 ° to 35 ° and 145 ° to 215 °, and 60 ° to 120 ° and 240 ° to 300 °. Is formed of the first curved surface 34 constituted by the straight line 82, but the present invention is not limited to the range of the rotation angle, and the center point 33C between the top dead center 33A and the bottom dead center 33B is the center. As long as the upper surface 33 of the compression member 9 is constituted by the second curved surface connecting the first curved surfaces 34, 34 through the first curved surface, the top dead center 33A and the bottom dead center 33B within the predetermined range. I do not care.

  The slope of the first curved surface 34 is steeper than the slope when the line 80 is a straight line over the entire range between the top dead center 33A and the bottom dead center 33B, and the top dead center 33A and the bottom dead center 33B. It is considered to be slower than the slope of the intermediate point when a sinusoidal curve is formed in the entire range between the two.

  As described above, the first curved surface 34 is configured so that the line 80 connecting the points having the same distance from the center of the rotation shaft 5 is a straight line, thereby easily processing the upper surface 33 of the compression member 9. This can be done, and the cost can be reduced. Further, the slope of the first curved surface 34 is made steeper than the slope when the line 80 is a straight line in the entire range between the top dead center 33A and the bottom dead center 33B, so that the top dead center 33A of the vane 11 and The movement near the bottom dead center 33B can be made smooth. Furthermore, the sliding loss due to the vane 11 can be reduced by making the slope slower than the slope of the intermediate point when the sinusoidal curve is formed in the entire range between the top dead center 33A and the bottom dead center 33B. it can. As a result, the performance of the compressor C can be improved and highly efficient compression can be realized.

  Further, the top dead center 33A of the compression member 9 faces the lower surface 14A of the protruding member 14 of the support member 7 so as to be movable through a minute clearance. Further, as described above, the vane 11 is disposed between the suction port 27 and the discharge port 28 and is in contact with the upper surface 33 of the compression member 9 so that the compression space 21 in the cylinder 8 is separated from the low pressure chamber LR and the high pressure chamber HR. Divide into and. The coil spring 18 always biases the vane 11 toward the upper surface 33 side.

  On the other hand, as shown in FIGS. 15 to 17, the bearing on the opposite side of the compression member 9 with respect to the auxiliary bearing 23 on the lower surface (other surface) side of the compression member 9, that is, on the upper surface 33 side of the compression member 9. A shaft seal 50 that contacts the rotary shaft 5 is provided at the end of the main bearing 13 that is a bearing. The shaft seal 50 is formed between the rotary shaft 5 and the support member 7 in contact with the rotary shaft 5 and the support portion formed by covering the iron plate with a rubber member such as an NBR material. The contact portion 52 is provided so as to seal the gap, and a spring member for urging the contact portion 52 inside (the rotation shaft 5) is attached to the contact portion 52. It is slidably in contact with. Further, the upper surface of the shaft seal 50 is closed by a cover 53 to prevent the shaft seal 50 from falling off (the shaft seal 50 and the cover 53 are not shown in FIGS. 1 and 2). The cover 53 is fixed to the upper surface of the support member 7 with bolts. By sealing the main bearing 13 with the shaft seal 50, the inner surface of the main bearing 13 can be sufficiently sealed to prevent gas leakage. In this way, it is possible to avoid inconvenience that the refrigerant gas in the compression space 21 leaks from the clearance of the main bearing 13 between the rotating shaft 5 and the support member 7, so that the volumetric efficiency can be improved. become. Thereby, the performance of the compressor 1 can be improved.

  The lower opening of the cylinder 8 is closed by a sub-support member 22, and a space 54 is formed between the lower surface (other surface) of the compression member 9 and the sub-support member 22 (the back side of the compression space 21). Yes. The space 54 communicates with the inside of the sealed container 1 through the pressure adjusting means 55. The pressure adjusting means 55 is formed in the sub-support member 22 in the axial direction, communicates with a hole 56 communicating with the lower surface of the compression member 9, and communicates with one end of the hole 56 and the outside of the sub-support member 22 from the hole 56. The other end of the communication hole 57 is inserted into the communication hole 57 that extends in the horizontal direction (on the closed container 1 side) and communicates with the inside of the closed container 1 and the other end of the communication hole 57 (the end that communicates with the inside of the sealed container 1). The nozzle member 58 has a minute passage (nozzle) formed in the center (FIG. 17).

  Due to the pressure adjusting means 55, the refrigerant in the sealed container 1 flows into the space 54. That is, the high-pressure refrigerant in the sealed container 1 flows in from the nozzle member 58 of the pressure adjusting means 55 and flows into the space 54 through the communication hole 57 and the hole 56. At this time, in the process of passing through the minute passage formed in the nozzle member 58, the refrigerant whose pressure is reduced flows into the space 54 due to the passage resistance of the minute passage. Thereby, the pressure in the space 54 on the lower surface side (other surface side) of the compression member 9 becomes a value lower than the pressure in the sealed container 1.

  Here, when the space 54 is set to a high pressure, the compression member 9 is strongly pressed toward the support member 7 by the pressure of the space 54, and the upper surface 33 of the compression member 9 and the lower surface 14 </ b> A of the projection member 14 serving as the receiving surface are formed. Friction occurs with the dead center 33A, and these wear out remarkably, resulting in a very poor durability. However, by setting the pressure in the space 54 to a value lower than the high pressure in the sealed container 1 by the pressure adjusting means 55 as in the present invention, the protruding member 14 whose top dead center 33A of the upper surface 33 of the compression member 9 is the receiving surface. The force pushed to the lower surface 14A side of the projection member 14 can be reduced, or a state with a slight clearance can be achieved without bringing the lower surface 14A of the protruding member 14 into contact with the top dead center 33A of the upper surface 33 of the compression member 9. become. Thereby, durability of the upper surface 33 of the compression member 9 can be improved, reliability can be improved, and mechanical loss can be reduced.

  The clearance between the top dead center 33A of the compression member 9 and the lower surface 14A of the projecting member 14 of the support member 7 is sealed with oil sealed in the sealed container 1 to avoid gas leakage. Can maintain high-efficiency operation.

  On the other hand, the hardness of the upper surface 33 (one surface) of the compression member 9 is set to be higher than the lower surface 14A of the protruding member 14 of the support member 7 as a receiving surface of the top dead center 33A. Here, FIG. 18 shows an example of the material and processing method of the members used for the upper surface 33 of the compression member 9 and the vane 11. As shown in FIG. 18, when a material obtained by nitriding high-speed tool steel material (SKH) is used as the vane 11, the rotary shaft 5 and the upper surface 33 of the compression member 9 are made of chromium molybdenum steel (SCM) or carbon steel. The surface of (for example, S45C or the like) that has been carburized and hardened, the one that has been induction hardened from chromium molybdenum steel or carbon steel, or gray cast iron (FC) or spheroidal graphite cast iron (FCD) is used. In this case, the hardness of the upper surface 33 (one surface) of the compression member 9 is lower than that of the vane 11.

  Moreover, when using what carried out the PVD process of the high-speed tool steel type material as the vane 11, the upper surface 33 of the rotating shaft 5 and the compression member 9 carburized and hardened the surface of the said chromium molybdenum steel or carbon steel, chromium The one obtained by induction hardening of molybdenum steel or carbon steel or one obtained by nitriding or quenching gray cast iron or spheroidal graphite cast iron in addition to gray cast iron or spheroidal graphite cast iron is used. Even in this case, the hardness of the upper surface 33 (one surface) of the compression member 9 is lower than that of the vane 11 as described above.

  Thus, by making the hardness of the upper surface 33 of the compression member 9 lower than that of the vane 11, the vane 11 is hardly worn. Thereby, durability of the vane 11 can be improved.

  Further, by making the hardness of the upper surface 33 of the compression member 9 higher than the lower surface 14A of the projecting member 14 as the receiving surface of the top dead center 33A of the compression member 9, the top dead center 33A is formed on the lower surface 14A of the projecting member 14. Even in the case of contact, the upper surface 33 of the compression member 9 is not easily worn, and the durability of the compression member 9 can be improved.

  Here, when the compression element 3 is not lubricated with oil such as lubricating oil and is not lubricated, the vane 11 and the upper surface 33 (one surface) of the compression member 9 are configured to have a hardness difference. That is, when the vane 11 is made of a carbon-based material as shown in FIG. 18, the surface of the rotary shaft 5 and the compression member 9 is carburized and hardened as the upper surface 33 of the rotary shaft 5 and the compression member 9, and the chromium molybdenum steel or carbon steel. These can be slid without being lubricated with oil or the like by using a material that has been induction-hardened or a material obtained by nitriding or quenching gray cast iron or spheroidal graphite cast iron. Also in this case, the hardness of the upper surface 33 (one surface) of the compression member 9 is lower than that of the vane 11.

  Similarly, when the vane 11 is composed of a ceramic material, the upper surface 33 of the rotating shaft 5 and the compression member 9 is carburized and quenched with the same ceramic material as the vane 11 or the surface of the above-described chromium molybdenum steel or carbon steel. If you use induction-hardened chromium-molybdenum steel or carbon steel, or nitriding or quenching gray cast iron or spheroidal graphite cast iron, in this case without lubricating the sliding part with oil, Can be slid. In this case, the hardness of the upper surface 33 (one surface) of the compression member 9 is lower than that of the vane 11.

  Further, when the vane 11 is made of a fluororesin-based material or a polyetheretherketone (PEEK) material of a polymer material, the surface of the rotating shaft 5 and the upper surface 33 of the compression member 9 is made of Al (aluminum) ( Alumite treated), the above-mentioned chromium molybdenum steel or carbon steel surface carburized and quenched, chromium molybdenum steel or carbon steel induction hardened, or gray cast iron or spheroidal graphite cast iron was nitrided or quenched In this case, the sliding portion can be slid without being lubricated with oil or the like as described above. In this case, the hardness of the upper surface 33 of the compression member 9 is higher than that of the vane 11.

  As described above, when the vane 11 is made of a carbon-based material, a ceramic-based material, a fluororesin-based material, or a polyether ether ketone, the upper surface 33 of the compression member 9 is subjected to the material and processing shown in FIG. When the vane 11 is made of a carbon-based material or a ceramic-based material, the hardness of the upper surface 33 of the compression member 9 is lower than the hardness of the vane 11 and is made of a fluororesin-based material or polyether ether ketone. In this case, the hardness of the upper surface 33 of the compression member 9 is higher than the hardness of the vane 11.

  In this way, the vane 11 is made of a carbon-based material, a ceramic-based material, a fluororesin-based material, or polyether ether ketone, and a hardness difference is generated between the upper surface 33 of the compression member 9 and the vane 11. By comprising in this, the abrasion resistance of the compression member 9 and the vane 11 improves, and it becomes possible to improve durability.

  Furthermore, by making the hardness of the upper surface 33 of the compression member 9 higher than the lower surface 14A of the projecting member 14 as a receiving surface of the top dead center 33A of the compression member 9, the top dead center 33A is formed on the lower surface 14A of the projecting member 14. Even in the case of contact, the upper surface 33 of the compression member 9 is not easily worn, and the durability of the compression member 9 can be improved.

  In particular, when the vane 11 is composed of the above-described carbon-based material, ceramic-based material, fluororesin-based material, or polyether ether ketone, the lubrication to the sliding portions such as the vane 11 and the compression member 9 is insufficient. In addition, good slidability can be maintained. That is, the sliding portion of the compression element 3 can be made unlubricated without being lubricated with oil. As a result, the compressor can be applied to a non-lubricated compressor, and versatility can be improved.

  Further, the circumferential surface of the compression member 9 forms a slight clearance with the inner wall of the cylinder 8, whereby the compression member 9 is rotatable. The space between the peripheral surface of the compression member 9 and the inner wall of the cylinder 8 is also sealed with oil.

The discharge valve 12 is attached to the outside of the discharge port 28 on the side surface of the compression space 21 of the cylinder 8, and the discharge pipe 37 is attached to the upper end of the sealed container 1. An oil sump 36 is formed in the lower part of the sealed container 1. An oil pump 40 is provided at the lower end of the rotating shaft 5, and one end is immersed in the oil reservoir 36. The oil sucked up by the oil pump 40 is an oil passage 42 formed in the center of the rotating shaft 5 and oil formed over the side surface of the compression element 3 in the axial direction of the rotating shaft 5 from the oil passage 42. It is supplied to the sliding portion of the compression element 3 through the holes 44 and 45. Further, a predetermined amount of, for example, CO ₂ (carbon dioxide), R-134a, or HC refrigerant is sealed in the sealed container 1.

  With the above configuration, when the stator coil of the stator 4 of the drive element 2 is energized, the rotor 6 rotates in the clockwise direction when viewed from below. The rotation of the rotor 6 is transmitted to the compression member 9 through the rotation shaft 5, and thereby the compression member 9 rotates in the clockwise direction in the cylinder 8 when viewed from below. Now, the top dead center 33 </ b> A of the upper surface 33 of the compression member 9 is on the vane 11 side of the discharge port 28, and the space surrounded by the cylinder 8, the support member 7, the compression member 9, and the vane 11 on the suction port 27 side of the vane 11. It is assumed that the refrigerant in the refrigerant circuit is sucked into the (low pressure chamber LR) from the suction port 27 through the suction pipe 26 and the suction passage 24.

  When the compression member 9 rotates from that state, the volume of the space is reduced by the inclination of the upper surface 33 from the stage where the top dead center 33A passes the vane 11 and the suction port 27, and the space (high pressure chamber) The refrigerant in HR) is compressed. The compressed refrigerant is continuously discharged from the discharge port 28 until the top dead center 33A passes through the discharge port 28. On the other hand, after the top dead center 33A passes through the suction port 27, the volume of the space (low pressure chamber LR) surrounded by the cylinder 8, the support member 7, the compression member 9, and the vane 11 on the suction port 27 side of the vane 11 is increased. Accordingly, the refrigerant in the refrigerant circuit is sucked into the compression space 21 from the suction port 27 through the suction pipe 26 and the suction passage 24.

  The refrigerant is discharged from the discharge port 28 into the sealed container 1 through the discharge valve 12. Then, the high-pressure refrigerant discharged into the sealed container 1 passes through the air gap between the stator 4 and the rotor 6 of the drive element 2, and oil and oil are passed through the upper part of the sealed container 1 (above the drive element 2). Separated and discharged from the discharge pipe 37 to the refrigerant circuit. On the other hand, the separated oil flows down from the gap 10 formed between the sealed container 1 and the stator 4 and returns to the oil reservoir 36.

  With such a configuration, the compressor C can exhibit a sufficient compression function while being small in size and simple in structure. In particular, the high pressure and the low pressure are not adjacent to each other in the entire area of the cylinder 8 as in the prior art, and the compression member 9 has a continuous thick portion 31 and a thin portion 32 and an upper surface 33 (one surface) is inclined. As a result, it is possible to sufficiently secure the seal dimension between the thick wall portion 32 corresponding to the high pressure chamber HR and the inner wall of the cylinder 8.

  As a result, the occurrence of refrigerant leakage between the compression member 9 and the cylinder 8 can be effectively prevented, and efficient operation becomes possible. Moreover, since the thick part 31 of the compression member 9 plays the role of a flyhole, torque fluctuation is also reduced. Further, since the compressor C is a so-called internal high-pressure type compressor, the structure can be further simplified.

  Further, since the slot 16 of the vane 11 is formed in the support member 7 (the projecting member 14 of the support member 7) and the coil spring 18 is provided in the support member 7, a vane mounting structure is required for the cylinder 8 that requires high accuracy. This eliminates the need to form the film and improves the workability. Furthermore, if the compression member 9 is formed integrally with the rotary shaft 5 as in the embodiment, the number of parts can be reduced.

  In this embodiment, the space 56 and the closed container 1 are communicated with the lower support member 22 in the axial direction communicating with the lower surface of the compression member 9, and the hole 56 and one end communicate with each other. A communication hole 57 extending horizontally from the hole 56 to the outside of the auxiliary support member 22 and having the other end communicating with the inside of the sealed container 1 is inserted into the other end of the communication hole 57, and a minute passage is formed at the center. The pressure is adjusted by allowing the high-pressure refrigerant in the sealed container 1 to pass through a minute passage formed in the nozzle member 58 through the pressure adjusting means 55 configured by the nozzle member 58 in which the (nozzle) is formed. The pressure in the space 54 on the lower surface side of the compression member 9 is set to a value lower than the pressure in the sealed container 1, but the pressure adjusting means is not limited to this. The space 54 and the inside of the sealed container 1 through a hole penetrating 22 in the axial direction The communicated, it may be as to insert the nozzle member small passage in the center an opening (nozzle) is formed of the closed casing 1 side.

  In the first embodiment, a shaft seal 50 is provided at the end of the main bearing 13 which is the bearing opposite to the compression member 9, and the refrigerant gas in the compression space 21 is between the rotary shaft 5 and the support member 7. Although the problem of leaking from the clearance of the bearing 13 is avoided in advance, the present invention is not limited to this, and a piston ring seal may be provided on the rotary shaft 5 at a position corresponding to the bearing.

  19 and 20 are examples of the compressor C in this case, FIG. 19 is a longitudinal side view of the rotary shaft 5 and the compression element 3, and FIG. 20 is a rotary shaft 5 with the cylinder 8 attached thereto. The perspective view of each is shown. As shown in FIGS. 19 and 20, a bearing on the opposite side of the compression member 9 with respect to the sub-bearing 23 on the lower surface (other surface) side of the compression member 9, that is, a bearing on the upper surface 33 side of the compression member 9. A groove 61 is formed on the outer peripheral surface of the rotary shaft 5 at a position corresponding to an end of a certain main bearing 13, and the piston ring seal 60 is attached in the groove 61. The piston ring seal 60 has a ring shape having a width of about 3 mm to 10 mm, and is made of a material excellent in stretchability and durability, such as a rubber member. The width of the piston ring 60 is set to be equal to or less than the depth (width) of the groove 61 (the piston ring seal 60 of the embodiment has a width of about 3 mm to 10 mm). That is, since the outer diameter of the piston ring 60 is set to be equal to or smaller than the outer diameter of the rotating shaft 5, when the piston ring 60 is mounted in the groove 61, the outer peripheral edge of the piston ring 60 extends from the outer peripheral surface of the rotating shaft 5. It is stored without protruding.

  When the compressor C is activated and the inside of the sealed container 1 becomes high pressure, the piston ring seal 60 is pushed downward and expanded (pushed outward) by the high pressure inside the sealed container 1 applied from above. Therefore, the gap between the support member 7 and the rotating shaft 5 is sufficiently sealed by the piston ring seal 60.

  As described above, the piston ring seal 60 sufficiently seals the inner surface of the main bearing 13, and the refrigerant gas in the compression space 21 leaks from the clearance of the main bearing 13 between the rotating shaft 5 and the support member 7. Therefore, it is possible to reduce the sliding loss at the end of the main bearing 13 and to simultaneously improve the volumetric efficiency by improving the sealing performance. Thereby, the performance of the compressor C can be improved.

  In this embodiment, one piston ring seal 60 is provided at a position corresponding to the main bearing 13. However, the installation position of the piston ring seal 60 is not limited to the above, and the rotary shaft 5 corresponding to the sub bearing 23 is provided. It does not matter even if it is attached to. A plurality of piston ring seals 60 may be used. As a result, the sealing performance between the rotary shaft 5 and the main bearing 13 or between the rotary shaft 5 and the auxiliary bearing 23 can be further improved, and a high-performance compressor can be provided.

  Next, a third embodiment of the present invention will be described with reference to FIGS. 21 is a longitudinal sectional view of the compressor C in this case, FIG. 22 is another longitudinal sectional view of the compressor C, and FIG. 23 is still another longitudinal side view of the compressor C. In FIG. 21 to FIG. 23, the same reference numerals as those shown in FIG. 1 to FIG. 20 have the same or similar effects.

  In the present embodiment, the hermetic container 1 houses the compression element 3 on the upper side and the driving element 2 on the lower side. That is, in this embodiment, the compression element 3 is disposed on the upper side of the drive element 2.

  The driving element 2 is fixed to the inner wall of the hermetic container 1 as in the above embodiment, and the stator 4 around which the stator coil is wound, and the rotor 6 having the rotation shaft 5 in the center inside the stator 4. It is an electric motor comprised by this.

  The compression element 3 is fixed to the inner wall of the hermetic container 1, a support member 77 located on the upper end side of the rotary shaft 5, a cylinder 78 attached to the lower side of the support member 77 with bolts, and the cylinder 78 The compression member 89 is disposed, and the vane 11, the discharge valve 12, the main support member 79 attached to the lower side of the cylinder 78 with a bolt, and the like. A central portion of the lower surface of the main support member 79 projects concentrically downward, and the main bearing 13 of the rotating shaft 5 is formed there. Further, the upper surface of the main support member 79 closes the lower opening of the cylinder 78.

  The support member 77 is fixed to the main member 85 whose outer peripheral surface is fixed to the inner wall of the hermetic container 1, the auxiliary bearing 83 formed through the center of the main member 85, and the lower surface central portion of the main member 85 with bolts. The lower surface 84A of the protruding member 84 is a smooth surface.

  A slot 16 is formed in the protruding member 84 of the support member 77, and the vane 11 is inserted into the slot 16 so as to be able to reciprocate up and down. A back pressure chamber 17 is formed at the upper portion of the slot 16, and a coil spring 18 is disposed in the slot 16 as an urging means for pressing the upper surface of the vane 11 downward.

  Then, the upper opening of the cylinder 78 is closed by the support member 77, whereby the compression space 21 is formed inside the cylinder 78 (between the compression member 89 in the cylinder 78 and the protruding member 84 of the support member 77). The A suction passage 24 is formed in the main member 85 and the protruding member 84 of the support member 77, and a suction pipe 26 is attached to the sealed container 1 and connected to one end of the suction passage 24. The cylinder 78 is formed with a suction port and a discharge port that communicate with the compression space 21, and the other end of the suction passage 24 communicates with the suction port. The vane 11 is located between the suction port and the discharge port.

  The rotary shaft 5 is supported and rotated by a main bearing 13 formed on the main support member 79, a sub bearing 83 formed on the support member 77, and a sub bearing 86 formed on the lower end. That is, the rotary shaft 5 is inserted through the center of the main support member 79, the cylinder 78, and the support member 77, and the central portion in the vertical direction is rotatably supported by the main bearing 13. Further, the upper portion of the rotating shaft 5 is rotatably supported by the auxiliary bearing 83 and the upper end is covered by the support member 77. Further, the lower side of the rotary shaft 5 is pivotally supported by the auxiliary bearing 86. The sub-bearing 86 is provided on the lower side of the driving element 2 and has a substantially donut shape having a hole for inserting the rotation shaft 5 in the center, and the outer peripheral edge stands up in the axial direction. It is fixed to the inner wall of the sealed container 1. The sub-bearing 86 is formed with holes 87 that communicate with each other vertically. Further, the convex portion 88 formed on the sub-bearing 86 has a vibration absorbing action that prevents vibration transmitted from the driving element 2 and the like to the rotating shaft 5 from being transmitted to the sealed container 1 via the sub-bearing 86. .

  Thus, by providing the bearings of the rotary shaft 5 on the upper side (sub bearing 83) and lower side (main bearing 13) of the compression element 3, and on the lower side (sub bearing 86) of the drive element 2, the rotary shaft 5 is provided. The vibration generated in the compressor C can be effectively reduced by supporting stably. As a result, the vibration characteristics of the compressor C can be improved.

  Further, by disposing the compression space 21 on the upper surface 93 of the compression member 89 on the side opposite to the driving element 2 as in the present embodiment, it is difficult for gas leakage from the main bearing 13 to occur, and the sealing performance of the main bearing 13 is improved. Can be increased. Further, by closing the upper end of the rotating shaft 5 with the support member 77, the sealing performance of the auxiliary bearing 83 can be improved, and the disadvantage that the peripheral surface of the rotating shaft 5 becomes high pressure can be avoided. .

  Conventionally, when the compression element 3 is arranged on the upper side of the sealed container 1, it has been difficult to supply the oil in the oil reservoir 36 in the lower part of the sealed container 1 to the sliding portion such as the compression member 89 of the compression element 3.

  That is, since the high pressure gas enters the peripheral surface of the rotating shaft 5 and becomes high pressure, the oil supply from the oil holes 44 and 45 provided above the rotating shaft 5 cannot be performed smoothly.

  However, by closing the upper end of the rotating shaft 5 with the support member 77, the sealing performance of the auxiliary bearing 83 can be improved, and the disadvantage that the peripheral surface of the rotating shaft 5 becomes high pressure can be improved. As a result, oil can be supplied to the sliding portion such as the compression member 89 provided on the upper side of the hermetic container 1, and the oil supply amount can be optimized.

  The compression member 89 is formed integrally with the upper portion of the rotating shaft 5 and is disposed in the cylinder 78. The compression member 89 is rotationally driven by the rotary shaft 5 and compresses the fluid (refrigerant) sucked from the suction port and discharges it into the sealed container 1 from the discharge port. Concentric and substantially cylindrical.

  Further, the upper surface 93 (one surface) that intersects the axial direction of the rotation shaft 5 of the compression member 89 passes from the highest dead center to the lowest dead center after returning from the lowest dead center to the bottom dead center. It has a continuously inclined shape.

  One surface of the compression member 89 having a continuously inclined shape is disposed on an upper surface 93 which is a surface opposite to the driving element 2 housed in the lower side of the sealed container 1 of the compression member 89.

  In addition, since the shape of the upper surface 93 of the compression member 89 is the same as the upper surface 33 of the compression member 9 of Example 1, description is abbreviate | omitted. Similarly, the hardness of the upper surface 93 (one surface) of the compression member 89 is set to be higher than the lower surface 84A of the protruding member 84 of the support member 77 as a receiving surface of the top dead center 33A. Further, the material and processing method of the upper surface 93 of the compression member 89 and the vane 11 are the same as those described in the first embodiment (see FIG. 18). Thereby, the durability of the compression member 89 and the vane 11 can be improved as in the above embodiment.

  In particular, when the vane 11 is made of a carbon-based material, a ceramic-based material, a fluororesin-based material, or a polyether ether ketone, the upper surface 93 of the compression member 89 is compressed by applying the material and processing shown in FIG. A difference in hardness occurs between the upper surface 93 of the member 89 and the vane 11, and good slidability is maintained even when lubrication to the sliding portion is insufficient or the compression element 3 is not lubricated. Will be able to.

  On the other hand, the vane 11 is disposed between the suction port and the discharge port and abuts on the upper surface 93 of the compression member 89 to partition the compression space 21 in the cylinder 78 into a low pressure chamber and a high pressure chamber. Further, the coil spring 18 constantly biases the vane 11 toward the upper surface 93 side.

  The lower opening of the cylinder 78 is closed by a main support member 79, and a space 54 is formed between the lower surface (other surface) of the compression member 89 and the main support member 79 (the back side of the compression space 21). The space 54 is a space sealed by the compression member 89 and the main support member 79. Since the refrigerant in the compression space 21 slightly flows into the space 54 from the clearance between the compression member 89 and the cylinder 78, the pressure in the space 54 is higher than the low-pressure refrigerant sucked into the suction port, and the sealed container 1 It becomes a value (intermediate pressure) lower than the pressure of the internal high-pressure refrigerant.

  Thus, by setting the pressure in the space 54 to an intermediate pressure, the compression member 89 is strongly pushed upward by the pressure in the space 54, and the lower surface 84 of the protruding member 84 whose upper surface 93 of the compression member 89 serves as a receiving surface, Can avoid the inconvenience of wear. Thereby, durability of the upper surface 93 of the compression member 89 can be improved.

  Furthermore, since the pressure in the space 54 on the other surface side of the compression member 89 is set to an intermediate pressure, the pressure in the space 54 becomes lower than the pressure in the sealed container 1. The oil can be smoothly supplied to the vicinity of the compression member 89 and the vicinity of the main bearing 13 as the peripheral portion.

  On the other hand, the above-described back pressure chamber 17 does not have a high pressure as in the prior art, and the pressure in the back pressure chamber 17 is higher than the pressure of the refrigerant (refrigerant) sucked into the suction port as a sealed space, The value is lower than the pressure. Conventionally, a part of the back pressure chamber 17 and the inside of the sealed container 1 are communicated to make the inside of the back pressure chamber 17 high, and the vane 11 is urged downward in addition to the coil spring 18. However, in this embodiment, since the compression element 3 is located above the hermetic container 1, there is a possibility that the oil supply to the vicinity of the vane 11 may be insufficient by setting the back pressure chamber 17 to a high pressure.

  Here, by making the back pressure chamber 17 a sealed space without communicating with the inside of the sealed container 1, the back pressure chamber 17 is connected to the low pressure chamber side and the high pressure chamber side of the compression space 21 from the gap of the vane 11. Only a small amount of refrigerant flows in. For this reason, the back pressure chamber 17 has an intermediate pressure that is higher than the pressure of the refrigerant sucked into the suction port and lower than the pressure in the sealed container 1. As a result, the pressure in the back pressure chamber 17 is lower than that in the sealed container 1, and the oil passage 42 in the rotating shaft 5 is lifted using the pressure difference, and the oil from the oil holes 44 and 45 is used. Can also be supplied to the periphery of the vane 11.

  As a result, even when the compression element 3 is provided on the upper side in the sealed container 1, lubrication to the sliding portions such as the compression member 89 and the vane 11 can be smoothly performed, and the reliability of the compressor C is improved. Will be able to.

  Further, a minute clearance is formed between the peripheral surface of the compression member 89 and the inner wall of the cylinder 78, whereby the compression member 89 is rotatable. The space between the peripheral surface of the compression member 89 and the inner wall of the cylinder 78 is also sealed with oil.

  The discharge valve 12 is mounted outside the discharge port on the side surface of the compression space 21 of the cylinder 78, and the cylinder 78 and the support member 77 are connected to the discharge valve 12 and the upper side in the sealed container 1. A communicating discharge pipe 95 is formed. Then, the refrigerant compressed in the cylinder 78 is discharged from the discharge port to the upper part in the sealed container 1 through the discharge valve 12 and the discharge pipe 95.

A communication hole 120 that penetrates the cylinder 78 and the support member 77 in the axial direction (vertical direction) is formed at a position of the cylinder 78 and the support member 77 that is substantially symmetrical with respect to the discharge valve 12. A discharge pipe 38 is attached to a position corresponding to the lower part of the communication hole 120 on the side surface of the sealed container 1. As described above, the refrigerant discharged from the discharge pipe 95 to the upper portion of the sealed container 1 passes through the communication hole 120 and is discharged from the discharge pipe 38 to the outside of the compressor C. An oil pump 40 is provided at the lower end of the rotary shaft 5, and one end is immersed in the oil reservoir 36 at the lower part in the sealed container 1. The oil sucked up by the oil pump 40 is an oil passage 42 formed in the center of the rotating shaft 5 and oil formed over the side surface of the compression element 3 in the axial direction of the rotating shaft 5 from the oil passage 42. It is supplied to the sliding portion of the compression element 3 through the holes 44 and 45. Further, a predetermined amount of, for example, CO ₂ (carbon dioxide), R-134a, or HC refrigerant is sealed in the sealed container 1.

  With the above configuration, when the stator coil of the stator 4 of the drive element 2 is energized, the rotor 6 rotates in the clockwise direction when viewed from below. The rotation of the rotor 6 is transmitted to the compression member 89 via the rotation shaft 5, and thereby the compression member 89 rotates in the clockwise direction in the cylinder 78 as viewed from below. Now, the top dead center (not shown) of the upper surface 93 of the compression member 89 is on the vane 11 side of the discharge port, and is surrounded by the cylinder 78, the support member 77, the compression member 89, and the vane 11 on the suction port side of the vane 11. It is assumed that the refrigerant in the refrigerant circuit is sucked into the space (low pressure chamber) from the suction port via the suction pipe 26 and the suction passage 24.

  Then, when the compression member 89 rotates from that state, the volume of the space is reduced by the inclination of the upper surface 93 from the stage where the top dead center passes the vane 11 and the suction port, and the inside of the space (high pressure chamber) is reduced. The refrigerant is compressed. The compressed refrigerant is continuously discharged from the discharge port until the top dead center passes through the discharge port. On the other hand, after the top dead center passes through the suction port, the volume of the space (low pressure chamber) surrounded by the cylinder 78, the support member 79, the compression member 89, and the vane 11 on the suction port side of the vane 11 increases. The refrigerant in the refrigerant circuit is sucked into the compression space 21 from the suction port via the suction pipe 26 and the suction passage 24.

  From the discharge port, the refrigerant is discharged into the upper portion of the sealed container 1 through the discharge valve 12 and the discharge pipe 95. The high-pressure refrigerant discharged into the sealed container 1 passes through the upper part of the sealed container 1 and is discharged to the refrigerant circuit from the discharge pipe 38 through the communication hole 120 formed in the support member 77 and the cylinder 78. On the other hand, the separated oil flows down through the communication hole 120 and further flows between the sealed container 1 and the stator 4 and returns to the oil reservoir 36.

  In the embodiment, the back pressure chamber 17 is a sealed space, so that the pressure of the back pressure chamber 17 applied as the back pressure of the vane 11 is higher than the pressure of the refrigerant sucked into the suction port, and the pressure in the sealed container 1 is increased. Although the lower value is set, the present invention is not limited to the case where the back pressure chamber 17 is used as a sealed space as described above. For example, the back pressure chamber 17 and the inside of the sealed container 1 may be communicated with each other through a fine passage (nozzle). Absent. In this case, since the refrigerant in the sealed container 1 flows into the back pressure chamber 17 through the nozzle, the pressure of the refrigerant decreases in the process of passing through the nozzle. As a result, the back pressure chamber 17 has a value higher than the pressure of the refrigerant sucked into the suction port and lower than the pressure in the sealed container 1, so that the oil supply to the peripheral portion of the vane 11 is smoothly performed using the pressure difference. Will be able to do. Further, the pressure of the refrigerant flowing into the back pressure chamber 17 can be freely set by adjusting the nozzle diameter.

  Further, the space 54 on the other surface side of the compression member 89 is also a sealed space, like the back pressure chamber 17, and the pressure of the space 54 is higher than that of the low-pressure refrigerant sucked into the suction port, and higher than the pressure of the high-pressure refrigerant in the sealed container 1. Although the intermediate pressure is low, the space 54 may be communicated with the inside of the sealed container 1 by a fine passage (nozzle). In this case, since the refrigerant in the sealed container 1 flows into the space 54 through the nozzle, the pressure of the refrigerant decreases in the process of passing through the nozzle. As a result, the pressure in the space 54 is higher than the pressure of the refrigerant sucked into the suction port and lower than the pressure in the sealed container 1, so that the upper surface 93 of the compression member 89 is significantly lower than the lower surface 84 of the projecting member 84 serving as the receiving surface. The inconvenience of wearing can be avoided. Thereby, durability of the upper surface 93 of the compression member 89 can be improved. Furthermore, by making the space 54 have such an intermediate pressure, it is possible to smoothly supply oil to the vicinity of the compression member 89 and the main bearing 13 that are the periphery of the space 54 by utilizing the pressure difference. Further, the pressure of the refrigerant flowing into the space 54 can be freely set by adjusting the nozzle diameter.

  Next, a fourth embodiment of the present invention will be described with reference to FIGS. 24 to 26 are longitudinal side views of the compressor C in this case, and each drawing shows a different cross section. In FIG. 24 to FIG. 26, the same reference numerals as those shown in FIG. 1 to FIG. 23 have the same or similar effects, and the description thereof will be omitted.

  In the present embodiment, in the hermetic container 1, the driving element 2 is accommodated on the upper side, and the compression element 3 is accommodated on the lower side. That is, the compression element 3 is arranged below the drive element 2.

  The compression element 3 includes a main support member 107 fixed to the inner wall of the hermetic container 1, a cylinder 108 attached by bolts to the lower side of the main support member 107, and a compression member 109 disposed in the cylinder 108. , The vane 11, the discharge valve 12, and the auxiliary support member 110 attached to the lower side of the cylinder 108 with bolts. The central portion of the upper surface of the main support member 107 projects upward concentrically, and the main bearing 13 of the rotary shaft 5 is formed there. Further, the outer peripheral edge rises in the axial direction (upward direction), and the raised outer peripheral edge is fixed to the inner wall of the sealed container 1 as described above.

  Then, the upper opening of the cylinder 108 is closed by the main support member 107, so that the space between the upper surface (other surface) of the compression member 109 provided in the cylinder 108 and the main support member 107 (other surface of the compression member 109). The closed space 115 closed by the compression member 109 and the main support member 107 is formed on the side).

  The sub-support member 110 includes a main body, a sub-bearing 23 formed through the center of the main body, and a projecting member 112 fixed to the center of the upper surface with a bolt. An upper surface 112A of the projecting member 112 has a smooth surface. Has been.

  Further, the lower opening of the cylinder 108 is closed by the protruding member 112 of the sub-supporting member 110, thereby compressing the inside of the cylinder 108 (inside the cylinder 108 between the compression member 109 and the protruding member 112 of the sub-supporting member 110). A space 21 is formed.

  A slot 16 is formed in the protruding member 112 of the sub-support member 110, and the vane 11 is inserted into the slot 16 so as to be capable of reciprocating up and down. A back pressure chamber 17 is formed at the lower portion of the slot 16, and a coil spring 18 is disposed in the slot 16 as an urging means for pressing the lower surface of the vane 11 upward.

  A suction passage 24 is formed in the cylinder 108 and the protruding member 112 of the sub-support member 110, and a suction pipe (not shown) is attached to the sealed container 1 and connected to one end of the suction passage 24. The cylinder 108 is formed with a suction port and a discharge port that communicate with the compression space 21, and the other end of the suction passage 24 communicates with the suction port. The vane 11 is located between the suction port and the discharge port.

  The rotation shaft 5 is supported by the main bearing 13 formed on the main support member 107 and the sub bearing 23 formed on the sub support member 110 and rotates. That is, the rotary shaft 5 is inserted through the center of the support member 107, the cylinder 108, and the sub support member 110, and the central portion in the vertical direction is rotatably supported by the main bearing 13, and the lower end is the sub support member 110. The sub bearing 23 is rotatably supported. The compression member 109 is integrally formed at a position below the center of the rotating shaft 5 and is disposed in the cylinder 108.

  The compression member 109 is disposed in the cylinder 108 described above, is driven to rotate by the rotating shaft 5, compresses the fluid (in this embodiment, refrigerant) sucked from the suction port, and compresses the discharge valve 12 and the discharge pipe from the discharge port. It is for discharging into the sealed container 1 through 95, and has a substantially cylindrical shape concentric with the rotary shaft 5 as a whole. The compression member 109 has a shape in which a thick portion on one side and a thin portion on the other side are continuous, and a lower surface 113 (one surface) intersecting the axial direction of the rotating shaft 5 is low in the thick portion, and the thin portion It has a high slope. That is, the lower surface 113 has a shape that is continuously inclined between the top dead center and the bottom dead center that returns from the highest top dead center to the top dead center through the lowest bottom dead center (not shown). ).

  One surface of the compression member 109 having a continuously inclined shape is disposed on a lower surface 113 which is a surface opposite to the driving element 2 housed on the upper side in the sealed container 1 of the compression member 109.

  Further, the discharge pipe 95 of this embodiment is a pipe extending from the discharge port 28 onto the oil surface of the oil reservoir 36 in the lower part of the sealed container 1, and the refrigerant compressed in the cylinder 108 is discharged from the discharge port 28. The oil is discharged onto the oil level in the sealed container 1 through the valve 12 and the discharge pipe 95.

  In addition, since the shape of the lower surface 113 of the compression member 109 is the same shape as the upper surface 33 of the compression member 9 of Example 1, description is abbreviate | omitted. Similarly, the hardness of the lower surface 113 (one surface) of the compression member 109 is set to be higher than the upper surface 112A of the protruding member 112 of the sub-support member 110 as a receiving surface of the top dead center 33A. Further, the materials and processing methods of the lower surface 113 of the compression member 109 and the vane 11 are the same as those described in the first embodiment (see FIG. 18). Thereby, the durability of the compression member 89 and the vane 11 can be improved as in the above embodiment.

  In particular, when the vane 11 is made of a carbon-based material, a ceramic-based material, a fluororesin-based material, or a polyether ether ketone, the lower surface 113 of the compression member 109 is compressed by applying the material and processing shown in FIG. A difference in hardness occurs between the lower surface 113 of the member 109 and the vane 11, and good slidability is maintained even when the lubrication to the sliding portion is insufficient or the compression element 3 is not lubricated. Will be able to.

  On the other hand, the vane 11 is disposed between the suction port and the discharge port as described above and abuts against the lower surface 113 of the compression member 109 to partition the compression space 21 in the cylinder 108 into a low pressure chamber and a high pressure chamber. Further, the coil spring 18 constantly biases the vane 11 toward the lower surface 113 side.

  The space 115 is a space sealed by the compression member 109 and the main support member 107 as described above, but the refrigerant in the compression space 21 slightly flows from the clearance between the compression member 109 and the cylinder 108. Therefore, the pressure of the space 115 is higher than the low-pressure refrigerant sucked into the suction port and becomes an intermediate pressure lower than the pressure of the high-pressure refrigerant in the sealed container 1.

  Thus, by setting the pressure of the space 115 to an intermediate pressure, the compression member 109 is strongly pushed upward by the pressure of the space 115, and the upper surface 112A of the protruding member 112 whose lower surface 113 of the compression member 109 serves as a receiving surface Can avoid the inconvenience of wear. Thereby, durability of the lower surface 113 of the compression member 109 can be improved.

  In addition, by setting the pressure in the space 115 on the other surface side of the compression member 109 to an intermediate pressure, the pressure in the space 115 becomes lower than the pressure in the sealed container 1. Oil can be smoothly supplied to the vicinity of the compression member 109 and the main bearing 13 which are peripheral portions.

  Furthermore, by disposing the compression space 21 on the lower surface 113 of the compression member 109 on the side opposite to the drive element 2, gas leakage from the main bearing 13 is less likely to occur, and the sealing performance of the main bearing 13 can be improved. Further, since the auxiliary bearing 23 on the lower surface 113 side of the compression member 109 that becomes the compression space 21 is located in the oil reservoir 36, gas leakage from the auxiliary bearing 23 can be avoided by oil, and the sealing performance of the auxiliary bearing 23 is improved. In addition, it is possible to avoid the inconvenience that the peripheral surface of the rotating shaft 5 becomes a high pressure. This makes it possible to smoothly perform refueling using the pressure difference.

  Similarly to the above-described embodiment (embodiment 3), the above-described back pressure chamber 17 does not have a high pressure as in the prior art, and the pressure of the back pressure chamber 17 is higher than the pressure of the refrigerant sucked into the suction port as a sealed space. And a value lower than the pressure in the sealed container 1. As a result, the pressure in the back pressure chamber 17 is lower than that in the sealed container 1. Therefore, the oil passage 42 in the rotating shaft 5 is raised using the pressure difference, and the rotating shaft 5 is moved from the oil passage 42 to the rotating shaft 5. Oil from an oil hole (not shown) formed over the side surface of the compression member 109 in the axial direction can be supplied also to the peripheral portion of the vane 11.

  In addition, a minute clearance is formed between the peripheral surface of the compression member 109 and the inner wall of the cylinder 108, so that the compression member 109 is rotatable. The space between the peripheral surface of the compression member 109 and the inner wall of the cylinder 108 is also sealed with oil.

  A discharge valve 12 is mounted outside the discharge port on the side surface of the compression space 21 of the cylinder 108, and a discharge pipe 95 is formed in the cylinder 108 and the main support member 107 outside the discharge valve 12. The upper end of the discharge pipe 95 is opened on the oil surface of the oil reservoir 36.

  As described above, the refrigerant gas discharged from the discharge port passes through the discharge pipe 95 and is guided onto the oil surface, whereby the pulsation of the discharged refrigerant can be reduced.

  As described above in detail, also in the present embodiment, oil supply to the sliding portions such as the compression member 109 and the vane 11 can be smoothly performed, and the reliability of the compressor C can be improved. Further, in the third embodiment, bearings of the rotary shaft 5 are provided at three locations on the upper side (sub bearing 83) and lower side (main bearing 13) of the compression element 3 and on the lower side (sub bearing 86) of the driving element 2. However, in this embodiment, the rotary shaft 5 can be sufficiently supported by the two bearings of the main bearing 13 and the sub-bearing 23, so that the number of parts is reduced and the compressor is configured at low cost. Can do.

  Next, FIGS. 27 to 29 show the compressor C of the fifth embodiment, and FIGS. 27 to 29 are longitudinal side views of the compressor C of the fifth embodiment, and each drawing has a different cross section. FIG. In FIG. 27 to FIG. 29, the same reference numerals as those shown in FIG. 1 to FIG. 26 have the same or similar effects, and the description thereof will be omitted.

  In this case, the drive element 2 is accommodated in the lower side of the sealed container 1, the compression element 3 is accommodated in the upper side, and the compression space 21 of the compression element 3 is the lower surface side that is the drive element 2 side of the compression member 109. The lower surface (one surface) 113 of 109 has a shape that inclines continuously from the top dead center to the bottom dead center. Here, as in the above embodiments, the hardness of the lower surface 113 (one surface) of the compression member 109 is set to be higher than the upper surface 112A of the protruding member 112 of the sub-support member 110 as the receiving surface of the top dead center 33A. Has been. Further, the materials and processing methods of the lower surface 113 of the compression member 109 and the vane 11 are the same as those described in the first embodiment (see FIG. 18). Thereby, the durability of the compression member 89 and the vane 11 can be improved as in the above embodiment.

  In particular, when the vane 11 is made of a carbon-based material, a ceramic-based material, a fluororesin-based material, or a polyether ether ketone, the lower surface 113 of the compression member 109 is compressed by applying the material and processing shown in FIG. A difference in hardness occurs between the lower surface 113 of the member 109 and the vane 11, and good slidability is maintained even when the lubrication to the sliding portion is insufficient or the compression element 3 is not lubricated. Will be able to.

  On the other hand, the space 115 on the other surface side of the compression member 109 is a space sealed by the compression member 109 and the main support member 107, so that the clearance between the compression member 109 and the cylinder 108 is slightly increased in the compression space 21. Therefore, the pressure in the space 115 is higher than the low-pressure refrigerant sucked into the suction port 27 and becomes an intermediate pressure lower than the pressure of the high-pressure refrigerant in the sealed container 1.

  Thus, by setting the pressure of the space 115 to an intermediate pressure, the compression member 109 is strongly pushed upward by the pressure of the space 115, and the upper surface 112A of the protruding member 112 whose lower surface 113 of the compression member 109 serves as a receiving surface Can avoid the inconvenience of wear. Thereby, durability of the lower surface 113 of the compression member 109 can be improved.

  On the other hand, a slot 16 is formed in the main support member 107 and the cylinder 108, and the vane 11 is inserted into the slot 16 so as to be able to reciprocate up and down. A back pressure chamber 17 is formed at the lower portion of the slot 16, and a coil spring 18 is disposed in the slot 16 as an urging means for pressing the lower surface of the vane 11 upward. The vane 11 abuts on the lower surface 113 of the compression member 109 and partitions the compression space 21 in the cylinder 108 into a low pressure chamber and a high pressure chamber. Further, the coil spring 18 constantly biases the vane 11 toward the lower surface 113 side.

  The back pressure chamber 17 is a sealed space as in the above embodiment, and the pressure of the back pressure chamber 17 is higher than the pressure of the refrigerant (refrigerant) sucked into the suction port 27 and lower than the pressure in the sealed container 1. Yes. In this way, by making the back pressure chamber 17 a sealed space without communicating with the inside of the sealed container 1, the back pressure chamber 17 is connected to the low pressure chamber side and the high pressure chamber side of the compression space 21 from the gap of the vane 11. Only a small amount of refrigerant flows in. For this reason, the back pressure chamber 17 has an intermediate pressure higher than the pressure of the refrigerant sucked into the suction port 27 and lower than the pressure in the sealed container 1. As a result, the pressure in the back pressure chamber 17 is lower than that in the sealed container 1, and the oil passage 42 in the rotating shaft 5 is lifted using the pressure difference, and the oil from the oil holes 44 and 45 is used. Can also be supplied to the periphery of the vane 11.

  On the other hand, the space 115 on the other surface side of the compression member 109 is a space sealed by the compression member 109 and the main support member 107. Thereby, since the refrigerant in the compression space 21 slightly flows from the clearance between the compression member 109 and the cylinder 108, the pressure in the space 115 is higher than the low-pressure refrigerant sucked into the suction port 27, and the high pressure in the sealed container 1. The intermediate pressure is lower than the refrigerant pressure.

  Thus, by setting the pressure of the space 115 to an intermediate pressure, the compression member 109 is strongly pushed upward by the pressure of the space 115, and the upper surface 112A of the protruding member 112 whose lower surface 113 of the compression member 109 serves as a receiving surface Can avoid the inconvenience of wear. Thereby, durability of the lower surface 113 of the compression member 109 can be improved.

  In addition, by setting the pressure in the space 115 on the other surface side of the compression member 109 to an intermediate pressure, the pressure in the space 115 becomes lower than the pressure in the sealed container 1. Oil can be smoothly supplied to the vicinity of the compression member 109 and the main bearing 13 which are peripheral portions.

  In each of the above embodiments, the compressor used for the refrigerant circuit of the refrigerator to compress the refrigerant has been described as an example. It is valid. Further, in each of the embodiments, the vertical compressor that stores the driving element and the compression element in the vertical direction in the vertical sealed container has been described. However, the present invention is not limited thereto, and a horizontal compressor is used. The present invention is also effective.

It is a vertical side view of the compressor of the 1st Example of the present invention. It is another longitudinal side view of the compressor of FIG. It is a perspective view of the compression element of the compressor of FIG. FIG. 2 is another perspective view of a compression element of the compressor of FIG. 1. It is a top view of the compression element of the compressor of FIG. It is a bottom view of the compression element of the compressor of FIG. It is a side view of the rotating shaft containing the compression member of the compressor of FIG. It is a 1st perspective view of the compression member of the compressor of FIG. It is a 2nd perspective view of the compression member of the compressor of FIG. It is a 3rd perspective view of the compression member of the compressor of FIG. It is a 4th perspective view of the compression member of the compressor of FIG. It is a 5th perspective view of the compression member of the compressor of FIG. It is a 6th perspective view of the compression member of the compressor of Drawing 1. It is an enlarged view which shows the inclination at the time of seeing the upper surface of the compression member of the compressor of FIG. 1 from the side surface. It is a vertical side view of the rotating shaft and compression element of the compressor of FIG. It is a perspective view of the rotating shaft in the state where the cylinder of FIG. 15 was attached. It is another longitudinal side view of the compression element of the compressor of FIG. It is a figure which shows the material and processing method of the member used for one surface of this compression member, this receiving surface, and a vane. It is a vertical side view of the compression element of the compressor of the 2nd Example of this invention. It is a perspective view of the compression element of the compressor of FIG. It is a vertical side view of the compressor of the 3rd Example of the present invention. It is another vertical side view of the compressor of FIG. FIG. 22 is still another longitudinal side view of the compressor of FIG. 21. It is a vertical side view of the compressor of the 4th Example of this invention. It is another vertical side view of the compressor of FIG. FIG. 25 is still another longitudinal side view of the compressor of FIG. 24. It is a vertical side view of the compressor of the 5th Example of this invention. It is another vertical side view of the compressor of FIG. FIG. 28 is still another longitudinal side view of the compressor of FIG. 27.

Explanation of symbols

C Compressor 1 Airtight container 2 Drive element 3 Compression element 4 Stator 5 Rotating shaft 6 Rotor 7, 77 Support member 8, 78, 108 Cylinder 9, 89, 109 Compression member 11 Vane 13 Main bearing 16 Slot 18 Coil spring 21 Compression Space 22, 110 Sub support member 23 Sub bearing 24 Suction passage 26 Suction pipe 27 Suction port 28 Discharge port 31 Thick part 32 Thin part 33, 93 Upper surface 34 Plane 35 Curved surface 36 Oil reservoir 37, 38 Discharge pipe 40 Oil pump 42 Oil Passage 44, 45 Oil hole 50 Shaft seal 52 Abutment 53 Cover 60 Piston ring seal 61 Groove 79, 107 Main support member 113 Lower surface 80 Line 82 Straight line 84, 84A, 84B Curve

Claims (3)

A compression element composed of a cylinder having a compression space therein;
A suction port and a discharge port communicating with the compression space in the cylinder;
One surface intersecting the axial direction of the rotation axis is continuously inclined between the top dead center and the bottom dead center, and is disposed in the cylinder and is driven to rotate by the rotation shaft, and is sucked from the suction port. A compression member that compresses and discharges from the discharge port;
A vane disposed between the suction port and the discharge port, abutting against one surface of the compression member, and dividing the compression space in the cylinder into a low pressure chamber and a high pressure chamber;
When the compression element is unlubricated, a difference in hardness is provided between the vane and one surface of the compression member.   2. The compressor according to claim 1, wherein the vane is made of a carbon material, a ceramic material, a fluororesin material, or a polyether ether ketone material.   The compressor according to claim 1 or 2, wherein a hardness of one surface of the compression member is higher than a receiving surface of the top dead center.

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