Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
  • F04C29/0021—Systems for the equilibration of forces acting on the pump
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids

Definitions

• grooves 2 to 27 are provided on the end faces 19 a and 19 b of the roller 19, respectively, and the communication section 20 a 27 a communicates with this groove to the inner peripheral side of the roller 19.
• the present invention relates to a rotary compressor provided with a compression machine part having good volumetric efficiency, which is used in a refrigerator or a freezing cycle of a freezer.
• compressors used for refrigeration cycles have been reduced in size by changing the compression method from a recipient type to a rotary type (rotary type). It has been requested.
• FIG. 1 A conventional rotary compressor will be described with reference to FIGS. 1 to 4.
• FIG. 1 A conventional rotary compressor will be described with reference to FIGS. 1 to 4.
• 1 is a sealed casing
• 2 is a motor section, and is connected to a cylinder 4, a roller 5, a vane 6, a main bearing 7, and an auxiliary bearing 8 via a shaft 3.
• It is connected to the mechanical unit body 9 composed of
• the shaft 3 is composed of a main shaft 3a, a sub shaft 3b, and a crank 3c eccentric by E from the axis of the main shaft 3a and the sub shaft 3b.
• a hole 3e is formed in the center of the shaft 3, and an oil supply hole 3f and an oil supply groove 3g are provided in the crank 3c.
• 10 is a spring provided on the back of the vane.
• the suction chamber and compression chamber 11 a and 11 b are formed in a cylinder 4 by a roller 5, a vane 6, a main bearing 7, and a sub-bearing 8.
• Reference numeral 1 2 denotes a refueling mechanism connected to the shaft 3.
• Reference numeral 13 denotes a suction pipe, which communicates with the suction chamber 11a via the auxiliary bearing 8 and the suction passage 14 of the cylinder 4.
• Reference numeral 15 denotes a discharge port, which communicates with the inside of the closed casing 1 via a discharge valve 16.
• Reference numeral 17 denotes a discharge pipe which is open in the closed casing 1.
• Reference numeral 18 denotes a lubricating oil.
• the direction of the solid arrow in FIG. 4 corresponds to the direction of movement of the roller 5 at a certain point during the compressor operation, and the direction of the dashed arrow corresponds to the operation of the roller 5.
• the direction in which the lubricating oil 18 flows on the end faces 5a and 5b of the cylinder is shown.
• 5 e is the theme of Roller 5. Of 5c and 5d, a section whose cross-sectional area gradually decreases in the direction of the dashed arrow, and 5f a section whose cross-sectional area gradually increases.
• Refrigerant gas from a cooling system (not shown) is led from the suction pipe 13 and the suction hole 14 and reaches the suction chamber 11 a in the cylinder 4.
• the refrigerant gas that has reached the suction chamber 11a is compressed by the compressor 5 divided by the roller 5 and the vane 6 rotatably stored in the crank 3c of the shaft 3.
• the compression is performed by the rotational motion of the shaft 3 accompanying the rotation of the motor unit 2.
• the compressed refrigerant gas is once discharged into the closed casing 1 through the discharge hole 15 and the discharge valve 16, and then is cooled through the discharge pipe 17. Is discharged to the system.
• the high-pressure lubricating oil 18 in the closed casing 1 in which the refrigerant has been melted is supplied to the hole 3 e of the shaft 3 by the oil supply mechanism 12, -3 one
• the oil is supplied to the sliding part between the main bearing 7 and the sub-bearing 8, and is also supplied to the inner periphery of the crank 3c and the roller 5 from the oil supply hole 3f and oil supply groove 3g. After lubricating the roller end faces 5a and 5b, it reaches the suction chamber 11a and the compression chamber lib, and then into the closed casing 1 from the discharge hole 15. Discharges and returns to the bottom of enclosure 1.
• the roller 5 rotates along with the rotation of the shaft 3 while revolving around the crank 3 c while considering the direction, and performs a revolving motion. Result
• the trajectory of one point on the roller 5 is spiral. Therefore, the direction of movement of the roller 5 changes close to 360 ° while the shaft 3 rotates, for example, the rotational movement of the roller 5.
• the direction of movement is the direction shown by the arrow in FIG. 4, the end faces 5a and 5b of the roller 5 are provided with teno degrees 5c and 5d. Only the lubricating oil 18 flowing into the vicinity of 5e in the part 5c, 5d becomes narrower in cross section from the inner diameter side to the outer diameter side. As a result, hydraulic pressure is generated. Accordingly, the hydraulic pressure in the vicinity of the tapers 5c and 5d is displaced, and as a result, the clearance S between the roller 5 and the main bearing 7 and the sub-bearing 8 is reduced.
• the wedge effect of lubricating oil that enters the taper is used, and this wedge effect is caused by the spiral motion of the roller accompanying the rotational movement of the shaft. This occurs in the orbital motion component of the motion, but the rotation of the taper turns around the crank because the cross-sectional area does not change in the circumferential direction. On the other hand, it does not occur and the wedge effect is small. Also, only one location on the roller end face where oil pressure is generated due to the wedge effect does not occur in most locations, and furthermore, the taper does not. Since the parts themselves have a shape that communicates in the circumferential direction, the pressure generated by the wedge effect escapes in the circumferential direction, and the wedge effect decreases. The generated pressure is low. As a result, there was a problem that the stability of the roller due to the wedge effect was not sufficient, and the effect of improving the volumetric efficiency was small.
• a first object of the present invention is to stabilize the movement of the roller and improve the volumetric efficiency of the compression mechanism.
• the second purpose is lubricating oil in which refrigerant is mixed into the suction chamber and compression chamber.
• the goal is to minimize the inflow of water.
• the end face of the roller facing the main bearing and the sub-bearing extends in the direction of communication with the inner peripheral side of ⁇ -axis and in a substantially circumferential direction as it separates from the communication part.
• a groove formed by a plurality of sealing portions having a large cross-sectional area is formed.
• the main bearing and the sub bearing opposing the roller communicate with the inner peripheral side of the roller, and at least once during one rotation of the end face of the roller and the shaft. In this case, a plurality of grooves are formed.
• FIG. 1 is a longitudinal sectional view of a conventional rotary compressor
• Fig. 2 is a view taken along the line ⁇ - ⁇ 'in Fig. 1
• Fig. 3 is an enlarged sectional view of the mechanical part in Fig. 1.
• Fig. 4 is a front view showing a roller of Fig. 1
• Fig. 5 is a front view of a roller of a rotary compressor showing a first embodiment of the present invention
• Fig. 6 is a fifth view.
• FIG. 7 is an enlarged cross-sectional view of the mechanical part shown in FIG. 7,
• FIG. 7 is a front view of a roller of a rotary compressor showing a second embodiment of the present invention, and FIG. FIG.
• FIG. 9 is a front view of a roller of a rotary compressor showing a third embodiment of the present invention
• FIG. 10 is an enlarged sectional view of the mechanical part of FIG. 9
• FIG. 12 is a front view of a main bearing of a rotary compressor showing a fourth embodiment of the present invention.
• FIG. 12 is an enlarged cross-sectional view of the mechanical part of FIG. 11, FIG. 13 and FIG.
• FIG. 2 is a cross-sectional view showing an operation state of the mechanical unit in FIG. 11;
• FIG. 5 and FIG. 6 show a first embodiment of the present invention.
• Reference numeral 19 denotes a roller, which is rotatably held by the crank 3c of the shaft 3 as in the related art.
• the same number of grooves 20 to 24 to 27 are provided on the end faces 19 a and 19 b of the roller 19, respectively.
• the grooves 20 to 27 extend from the communication portions 20 a to 27 a with the inner peripheral side of the roller 19 and the communication portions 20 a to 27 a along the circumferential direction, and extend and communicate with the communication portions 2. It is formed by the sealing portions 2 b to 27 b and 20 c to 27 c whose cross-sectional area decreases as the distance from 0 a to 27 a increases.
• the refrigerant gas sucked through the suction pipe 13 is compressed as in the conventional case, and is discharged to the cooling system through the discharge pipe 17.
• the high-pressure lubricating oil 18 in the sealed casing 1 in which the refrigerant has melted also lubricates the machine body 9 as before, but lubrication that has flowed into the inner peripheral side of the roller 19 After lubricating the rollers 19a and 19b, the oil 18 returns to the lower part of the closed casing as before.
• the roller 19 performs a revolving motion and a rotation according to the rotation of the shaft 3 as in the related art, and as a result, the roller 19 performs a spiral motion.
• the direction of the motion at the moment of the rotational motion is the solid arrow direction as in the past, and the direction in which the lubricant 18 flows by the motion of the roller 19 is the direction of the broken arrow.
• the sealing portions 20 b to 27 b and 20 c to 27 c are the sealing portions 2.
• 0 c, 21 c, 23 b, 2 b, 25 b, 26 b, 26 c, and 27 c are cut in the flow direction of the lubricating oil 18 indicated by the dashed arrow.
• the area is reduced, and the water flows in from the communication parts 20a to 27a.
• - ⁇ -Lubricating oil 18 generates hydraulic pressure.
• the oil is applied to one or both of the sealing portions 20 b to 27 b and 20 c to 27 c.
• Pressure is generated, and the hydraulic pressure generation position is dispersed on the roller end face 19a, which is different from only one conventional position.
• Hydraulic pressure is generated at one or both of the stop portions 20b to 27b and 20.c to 27c, and the hydraulic pressure is generated at the end faces 19a and 19b. It is a symmetric position.
• the sealing portions 20b to 27b and 20c to 27c whose cross-sectional areas decrease in a substantially circumferential direction are formed.
• hydraulic pressure is generated in either direction of rotation due to the wedge effect.
• the oil pressure is generated in the vicinity of the sealing portions 20b to 27b and 20c to 27c, there is no escape for the oil pressure, and the oil pressure is kept high. Therefore, the same hydraulic pressure is always generated and distributed on the end faces 19a and 19b of the roller 19 at positions where the same hydraulic pressure is dispersed.
• this oil pressure is higher than before due to the oil pressure generated by the rotation component and the oil pressure that is maintained high without escaping.
• the grooves 20 to 27 are not provided over the entire circumference, and the seal distance is longer than when a taper is provided. In addition, the amount of lubricating oil flowing into the compression chamber and the suction chamber is reduced, and the volume efficiency is improved even in the case of a small compressor having a thin roller.
• the end faces 19a and 19b of the roller 19 are provided with the same number of grooves 28 to 32 to 35, respectively.
• the grooves 28 to 35 extend substantially radially from the communicating portions 28 a to 35 a and the communicating portions 28 a to 35 a with the inner peripheral side of the roller 19 and the communicating portions 28 a to Sealing parts 28 b to 35 b and 28 c to 35 c, 28 d to 35 d, 28 e to 35 e, 2 which reduce the cross-sectional area as they move away from 35 a It is formed by 8i to 35f.
• the refrigerant gas sucked from the suction pipe 13 is compressed as in the conventional case, and is discharged to the cooling system through the discharge pipe 17.
• the high-pressure drip oil 18 in the closed casing 1 in which the refrigerant has dissolved also lubricates the machine body 9 as before, but lubrication that has flowed into the inner peripheral side of the roller 19
• the oil 18 returns to the lower part of the closed casing as before, after lubricating the end faces 19a and 19b of the roller.
• the roller 19 performs a revolving motion and a rotation according to the rotation of the shaft 3 as in the related art, and as a result, the roller 19 performs a spiral motion.
• the direction of the momentary movement of the rotary motion is the same as the conventional direction indicated by the solid arrow, and the direction in which the lubricant 18 flows by the motion of the roller 19 is the direction indicated by the broken arrow.
• Oil pressure is generated by lubricating oil 18 flowing in from 35 a.
• the sealing portions 28e and 28f generate hydraulic pressure
• the hydraulic pressure occurs in the sealing portions 32c and 32d. That will be.
• hydraulic pressure is generated at the two sealing portions for all the grooves 28 to 35, and the hydraulic pressure is generated only at the conventional one position. Unlike, they are distributed on the roller end face 19a.
• the same operation is performed on the end face 19b side, and the hydraulic pressure generation position is symmetrical at the end faces 19a and 19b, and the oil generated at the end faces 19a and 19b Pressure balances.
• the sealing portions 28 c to 35 c, 28 d to 35 d, 28 d whose cross-sectional area decreases substantially in the circumferential direction Since e-35e and 28f-35f are formed, hydraulic pressure is generated in either direction of rotation due to the wedge effect.
• the oil pressure is in the vicinity of the sealing portions 28b to 35b, 28c to 35c, 28d to 35d, 28e to 35e, 28f to 35f. Since there is no escape for oil pressure, the oil pressure is kept high. Therefore, the same hydraulic pressure is normally generated at the end faces 19a and 19b of the roller 19 at the positions where the same hydraulic pressure is dispersed, and the load is distributed.
• the grooves 28 to 35 are not provided over the entire circumference, and the seal distance is longer than when a taper is provided. , -10-The amount of lubricating oil flowing into the compression chamber and the suction chamber is reduced, and the volume efficiency is improved even with a small compressor, etc., even with a small thickness.
• FIG. Grooves 37 to 44 are provided in the end faces 36 a and 36 b of the roller 36.
• the grooves 37 to 44 are formed with communicating portions 37 a to 44 a passing through the inner peripheral wall of the roller 36 and the grooves 37 to 44, and a sealing portion 37 b To 44 b, 37 c to 44 c, 37 d to 44 d, 37 e to 44 e, and 37 to 44 are communication parts 37 & to 44 & groove of 37 to 4 It is formed radially from the opening to 4.
• hydraulic pressure is generated by the spiral motion at the sealing portions 37 b to 44 f, but the communication portions 37 a to 44 a are formed by the grooves 37 to 44.
• a hole is formed in the center, and hydraulic pressure is generated under the same conditions because the distance between the communicating parts 37a to 44a is constant in all the sealing parts 37b to 44f.
• a higher oil pressure than that of the second embodiment can be obtained, and the lubricating oil can be smoothly supplied.
• FIG. 11 a fourth embodiment of the present invention will be described with reference to FIGS. 11 to 14.
• FIG. 11 a fourth embodiment of the present invention will be described with reference to FIGS. 11 to 14.
• Reference numeral 45 denotes a main glaze
• reference numeral 46 denotes a sub bearing.
• the shaft 3 is rotated by the shaft 3 as in the conventional case.
• Reference numeral 47 denotes a roller, which is rotatably held by the crank 3 c of the shaft 3.
• the main bearing 45 and the auxiliary bearing 46 are provided with the same number of grooves 48 to 52 to 55, respectively.
• the grooves 48 to 55 are formed in a shape whose cross-sectional area decreases in the circumferential and radial directions from the center of the groove.
• the two-dot chain line shows the inner peripheral surface of the cylinder 4, the vanes 6 and the rollers 47, and the groove 48 at a certain rotational position.
• Figs. 13 and 14 also show the positional relationship between the grooves 48-55 and the roller 47, but in practice the grooves 48-55 should be displayed as hidden lines. However, it is shown with solid lines to make the figure easier to understand.
• the refrigerant gas sucked in from the suction pipe 13 is compressed as in the related art, and discharged to the cooling system through the discharge pipe 17.
• the high-pressure lubricating oil 18 in the sealed casing 1 in which the refrigerant has dissolved lubricates the machine body 9 as before, but has flowed into the inner periphery of the roller 47. After lubricating the both end surfaces of the roller 47, the lubricating oil 18 returns to the lower portion of the closed casing as in the related art.
• the roller 47 performs a public tilling operation and a rotation motion with the rotation of the shaft 3 as in the conventional case.
• the direction of the rotation at a rotational angle with a helical motion is indicated by a solid arrow as in the conventional case.
• the grooves 48 to 55 of the main bearing 45 are sealed by the end face of the roller 47. Is in a state of Also, the grooves 48 to 55 of the auxiliary bearing 46 are also sealed.
• the grooves 48 to 55 have a shape whose cross section ⁇ is reduced in the radial direction and the circumferential direction from the center of the groove, and a solid line is provided inside the grooves 50 to 53 to be sealed.
• the positions where the hydraulic pressures are generated are four at each end of the roller 47, and the hydraulic pressure is balanced at both ends.
• grooves 48 to 55 are formed so as to reduce the cross-sectional area in the circumferential direction. Even in these rotation directions, they occur in the grooves 50 to 53 which are sealed by the wedge effect.
• the grooves 48 to 55 are independent of each other, and there is no escape for the oil pressure generated in the sealed grooves 50 to 53, and the oil pressure is kept high. .
• the grooves 48 to 55 and the roller 47 always face only a part, and the seal distance is longer than when a taper is provided. As a result, the flow of lubricating oil flowing into the compression chamber is reduced, and volumetric efficiency is improved even when the roller thickness is small with small compressors, etc.o
• the contact surface between ⁇ - -13-Due to the formation of a communicating part that communicates with the sealing part of the lubricating oil and the inner peripheral surface of the roller the same magnitude of hydraulic pressure is always generated at dispersed positions. It is something to be balanced. Therefore, when it is used for a refrigerating cycle such as a refrigerator or a freezer, the movement of the roller is stabilized, the volumetric efficiency is improved, and the performance of the refrigerating cycle is improved. is there .

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Applications Or Details Of Rotary Compressors (AREA)

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Citations (3)

• 1991
  • 1991-05-30 BR BR919106801A patent/BR9106801A/pt not_active IP Right Cessation
  • 1991-05-30 DE DE69125008T patent/DE69125008T2/de not_active Expired - Fee Related
  • 1991-05-30 WO PCT/JP1991/000725 patent/WO1992021881A1/ja active IP Right Grant
  • 1991-05-30 CA CA 2088160 patent/CA2088160C/en not_active Expired - Fee Related
  • 1991-05-30 EP EP91910170A patent/EP0541801B1/en not_active Expired - Lifetime

Patent Citations (3)

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