JP2013224606A - Refrigerant compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerant compressor capable of preventing overturning of an Oldham's ring and allowing a key groove at an orbiting scroll and a key part of the Oldham's ring to slide on a large surface.SOLUTION: A refrigerant compressor A comprises a ceiling part 23 above at least one of Oldham key grooves 3c and at a position overlapping with an upper surface of a key part 5b when at least the key part 5b reciprocates in the Oldham key groove 3c and a moving distance to a radial direction outer side becomes the maximum.

Description

  The present invention relates to a refrigerant compressor suitable for a refrigeration / air-conditioning apparatus using, for example, a vapor compression refrigeration cycle.

  2. Description of the Related Art A scroll type refrigerant compressor that has been well known in the past is configured such that a compression chamber whose volume changes relatively is formed by combining a fixed scroll that is a compression element portion and an orbiting scroll. In such a refrigerant compressor, an Oldham ring is used to suppress the rotation that occurs when the orbiting scroll performs an orbiting motion (see, for example, Patent Document 1).

  The refrigerant compressor described in Patent Document 1 is provided with a key groove of a frame in which the key portion of the Oldham ring slides, and a spring is provided in the key groove in a direction in which the key portion of the Oldham ring slides. The inertial force due to the reciprocating motion of the Oldham ring was reduced by the elastic force. Further, in Patent Document 1, as a structure that does not use a spring, the fluid in the space formed by the hole of the frame in which the key portion of the Oldham ring enters and the key portion of the Oldham ring is compressed by the elastic force of the fluid due to the compression action. A refrigerant compressor configured to reduce the inertia of the ring is disclosed.

Japanese Patent Laid-Open No. 3-64685 (FIGS. 2, 3, etc.)

  In the refrigerant compressor described in Patent Document 1, the Oldham ring reciprocates when the orbiting scroll rotates, and inertial force works. At the maximum amplitude of the Oldham ring's reciprocating motion, the inertial force is maximized, and this large inertial force increases the surface pressure between the keyway in the orbiting scroll and the key part of the Oldham ring. Wear progresses. In addition, since the center of gravity of the Oldham ring is not in the key portion but in the ring portion, a moment is generated in the Oldham ring's inertia force and the key portion of the Oldham ring that receives it, and the Oldham ring is overturned. As a result, the key groove on the orbiting scroll and the key portion of the Oldham ring are inclined to contact each other, causing one-side wear.

  In order to solve such a situation, the refrigerant compressor described in Patent Document 1 attempts to reduce the inertial force due to the reciprocating motion of the Oldham ring by the elastic force of the spring provided in the key groove of the frame. However, depending on the natural frequency of the spring, the effect of damping the inertial force of the Oldham ring will disappear, so this is applicable to refrigerant compressors that employ an inverter drive system that can vary the operating speed of the orbiting scroll. It was difficult. In addition, since extra power is required to compress the spring, the required power of the refrigerant compressor is increased, and the performance is deteriorated.

  Furthermore, Patent Document 1 discloses a refrigerant compressor having a structure that attempts to reduce the inertial force due to the reciprocating motion of the Oldham ring without using a spring. However, the inside of the keyway of the frame is often filled with a lubricating oil called refrigeration oil to improve the slidability of the keyway and the key part of the Oldham ring, and the elastic force of the lubricating oil is used. turn into. The power for compressing the lubricating oil is very large, which also increases the power required for the refrigerant compressor, leading to a decrease in the performance of the refrigerant compressor.

  In recent years, efforts to combat global warming have been strengthened, and the transition to a refrigerant with a low global warming potential (GWP) as a refrigerant used in the refrigeration cycle is being studied. However, in order to achieve both high efficiency equal to or higher than that of conventional refrigerant use and low GWP, it is necessary to cope with each refrigerant. Currently, refrigerants that are used as substitutes for R410A refrigerants used in home and commercial air conditioners are CFC-based low GWP refrigerants such as HFO1234yf and hydrocarbon-based natural refrigerants such as propane.

  In order to obtain refrigeration capacity, heating capacity, or efficiency equivalent to or higher than those of conventional refrigerants, it is necessary to increase the circulation amount of the refrigerant, and the refrigerant compressor can increase the operating speed or stroke volume. It is necessary to take measures such as increasing the size. As a guideline for increasing the circulation amount of the refrigerant, it is about 2 to 2.5 times for a fluorocarbon low GWP refrigerant such as HFO1234yf, and about 1.5 to 2 times for a natural hydrocarbon refrigerant such as propane, relative to R410A. It is.

  When the operating speed of the refrigerant compressor is increased or when the stroke volume is increased, the inertia force of the Oldham ring becomes larger than that in the conventional case. Then, the moment is further increased at the key portion of the Oldham ring that receives the increased inertial force, and the inclination of the key groove in the orbiting scroll and the key portion of the Oldham ring is increased. Due to this inclination, the keyway of the orbiting scroll and the key portion of the Oldham ring may be rolled, and the Oldham ring may be damaged.

  The Oldham ring preferably uses a light material such as an aluminum alloy in order to reduce the inertial force, but the aluminum alloy has a small rigidity and is easily deformed. For this reason, when deformation occurs, the angular phase combined with the vortex shifts, and a leak gap occurs when the compression chamber is formed. For this reason, it is necessary to increase the ring shape as a countermeasure against deformation, and if it is difficult to secure the sliding space of the Oldham ring, it is necessary to use a ferrous metal with a high rigidity and a low inertial force. Design restrictions such as being impossible will occur.

  The present invention has been made to solve at least one of the problems as described above, and can suppress the overturning of the Oldham ring. The key groove in the orbiting scroll and the key portion of the Oldham ring are provided. An object of the present invention is to provide a refrigerant compressor that can slide on a large surface.

  The refrigerant compressor according to the present invention has a fixed scroll in which a lap portion is erected on one surface of the end plate, and a wrap portion is erected on one surface of the end plate, and the wrap portion is connected to the wrap portion of the fixed scroll. An oscillating scroll arranged so as to be engaged, an Oldham ring arranged on the back side of the oscillating scroll to prevent rotation of the oscillating scroll, and a key portion of the Oldham ring are slidably stored. Two Oldham key grooves are formed at opposite positions, and the frame is disposed above at least one of the frame for supporting the swing scroll so as to be swingable, and at least one of the Oldham key grooves, and at least the key portion is within the Oldham key groove. A ceiling portion provided at a position overlapping with the upper surface of the key portion when the movement distance to the outside in the radial direction becomes the maximum after reciprocating. It is.

  According to the refrigerant compressor concerning the present invention, even if the inertial force of the Oldham ring increases by providing the ceiling portion, it can be corrected by pressing the upper surface of the key portion of the Oldham ring. As a result, the sliding state of the key groove on the orbiting scroll and the key portion of the Oldham ring can slide as much as possible, and the wear on the key groove of the orbiting scroll and the key portion of the Oldham ring can be reduced. .

It is a longitudinal cross-sectional view which shows the cross-sectional structural example of the refrigerant compressor which concerns on Embodiment 1 of this invention. It is a schematic perspective view which expands and shows the structure of the rocking | fluctuating scroll, Oldham ring, and frame of the refrigerant compressor which concerns on Embodiment 1 of this invention. It is a schematic sectional drawing for demonstrating the effect | action of the ceiling part with respect to the reciprocating motion of the Oldham ring of the refrigerant compressor which concerns on Embodiment 1 of this invention. It is a schematic sectional drawing for demonstrating the effect | action of the ceiling part with respect to the reciprocating motion of the Oldham ring of the refrigerant compressor which concerns on Embodiment 2 of this invention. It is a schematic sectional drawing for demonstrating the effect | action of the ceiling part with respect to the reciprocating motion of the Oldham ring of the refrigerant compressor which concerns on Embodiment 3 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view showing a sectional configuration example of a refrigerant compressor A according to Embodiment 1 of the present invention. A schematic configuration of the refrigerant compressor A will be described with reference to FIG. This refrigerant compressor A is a scroll type compressor, and is one of the components of a refrigeration cycle used in various industrial machines such as refrigerators, freezers, vending machines, air conditioners, refrigeration equipment, and water heaters. Is. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one.

[Schematic configuration of refrigerant compressor A]
The refrigerant compressor A sucks the refrigerant circulating in the refrigeration cycle, compresses it, and discharges it as a high-temperature and high-pressure state. The refrigerant compressor A includes a fixed scroll 1 and a fixed scroll 1 in a closed container 20 constituted by a closed container (center shell) 17, a closed container (lower shell) 18, and a closed container (upper shell) 19. The compression element portion 50 is combined with the swing scroll 2 that swings. Further, the refrigerant compressor A includes a drive element unit 60 made of an electric rotary machine or the like in the sealed container 20.

  The sealed container 20 is configured such that an upper part 19 of the sealed container is provided with an upper part 19 of the sealed container and a lower part 18 of the sealed container is provided 18. The bottom 18 of the sealed container is an oil sump 16 for storing lubricating oil. Further, the closed container 17 is connected to a suction connection pipe 21 that is connected to the refrigerant circuit and takes in the refrigerant gas from the refrigerant circuit. A discharge connection pipe 22 for connecting the refrigerant circuit and discharging the refrigerant gas to the refrigerant circuit is connected to the top 19 of the sealed container. The inside of the sealed container 17 is a low pressure chamber, and the inside of the sealed container 19 is a high pressure chamber.

  The fixed scroll 1 includes an end plate 1b and a wrap portion 1a that is a spiral projection standing on one surface of the end plate 1b. Further, the orbiting scroll 2 is composed of an end plate 2b and a wrap portion 2a which is a spiral protrusion that is erected on one surface of the end plate 2b so as to be engaged with the lap portion 1a. Yes. The other surface of the end plate 2b (the surface opposite to the surface on which the wrap portion 2a is formed (rear surface)) acts as an orbiting scroll thrust bearing portion (thrust bearing portion 2d shown in FIG. 2).

  The orbiting scroll 2 is configured such that a thrust bearing load generated during operation of the compressor is supported by the frame 3 via a thrust plate 4. A thrust plate 4 is installed on the swing scroll thrust bearing portion of the swing scroll 2. The thrust plate 4 is formed in a ring shape, and the boss 2e of the orbiting scroll 2 is positioned at the center. The thrust plate 4 serves as a thrust bearing that supports the orbiting scroll 2 in the axial direction. The boss 2e is a rocking bearing that supports the main shaft 8 in the rotational direction.

  The oscillating scroll 2 and the fixed scroll 1 are mounted in an airtight container 20 by combining the wrap portion 2a and the wrap portion 1a. In a state where the swing scroll 2 and the fixed scroll 1 are combined, the winding directions of the wrap portion 1a and the wrap portion 2a are opposite to each other. A compression chamber 25 whose volume changes relatively is formed between the wrap portion 2a and the wrap portion 1a. In the fixed scroll 1 and the orbiting scroll 2, in order to reduce refrigerant leakage from the front end surfaces of the wrap portion 1a and the wrap portion 2a, the front end surfaces (upper end surface and lower end surface) of the wrap portion 1a and wrap portion 2a are provided. A seal (not shown) is provided.

  The fixed scroll 1 is fixed to the frame 3 with bolts or the like not shown. A discharge port 1c that discharges the compressed and high-pressure refrigerant gas is formed at the center of the end plate 1b of the fixed scroll 1. The compressed refrigerant gas having a high pressure is discharged into a high-pressure chamber provided in the upper part of the fixed scroll 1. The refrigerant gas discharged to the high pressure chamber is discharged to the refrigeration cycle through the discharge connecting pipe 22. The discharge port 1c is provided with a discharge valve 24 for preventing the refrigerant from flowing backward from the high pressure chamber to the discharge port 1c side.

  The oscillating scroll 2 performs an oscillating motion without rotating with respect to the fixed scroll 1 by an Oldham ring 5 for preventing the rotating motion. A hollow cylindrical boss portion 2e is formed at a substantially central portion of the surface of the swing scroll 2 opposite to the surface on which the lap portion 2a is formed. An eccentric slider shaft 8a provided at the upper end of the main shaft 8 is inserted into the boss portion 2e. A specific configuration of the orbiting scroll 2 will be described in detail with reference to FIG.

  The Oldham ring 5 has an Oldham claw (Oldham key groove 2c shown in FIG. 2) formed on an Oldham key groove (Oldham key groove 2c shown in FIG. 2) formed on an orbiting scroll thrust bearing portion of the orbiting scroll 2. The key portion 5b shown in FIG. 2 is slidably housed and installed in the Oldham key groove (Oldham key groove 3c shown in FIG. 2) formed in the frame 3. A specific configuration of the Oldham ring 5 will be described in detail with reference to FIG.

  The frame 3 supports the swing scroll 2 and the fixed scroll 1 and is fixed to the inside of the sealed container 20 (the inner surface of the upper part of the sealed container 17). For example, the outer peripheral surface of the frame 3 is fixed to the inner peripheral surface of the sealed container 20 by shrink fitting, welding, or the like. Further, a main bearing (main bearing 3a shown in FIG. 2) for supporting the rotation of the drive element portion 60 (particularly the main shaft 8) is provided at the center opening of the frame 3. A specific configuration of the frame 3 will be described in detail with reference to FIG.

  The drive element unit 60 includes an electric motor rotor 6 fixed to the main shaft 8, an electric motor stator 7, a main shaft 8 that is a rotating shaft, and the like. The electric motor rotor 6 is shrink-fitted and fixed to the main shaft 8 and is rotationally driven when the electric current to the electric motor stator 7 is started to rotate the main shaft 8. The electric motor rotor 6 is arranged at the lower part of the balancer 11 fixed to the main shaft 8 together with the electric motor stator 7 which is fixed by shrinkage fitting to the inner surface of the intermediate portion of the sealed container 17. Electric power is supplied to the motor stator 7 via a power supply terminal provided in the sealed container 17.

  The main shaft 8 rotates with the rotation of the electric motor rotor 6 to turn the orbiting scroll 2. A slider 9 that supports the orbiting scroll 2 is installed on the outer periphery on the upper end side of the main shaft 8 to revolve the orbiting scroll 2. The upper end side of the main shaft 8 is an eccentric slider shaft 8 a that is a slider mounting shaft installed so that the slider 9 is eccentric with respect to the main shaft 8.

  The upper portion of the main shaft 8 (in the vicinity of the eccentric slider shaft 8a) is rotatably supported by a main bearing provided at the center of the frame 3. The main bearing is provided with a sleeve 10 for smoothly rotating the main shaft 8. The sleeve 10 functions to make the sliding surfaces in the main bearing parallel. On the other hand, the lower portion of the main shaft 8 is rotatably supported by a ball bearing 14. The ball bearing 14 is press-fitted and fixed to a bearing housing portion formed at the center portion of the sub-frame 13 provided at the lower portion of the sealed container 20.

  The subframe 13 is provided with a positive displacement oil pump 15. A pump shaft 8 b that transmits rotational force to the oil pump 15 is formed integrally with the main shaft 8. In the center of the main shaft 8, there is provided an oil hole 8c penetrating in the axial direction from the lower end of the pump shaft 8b to the upper end of the main shaft 8. The oil hole 8c communicates with the oil pump 15 on the lower end side. The lubricating oil sucked by the oil pump 15 is sent to each sliding portion through the oil hole 8c.

  Further, a balancer 11 is provided on the upper portion of the main shaft 8 in order to cancel the imbalance with respect to the rotation center of the main shaft 8 generated by the swing scroll 2 being mounted on the eccentric slider shaft 8a and swinging. . A balancer 12 is provided below the motor rotor 6 in order to cancel out the imbalance with respect to the center of rotation of the main shaft 8 generated by the swing scroll 2 mounted on the eccentric slider shaft 8a and swinging. The balancer 11 is fixed to the upper part of the main shaft 8 by shrink fitting, and the balancer 12 is fixed to the lower part of the motor rotor 6 integrally with the motor rotor 6.

[Detailed configuration of the orbiting scroll 2, the Oldham ring 5, and the frame 3]
FIG. 2 is a schematic perspective view showing the configuration of the orbiting scroll 2, the Oldham ring 5, and the frame 3 in an enlarged manner. Based on FIG. 2, the rocking scroll 2, the Oldham ring 5, and the frame 3 will be described in detail.

  As shown in FIG. 2, the orbiting scroll 2 is composed of an end plate 2b and a wrap portion 2a. Further, the surface of the end plate 2b opposite to the side on which the lap portion 2a is formed functions as a thrust bearing portion 2d. The thrust bearing portion 2d is formed with an Oldham key groove 2c in which the key portion 5a of the Oldham ring 5 is slidably housed. Further, a hollow cylindrical boss 2e is formed at the center of the surface of the end plate 2b on the thrust bearing portion 2d side. An eccentric slider shaft 8a and a slider 9 are inserted into the boss portion 2e.

  The Oldham keyway 2 c of the orbiting scroll 2 is formed of an iron-based metal such as cast iron or the same material as the orbiting scroll 2 or an Al—Si based metal. Further, since the orbiting scroll 2 needs to perform an orbiting motion with respect to the fixed scroll 1, the Oldham key groove 3 c is provided in the frame 3 that is fastened to the fixed scroll 1, thereby causing the orbiting scroll 2 to orbit. Can be given.

  As shown in FIG. 2, the Oldham ring 5 is provided on an annular ring portion 5c, two key portions 5a provided on the upper surface of the ring portion 5c, and a lower surface of the ring portion 5c. And two key portions 5b. The two key portions 5a are provided at positions facing each other across the center of the ring portion 5c. Similarly, the two key portions 5b are also provided at positions facing each other across the center of the ring portion 5c. The key portion 5 a is accommodated in an Oldham key groove 2 c formed in the swing scroll 2. The key portion 5 b is housed in an Oldham key groove 3 c formed in the frame 3.

  The key portions 5a and 5b of the Oldham ring 5 are formed of a high-rigidity and light-weight material such as an iron-based metal such as sintered material of the Oldham ring 5 or an aluminum-based mixed metal. Further, for the purpose of improving slidability, only the key portions 5a and 5b of the Oldham ring 5 or the surface of the Oldham ring 5 including the key portions 5a and 5b of the Oldham ring 5 is formed with DLC (Diamond Like Carbon), DLC- Any of Si (silicon-containing diamond-like carbon), CrN (chromium nitride), TiN (titanium nitride), TiCN (titanium carbonitride), TiAlN (titanium nitride aluminum), WCC (tungsten carbide), VC (vanadium carbide), etc. Or any coating treatment such as a manganese phosphate coating, a molybdenum disulfide coating, or a hard alumite treatment.

  As shown in FIG. 2, the frame 3 has an opening (hereinafter referred to as a center opening 3e) formed so as to penetrate the center vertically. A main bearing 3a is provided on the inner wall of the central opening 3e. The upper end side of the main shaft 8 is inserted into the center opening 3e, and the insertion portion is supported by the main bearing 3a.

  In addition, a boss portion storage portion 3f is formed above the center opening portion 3e so as to communicate with the center opening portion 3e and store the boss portion 2e of the orbiting scroll 2 so as to be turnable. Above the boss portion storage portion 3f, an Oldham ring storage portion 3g is formed which communicates with the central opening 3e and the boss portion storage portion 3f and in which the ring portion 5c of the Oldham ring 5 is slidably stored. Above the Oldham ring storage portion 3g, there is formed a swing scroll storage portion 3h that communicates with the central opening 3e, the boss portion storage portion 3f, and the Oldham ring storage portion 3g, and in which the swing scroll 2 is swingably stored. Has been.

  And the diameter becomes large in order of the center opening part 3e, the boss | hub part accommodating part 3f, the Oldham ring accommodating part 3g, and the rocking | scrolling scroll accommodating part 3h. That is, the internal cross-sectional structure of the frame 3 is configured in a step shape. The diameters of the central opening 3e, the boss portion storage portion 3f, the Oldham ring storage portion 3g, and the swing scroll storage portion 3h are determined according to the size of the refrigerant compressor A, the size of the swing scroll 2, and the like. It is like that.

  A suction port 3b for taking in the refrigerant into the compression element portion 50 is formed in an opening at a part of the bottom surface of the swing scroll storage portion 3h. An Oldham key groove 3c is formed in the boss portion accommodating portion 3f by notching a part of the wall surface toward the radially outer side. The Oldham key groove 3c is formed at a position corresponding to the key portion 5b of the Oldham ring 5, that is, at a position facing the main shaft 8 as a center, and slidably accommodates the key portion 5b. The Oldham keyway 3c is formed so as to communicate between the inside and the outside of the frame 3. Therefore, a part of the wall surface of the Oldham ring storage part 3g and a part of the bottom surface of the swing scroll storage part 3h at the position where the Oldham key groove 3c is formed are cut out. The Oldham key groove 3 c is formed of an iron-based metal such as cast iron made of the same material as the frame 3. In addition, the bottom surface of the Oldham ring storage portion 3g acts as the Oldham sliding surface 3d.

  Furthermore, a ceiling portion 23 that suppresses overturning of the Oldham ring 5 is provided above the ring portion 5c of the Oldham key groove 3c. The ceiling part 23 constitutes a part of the bottom surface of the swing scroll accommodating part 3h and a part of the wall surface of the Oldham ring accommodating part 3g in a state where it is installed on the frame 3. That is, the ceiling part 23 is provided so that it may bridge over the upper part which protruded to the outer peripheral side rather than the ring part 5c of the Oldham keyway 3c. Moreover, the ceiling part 23 is installed in the vicinity of both terminal ends of the reciprocating movement amount of the Oldham ring 5 where the inertial force of the Oldham ring 5 is maximized. The ceiling part 23 is firmly attached by using a fastening member 23b such as a bolt.

  The ring portion 5c of the Oldham ring 5 is disposed on the Oldham sliding surface 3d of the frame 3 so as to be able to reciprocate along the Oldham key groove 3c. Moreover, the moving distance of the reciprocating motion of the Oldham ring 5 is determined by the shape of the spiral (wrap portion 1a, wrap portion 2a). Therefore, in the refrigerant compressor A, it can respond | correspond by replacing | exchanging only the ceiling part 23 according to the shape of a spiral, ie, according to the movement distance of the reciprocating motion of the Oldham ring 5. FIG. The gap between the upper surface of the key portion 5b and the lower surface of the ceiling portion 23 is approximately the same as the gap between the key portion 5b and the Oldham key groove 3c so that the key portion 5b can slide.

  The ceiling part 23 is formed of a material having good slidability, such as iron-based metal such as cast iron and sintering, or aluminum-based mixed metal. For the purpose of further improving the slidability, only the lower surface of the ceiling portion 23 or the surface of the ceiling portion 23 including the lower surface of the ceiling portion 23 is formed on the DLC, DLC-Si, CrN, TiN, TiCN, TiAlN, WCC. , VC or any other coating treatment such as manganese phosphate coating, molybdenum disulfide coating, or hard alumite treatment.

[Operation of ceiling part 23]
FIG. 3 is a schematic cross-sectional view for explaining the action of the ceiling portion 23 with respect to the reciprocating motion of the Oldham ring 5. Based on FIG. 3, the action of the ceiling portion 23 on the reciprocating motion of the Oldham ring 5 will be described in detail together with the reciprocating motion of the Oldham ring 5. FIG. 3A shows the state when the Oldham ring 5 reciprocates (moves left and right in the figure) along the Oldham key groove 3c of the frame 3 and the moving distance becomes maximum (when it moves to the left most). FIG. 3B shows a state when the Oldham ring 5 starts to move to the right side of the drawing.

  In FIG. 3 (a), an inertial force acts on the Oldham ring 5 in the left direction of the drawing. However, since the key portion 5a is regulated by the Oldham key groove 2c of the orbiting scroll 2, the Oldham ring 5 is rotated clockwise. Overturn. On the other hand, in the refrigerant compressor A, the lower surface of the ceiling portion 23 is slidable with the upper surface of the key portion 5b of the Oldham ring 5, and the upper surface of the key portion 5b of the Oldham ring 5 is disposed on the lower surface of the ceiling portion 23 with Oldham. The overturning of the Oldham ring 5 is suppressed by installing the ceiling portion 23 at a position where the overturning of the ring 5 is restricted.

  As shown in FIG. 3, the ceiling portion 23 does not cover the entire upper part of the Oldham key groove 3 c of the frame 3, and the gap between the outermost end wall of the Oldham key groove 3 c of the frame 3 and the opposing outer peripheral surface thereof. And a space (space portion 70 shown in FIG. 3). Therefore, in the state shown in FIG. 3A, even if the Oldham key groove 3c of the frame 3 is filled with the lubricating oil, the lubricating oil can flow out of the space portion 70 (dotted arrow shown in FIG. 3A). . On the other hand, when the Oldham key groove 3c of the frame 3 is in a vacuum state in the state shown in FIG. 3B, the lubricating oil can flow from the space portion 70 (dotted line arrow shown in FIG. 3B).

[Operation of Refrigerant Compressor A]
The operation of the refrigerant compressor A will be described.
When power is supplied to the motor stator 7, the motor rotor 6 rotates by receiving a rotational force from the rotating magnetic field generated by the motor stator 7. The main shaft 8 is rotationally driven by the rotation of the electric motor rotor 6. In addition, although a general commercial power source of 50 Hz or 60 Hz is used as the power source, in the refrigerant compressor A, an inverter power source is also used so that the driving rotational speed can be driven in a range of 600 rpm to 15000 rpm in order to vary the refrigerant circulation amount. Has been.

  When the main shaft 8 is driven to rotate, the eccentric slider shaft 8 a rotates in the rocking bearing via the slider 9 and is transmitted to the rocking scroll 2. At this time, the Oldham ring 5 that reciprocates inside the Oldham key groove 2 c of the swing scroll 2 that houses the key portion 5 a of the Oldham ring 5 and the Oldham key groove 3 c of the frame 3 that houses the key portion 5 b of the Oldham ring 5. Thus, the orbiting scroll 2 is restrained from rotating and performs an orbiting motion.

  As described above, the frame 3 and the subframe 13 are fixed in the sealed container 17. An axial misalignment between the main bearing 3a and the ball bearing 14 occurs due to variations in accuracy when the frame 3 and the sub-frame 13 are fixed and variations in accuracy of individual components. Further, the deflection of the main shaft 8 is also added, and the main bearing 3a and the main shaft 8, and the ball bearing 14 and the main shaft 8 are not necessarily parallel. Here, in the refrigerant compressor A, the sleeve 10 is accommodated between the main shaft 8 and the main bearing 3a in order to make the sliding surface in the main bearing 3a parallel. Therefore, when the axial misalignment between the main bearing 3a and the ball bearing 14 occurs, the main shaft 8 is inclined with respect to the main bearing 3a, but the second pipette portion (not shown) is in contact with the inner peripheral surface of the sleeve 10, The second pipette portion absorbs the inclination, so that the outer periphery of the sleeve 10 can always slide in parallel with the main bearing 3a.

  When the swing scroll 2 swings, a centrifugal force is generated in the swing scroll 2, and the eccentric slider shaft 8a of the main shaft 8 slides within a slidable range on a slide surface (not shown) in the slider 9. The centrifugal load of the orbiting scroll 2 and the radial load generated to compress the refrigerant are applied to the eccentric slider shaft 8a of the main shaft 8, and the eccentric slider shaft 8a bends, whereby the outer peripheral surface of the eccentric slider shaft 8a. However, it is not always parallel to the inner wall surface of the boss 2e.

  Here, in the refrigerant compressor A, the slider 9 is accommodated between the eccentric slider shaft 8a of the main shaft 8 and the oscillating bearing in order to make the sliding surfaces in the oscillating bearing parallel. Therefore, when the eccentric slider shaft 8a is bent, the eccentric slider shaft 8a is inclined with respect to the swing bearing, but the first pipette portion (not shown) is in contact with the slider surface of the slider 9, and the inclination is changed to the first pipette portion. The outer periphery of the slider 9 can always slide in parallel with the rocking bearing.

  The refrigerant that can be used in the refrigerant compressor A has a double bond of carbon in the composition of HFO refrigerant having an ozone depletion coefficient of zero, HFO1234yf, HFO1234ze, and HFO1243zf, which are called chlorofluorocarbon low GWP refrigerants. There are halogenated hydrocarbons, natural refrigerants such as propane and propylene, natural hydrocarbons, or mixed refrigerants obtained by appropriately mixing them.

  When the swing scroll 2 swings, the refrigerant in the refrigerant circuit is sucked into the sealed container 20 from the suction connection pipe 21, and the wrap portion 2 a of the swing scroll 2 and the fixed scroll 1 are wrapped from the suction port 3 b of the frame 3. It enters the compression chamber 25 formed by the part 1a. The compression chamber 25 moves to the center of the rocking scroll 2 by the rocking motion of the rocking scroll 2. Thereby, the refrigerant in the compression chamber 25 is compressed by further reducing the volume. At this time, the fixed refrigerant 1 and the orbiting scroll 2 are subjected to a load that tends to be separated in the axial direction by the compressed refrigerant, but in a bearing constituted by the thrust bearing portion 2 d of the orbiting scroll 2 and the thrust plate 4. Supports the load.

  The refrigerant compressed in the compression chamber 25 passes through the discharge port 1 c of the fixed scroll 1, pushes open the discharge valve 24, passes through the high-pressure portion in the sealed container 20, and is discharged from the sealed container 20 through the discharge connection pipe 22. The This refrigerant circulates in the external refrigerant circuit and is then sucked into the refrigerant compressor A again.

Next, the flow of the lubricating oil will be described.
The lubricating oil stored in the oil sump 16 of the sealed container 20 is pumped up in the oil hole 8c of the main shaft 8 by driving the oil pump 15 by the pump shaft 8b by the rotation of the main shaft 8, and each sliding portion. To lubricate each sliding part.

  The sliding portions are the sliding portions of the thrust bearing portion 2d and the thrust plate 4 of the orbiting scroll 2, the wrap portion 2a of the orbiting scroll 2, the wrap portion 1a of the fixed scroll 1, and the lap portion 1a of the fixed scroll 1. The seal disposed on the front end surface of the oscillating scroll 2 and the tooth bottom surface of the end plate 2b of the swing scroll 2 on the lap portion 2a side, the seal disposed on the front end surface of the wrap portion 2a of the swing scroll 2 and the end plate of the fixed scroll 1 This is the tooth bottom surface on the side of the lap portion 1a.

  Other sliding parts to which the lubricating oil is supplied include the Oldham key groove 2c of the orbiting scroll 2, the key part 5a of the Oldham ring 5, the Oldham key groove 3c of the frame 3, and the key part 5b of the Oldham ring 5. The first pivot part of the eccentric slider shaft 8a for mounting the rocking bearing (boss portion 2e) of the rocking scroll 2 and the outer periphery of the slider 9 and the slider 9 which is eccentric with respect to the rotation center of the main shaft 8 and drives the rocking shaft. There are a slide surface of the slider 9, an outer periphery of the sleeve 10 that supports rotation of the main bearing 3 a and the main shaft 8, an inner side of the sleeve 10, a second pipette portion of the main shaft 8, and the like.

  In addition, since these sliding parts become high temperature, they are the same atmosphere as the comparatively low temperature refrigerant | coolant suck | inhaled in the airtight container 20, and are cooled with this refrigerant | coolant. In addition, the relatively low temperature refrigerant sucked into the sealed container 20 has an effect of cooling the motor rotor 6 and the motor stator 7, and the suction connection pipe 21 for taking in the refrigerant from the refrigerant circuit includes the frame 3 and the motor stator. It is good to comprise so that it may be connected to each vicinity of 7.

  The surface of the Oldham sliding surface 3d of the frame 3 on which the Oldham ring 5 slides is filled with lubricating oil, and is used for lubricating the ring portion 5c of the Oldham ring 5 and the Oldham sliding surface 3d of the frame 3. . In addition, the lubricating oil lubricates the thrust bearing portion 2 d of the orbiting scroll 2 and the sliding portion of the thrust plate 4. The lubricating oil leaked to the side of the wrap portion 2a of the end plate 2b of the swing scroll 2 is taken into the compression chamber 25 together with the refrigerant taken into the frame 3 from the suction port 3b of the frame 3, and the swing scroll 2 The wrap portion 2a and the wrap portion 1a of the fixed scroll 1, the seal disposed on the tip surface of the wrap portion 1a of the fixed scroll 1 and the tooth bottom surface of the oscillating scroll 2 on the lap portion 2a side, It is used to lubricate the seal disposed on the front end surface of the wrap portion 2a and the tooth bottom surface of the fixed scroll 1 on the lap portion 1a side.

  Thereafter, the lubricating oil passes through the discharge port 1c of the fixed scroll 1 together with the refrigerant gas, pushes the discharge valve 24 open, passes through the high pressure portion in the sealed container 20, and passes through the discharge connecting pipe 22 from the sealed container 20. It is discharged and returns from the suction connection pipe 21 of the compressor around the refrigerant pipe of the refrigerating and air-conditioning equipment.

[Effects of refrigerant compressor A]
As described above, according to the refrigerant compressor A, the ceiling portion 23 can be provided even if the inertial force of the Oldham ring 5 is increased by providing the ceiling portion 23 capable of suppressing the overturn of the Oldham ring 5 above the Oldham key groove 3c. Can be corrected by pressing the upper surface of the key portion 5b, and the overturn of the Oldham ring 5 can be suppressed. Therefore, the sliding state of the Oldham key groove 2c of the orbiting scroll 2 and the key portion 5a of the Oldham ring 5 can slide on as large a surface as possible, and the Oldham key groove 2c of the orbiting scroll 2 and the key portion 5a of the Oldham ring 5 A highly reliable refrigerant compressor that can reduce wear and avoid damage to the Oldham ring 5 can be obtained.

  Further, the refrigerant compressor A is a refrigerant having a low global warming potential (GWP) such as a chlorofluorocarbon low GWP refrigerant such as HFO1234yf or a hydrocarbon natural refrigerant such as propane, which needs to increase the circulation amount of the refrigerant. Also in this transition, it is possible to easily cope with the case where the operating rotational speed is increased or the stroke volume is increased.

  Further, according to the refrigerant compressor A, the Oldham ring 5 can be prevented from being overturned even if a high rigidity iron-based metal that could not be used because the inertial force is increased in the Oldham ring 5 is compressed. It becomes possible to maintain the angular phase combined with the lap portions (the lap portion 1a and the lap portion 2a) forming the chamber 25 with high accuracy, and to achieve higher performance.

  Furthermore, since the ceiling portion 23 is disposed near both ends of the reciprocating movement of the Oldham ring 5 where the inertial force of the Oldham ring 5 becomes the largest, the inside of the Oldham key groove 3c of the frame 3 is made of lubricating oil. Even if it is satisfied, the lubricating oil can flow out from the space portion 70 formed on the back side of the ceiling portion 23. Therefore, according to the refrigerant compressor A, power for compressing the lubricating oil is not generated, and a high-performance state can be maintained without increasing the necessary power of the refrigerant compressor A.

  Specifically, FIG. 3A shows a state when the movement distance of the Oldham ring 5 is maximized. At this time, the Oldham key groove 3c of the frame 3 is filled with lubricating oil. Even so, since the space portion 70 is formed between the ceiling portion 23 and the outermost end wall of the Oldham key groove 3 c of the frame 3, the lubricating oil can flow out from the space portion 70. Therefore, no power is generated to compress the lubricating oil, and high performance can be maintained without increasing the required power of the refrigerant compressor A.

  FIG. 3B shows a state when the Oldham ring 5 starts to move to the right side of the page. Even if the Oldham key groove 3c of the frame 3 is in a vacuum state, the ceiling portion 23 and the frame Since the space portion 70 is formed between the three Oldham key grooves 3 c and the outermost end wall, the lubricating oil can flow from the space portion 70. Therefore, in the refrigerant compressor A, no power is generated due to the vacuum state.

  The above effect is not only the HFC refrigerant that requires a large amount of refrigerant circulation, the ozone layer depletion coefficient is zero, but also the composition of carbon such as HFO1234yf, HFO1234ze, and HFO1243zf, which are called chlorofluorocarbon-based low GWP refrigerants. When using a halogenated hydrocarbon having a double bond, a natural hydrocarbon such as propane or propylene, or a mixed refrigerant obtained by appropriately mixing them, the effect is further increased. When such a refrigerant is used, in order to obtain performance equivalent to that of R410A, which is a fluorocarbon refrigerant mainly used as an HFC refrigerant having an ozone layer depletion coefficient of zero, the refrigerant compressor A has an operating rotational speed. It is necessary to take measures such as increasing the speed or increasing the stroke volume.

  Then, as described above, the overturn of the Oldham ring 5 is increased, but by suppressing the overturn of the Oldham ring 5 by the ceiling portion 23, the refrigerant compressor A can be installed even if a refrigerant having a small global warming coefficient is used. It is possible to configure with high efficiency. That is, when the operating speed is increased, the inertial force increases in proportion to the operating speed, and when the stroke volume is increased, the distance of the reciprocating motion of the Oldham ring 5 is increased and the inertial force is increased. Since the load applied to the key portions 5a and 5b of the ring 5 also increases, the structure that suppresses the overturning of the Oldham ring 5 is more effective.

Embodiment 2. FIG.
FIG. 4 is a schematic cross-sectional view for explaining the action of the ceiling portion 23 on the reciprocating motion of the Oldham ring 5 of the refrigerant compressor according to Embodiment 2 of the present invention. Based on FIG. 4, the action of the ceiling 23 on the reciprocating motion of the Oldham ring 5 will be described in detail together with the reciprocating motion of the Oldham ring 5 of the refrigerant compressor according to the second embodiment. In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.

  In the first embodiment, the structure in which the ceiling portion 23 is attached to both of the Oldham key grooves 3c of the pair of frames 3 has been described. However, in Embodiment 2, the ceiling portion 23 is attached to one of the Oldham key grooves 3c of the frame 3. The structure will be described. Note that FIG. 4 shows a cross section on the side where the ceiling portion 23 is attached. FIG. 4A shows a state when the Oldham ring 5 is reciprocated along the Oldham key groove 3c of the frame 3 (left-right movement in the figure) and the moving distance becomes maximum (when moved to the left most). FIG. 4 (b) shows the state when the Oldham ring 5 reaches the maximum distance on the opposite side (when moved to the right most).

  In the state shown in FIG. 4A, the arrangement position of the ceiling part 23 is determined so as to be a bare position that does not contact the ring part 5 c of the Oldham ring 5. Moreover, the arrangement | positioning position of the ceiling part 23 is determined so that it may overlap with the upper surface of the key part 5b of the Oldham ring 5 in the state shown in FIG.4 (b). That is, as shown in FIG. 4B, in the state where the Oldham ring 5 is moved to the rightmost side, the ceiling portion 23 and the key portion 5b of the Oldham ring 5 are overlapped with the lower surface of the ceiling portion 23. The size and positional relationship of the key portion 5b of the Oldham ring 5 are adjusted. Note that, except for the size and the positional relationship of the ceiling portion 23 and the key portion 5b of the Oldham ring 5, it is the same as in the first embodiment.

[Effects of refrigerant compressor according to Embodiment 2]
As described above, according to the refrigerant compressor according to the second embodiment, the upper surface of the key portion 5b of the Oldham ring 5 is different from the lower surface of the ceiling portion 23 at any time when the movement distance of the Oldham ring 5 is maximum. It is configured to overlap. As a result, the same effect as in the first embodiment can be obtained by attaching the ceiling portion 23 only to one of the Oldham key grooves 3 c of the frame 3.

  Specifically, the ceiling portion 23 only needs to be attached to one of the Oldham key grooves 3c of the frame 3, and even if the inertial force of the Oldham ring 5 increases, the overturn of the Oldham ring 5 can be suppressed. Moreover, since it is only necessary to attach the ceiling part 23 to only one of the Oldham key grooves 3c of the frame 3, the wear of the Oldham key groove 2c in the swing scroll 2 and the key part 5a of the Oldham ring 5 can be reduced. In addition, a highly reliable refrigerant compressor that can avoid damage to the Oldham ring 5 can be obtained. As a result, the number of parts can be reduced and the production time can be shortened, so that the cost can be reduced.

Embodiment 3 FIG.
FIG. 5 is a schematic cross-sectional view for explaining the action of the ceiling portion 23 on the reciprocating motion of the Oldham ring 5 of the refrigerant compressor according to Embodiment 3 of the present invention. Based on FIG. 5, the action of the ceiling 23 on the reciprocating motion of the Oldham ring 5 will be described in detail together with the reciprocating motion of the Oldham ring 5 of the refrigerant compressor according to the third embodiment. In the third embodiment, differences from the first and second embodiments will be mainly described, and the same parts as those in the first and second embodiments will be denoted by the same reference numerals and the description thereof will be omitted.

  In the first and second embodiments, the structure in which the ceiling portion 23 is attached to both or one of the Oldham key grooves 3c of the pair of frames 3 has been described. However, in the third embodiment, the Oldham key groove 3c of the ceiling portion 23 and the frame 3 is described. The structure using the key part 5b of the Oldham ring 5 as a piston will be described using the space constituted by the cylinder as a cylinder. That is, in the embodiment, the ceiling portion 23 is installed so as to be in contact with the outermost end wall of the Oldham keyway 3 c of the frame 3. In addition, in FIG. 5, the cross section of either one of the ceiling parts 23 is shown. FIG. 5 (a) shows the state when the Oldham ring 5 reciprocates along the Oldham key groove 3c of the frame 3 (left and right movement in the figure) and the moving distance becomes maximum (when it moves to the left most). FIG. 5B shows the state when the Oldham ring 5 starts to move to the right side of the drawing.

  In Embodiment 3, the ceiling part 23 in which the oil drain hole 23a is formed covers the upper part of the Oldham key groove 3c of the frame 3 so as to cover it. The Oldham key groove 3c and the rocking motion space (the rocking scroll storage portion 3h) in which the rocking scroll 2 in the frame 3 performs rocking motion communicate with the outermost end wall of the Oldham key groove 3c of the frame 3. An oil supply path 26 is formed. Further, a check valve 27 is provided between the Oldham key groove 3c in the oil supply path 26 and the swing motion space in a direction to prevent the flow of lubricating oil from the swing motion space to the Oldham key groove 3c of the frame. Yes. Further, the thrust plate 4 is provided with an oil supply hole 4a communicating with the oil supply path 26, so that the oil supply path 26 and the swing motion space are not blocked.

  Normally, the Oldham key groove 3c of the frame 3 is filled with lubricating oil, so that the space formed by the ceiling portion 23 and the Oldham key groove 3c of the frame 3 functions as a cylinder. Then, as shown in FIG. 5A, the key portion 5 b of the Oldham ring 5 functions as a piston, and the space formed by the key portion 5 b of the Oldham ring 5 is formed by the ceiling portion 23 and the Oldham key groove 3 c of the frame 3. The lubricating oil accumulated in the oil flows into the oil supply passage 26, pushes the check valve 27 open, and is ejected into the swing motion space. On the other hand, in the state of FIG. 5B, the check valve 27 is closed to prevent the backflow of the refrigerant gas from the swing motion space.

[Effects of the refrigerant compressor according to Embodiment 3]
As described above, according to the refrigerant compressor according to the third embodiment, the same effect as in the first embodiment is achieved, and the ceiling portion 23 and the Oldham key groove 3c form a space that functions as a cylinder. Lubricating oil can be further supplied to the rocking motion space. Therefore, more lubricating oil is taken into the compression chamber 25 together with the refrigerant, the sliding characteristics of the sliding portion by the fixed scroll 1 and the swing scroll 2 are improved, and it is possible to reduce the sliding loss. In addition, reliability can be improved.

  Further, since the oil drain hole 23a is formed in the ceiling portion 23, even if the moving distance in which the key portion 5b of the Oldham ring 5 serving as a piston reciprocates along the Oldham key groove 3c increases, the oil passage 26 swings. The amount of lubricating oil ejected into the dynamic motion space can be easily adjusted. According to this oil supply method, the amount of oil supply per rotation, that is, one reciprocation of the Oldham ring 5 can be set reliably. Therefore, in contrast to the conventional case where the thrust bearing portion 2d of the orbiting scroll 2 and the sliding portion of the thrust plate 4 are lubricated with the leaked oil, the sliding by the fixed scroll 1 and the orbiting scroll 2 is performed. The sliding characteristics of the part can be stabilized.

  In the third embodiment, the case where a spherical valve is used as the check valve 27 is illustrated as an example. However, the present invention is not limited to this, and a configuration using a leaf spring or the like may be used. The third embodiment can be applied to any of the first and second embodiments as long as the ceiling portion 23 is installed so as to be in contact with the outermost end wall of the Oldham keyway 3c of the frame 3.

  1 fixed scroll, 1a wrap part, 1b end plate, 1c discharge port, 2 swing scroll, 2a wrap part, 2b end plate, 2c Oldham keyway, 2d thrust bearing part, 2e boss part, 3 frame, 3a main bearing, 3b suction port 3c Oldham keyway, 3d Oldham sliding surface, 3e Center opening, 3f Boss storage, 3g Oldham ring storage, 3h Oscillating scroll storage, 4 Thrust plate, 4a Oiling hole, 5 Oldham ring, 5a Key 5b Key portion, 5c Ring portion, 6 Motor rotor, 7 Motor stator, 8 Main shaft, 8a Eccentric slider shaft, 8b Pump shaft, 8c Oil hole, 9 Slider, 10 Sleeve, 11 Balancer, 12 Balancer, 13 Subframe, 14 Ball bearing, 15 Oil pump, 16 Oil sump 17 Sealed container, 18 Under sealed container, 19 On sealed container, 20 Sealed container, 21 Suction connection pipe, 22 Discharge connection pipe, 23 Ceiling part, 23a Oil drain hole, 23b Fastening member, 24 Discharge valve, 25 Compression chamber, 26 oil supply path, 27 check valve, 50 compression element part, 60 drive element part, 70 space part, A refrigerant compressor.

Claims (8)

A fixed scroll with a lap portion standing on one side of the end plate;
An oscillating scroll arranged so that a lap portion is erected on one surface of the end plate, and this lap portion is engaged with the wrap portion of the fixed scroll;
An Oldham ring disposed on the back side of the orbiting scroll to prevent the orbiting scroll from rotating,
An Oldham key groove for slidably storing the key portion of the Oldham ring is formed at two opposing positions, and a frame that supports the swing scroll so as to be swingable.
When at least one of the Oldham key grooves is reciprocated in the Oldham key groove and the moving distance to the outside in the radial direction is maximized, the upper surface overlaps with the upper surface of the key section. A ceiling provided at a position to be
A refrigerant compressor characterized by comprising: The ceiling part is
The refrigerant compressor according to claim 1, wherein the refrigerant compressor is provided in each of the Oldham key grooves. The ceiling part is
2. The refrigerant compressor according to claim 1, wherein the lower surface of the key portion overlaps with the upper surface of the key portion while the key portion reciprocates in the Oldham key groove. The ceiling part is
The refrigerant compressor according to any one of claims 1 to 3, wherein the refrigerant compressor is disposed with a space from an outermost end wall of the Oldham keyway. The ceiling is installed in contact with the outermost end wall of the Oldham keyway,
An oil supply path that communicates from the outermost end wall of the Oldham keyway to a swinging motion space in which the swinging scroll in the frame swings is provided,
The refrigerant compressor according to any one of claims 1 to 3, wherein a reverse support valve is provided in the oil supply path in a direction to prevent a flow from the rocking motion space to the Oldham key groove. In the ceiling,
The refrigerant compressor according to claim 5, wherein an oil drain hole for adjusting an oil supply amount from the Oldham key groove is provided. The frame is provided with a thrust plate for supporting a thrust bearing load of the orbiting scroll,
In the thrust plate,
The refrigerant compressor according to claim 5 or 6, wherein an oil supply hole for communicating the oil supply path and the rocking motion space is formed. The refrigerant according to any one of claims 1 to 7, wherein the refrigerant is a halogenated hydrocarbon refrigerant having a carbon double bond in the composition, a hydrocarbon refrigerant, or a refrigerant obtained by mixing them. Compressor.

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