WO2016072013A1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

Info

Publication number
WO2016072013A1
WO2016072013A1 PCT/JP2014/079577 JP2014079577W WO2016072013A1 WO 2016072013 A1 WO2016072013 A1 WO 2016072013A1 JP 2014079577 W JP2014079577 W JP 2014079577W WO 2016072013 A1 WO2016072013 A1 WO 2016072013A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
main shaft
scroll compressor
lubricating oil
oil
Prior art date
Application number
PCT/JP2014/079577
Other languages
French (fr)
Japanese (ja)
Inventor
光勇 太田
修平 小山
功一 福原
長田　淳
祐司 ▲高▼村
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2014/079577 priority Critical patent/WO2016072013A1/en
Publication of WO2016072013A1 publication Critical patent/WO2016072013A1/en

Links

Images

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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • 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
    • F04C29/02—Lubrication; Lubricant separation

Definitions

  • the present invention relates to a scroll compressor.
  • a main shaft a frame having a main bearing for supporting the upper portion of the main shaft, a sub frame having a sub bearing for supporting the lower portion of the main shaft, and a pump provided on the lower end side of the main shaft and having a pump casing.
  • the pump casing is provided with a radial groove whose one end stops on the inner side of the outer diameter of the main shaft on the upper end surface and whose other end is open to the outer periphery, and the subframe is a bottom of the pump element housing portion.
  • the scroll fluid compressor described in Patent Document 1 drives the pump by rotating the main shaft
  • the supply amount of the lubricating oil depends on the rotational speed of the main shaft. For this reason, the supply amount of the lubricating oil increases as the rotational speed of the main shaft increases, so that an excessive amount of lubricating oil is supplied to the bearing and the swirl to increase the oil rise, and the lubricating oil supplied to the bearing and the swirl is sealed. It may be discharged outside the container. Accordingly, there is a problem that the amount of lubricating oil stored in the sealed container is reduced, and mechanical loss such as bearing damage and seizure occurs.
  • the present invention has been made against the background of the above-described problems, and an object thereof is to obtain a scroll compressor capable of reducing mechanical loss and operating at high speed.
  • a scroll compressor includes a sealed container having an oil reservoir, a main shaft provided inside the sealed container, a pump driven by rotation of the main shaft, and a pump provided above the pump.
  • a gap is provided between the lower surface of the pump casing and the upper surface of the pump so as to communicate the low pressure portion and the high pressure portion.
  • a gap is provided between the lower surface of the pump casing and the upper surface of the pump so as to communicate the low pressure portion and the high pressure portion.
  • FIG. 1 is a cross-sectional view of a scroll compressor 100 according to Embodiment 1 of the present invention.
  • the scroll compressor 100 includes an orbiting scroll 1, a fixed scroll 2, a frame 3, a main shaft 4, a stator 5, a rotor 6, a subframe 8, and ball bearings 9.
  • the pump 10 and the oil pipe 17 are provided.
  • the outer shell of the scroll compressor 100 is composed of a sealed container 100A.
  • the orbiting scroll 1 is a member having a base plate 1a and spiral teeth 1b.
  • the fixed scroll 2 is a member having a base plate 2a and spiral teeth 2b.
  • the swing scroll 1 and the fixed scroll 2 are combined to form a compression chamber 30.
  • the swing scroll 1 and the fixed scroll 2 are accommodated in a frame 3.
  • the frame 3 is a member fixed to the sealed container 100A in the upper part of the sealed container 100A, and has a main bearing 3a.
  • the main bearing 3a supports the upper part of the main shaft 4 rotatably.
  • the main shaft 4 is a member extending in the vertical direction of the sealed container 100 ⁇ / b> A, and has a pump shaft 4 b that transmits a rotational force to the pump 10.
  • the main shaft 4 is provided with an oil hole 4c through which lubricating oil is passed.
  • a stator 5 and a rotor 6 are provided outside the outer surface of the main shaft 4.
  • the stator 5 is a member configured in a substantially cylindrical shape, for example, and is fixed to the sealed container 100A.
  • the rotor 6 is a member configured in a substantially cylindrical shape, for example, and the main shaft 4 is inserted therethrough.
  • the stator 5 and the rotor 6 constitute an electric motor part of the scroll compressor 100.
  • a subframe 8 is provided below the stator 5 and the rotor 6.
  • the subframe 8 is a member fixed to the sealed container 100A at the lower part inside the sealed container 100A, and has a ball bearing 9.
  • the ball bearing 9 supports the lower part of the main shaft 4 rotatably.
  • a pump 10 is fixed to the lower end surface of the ball bearing 9.
  • the pump 10 is a member that sucks the lubricating oil stored in the oil reservoir 16 and supplies the lubricating oil to each sliding portion, and is constituted by a positive displacement pump, for example.
  • the pump 10 will be described in detail with reference to FIG.
  • the oil sump 16 is a part where lubricating oil is stored, and is provided at the bottom of the sealed container 100A.
  • An oil pipe 17 is immersed in the oil reservoir 16.
  • the oil pipe 17 is configured by, for example, a cylindrical member that passes through the upper and lower surfaces.
  • FIG. 2 is a cross-sectional view showing a main part of the scroll compressor 100 according to Embodiment 1 of the present invention.
  • the pump 10 is provided with a low pressure part 20a and a high pressure part 20b.
  • a pump cover 12 is provided below the pump 10, and a pump casing 11 is provided above the pump 10.
  • the low-pressure part 20a is a space through which the lubricant before compression among the lubricant flowing through the pump 10 flows, and is provided so as to penetrate part of the upper and lower surfaces of the pump 10.
  • the low pressure part 20a communicates with the suction port 13a.
  • the suction port 13a is a space for allowing the lubricating oil discharged from the oil pipe 17 to pass through the low pressure portion 20a.
  • the high-pressure portion 20b is a space through which the compressed lubricating oil out of the lubricating oil flowing through the pump 10 flows, and is provided so as to penetrate part of the upper and lower surfaces of the pump 10.
  • the high pressure portion 20b communicates with the discharge port 13b.
  • the discharge port 13b is a space for allowing the lubricating oil discharged from the high pressure portion 20b to pass through the oil hole 4c.
  • the pump cover 12 is a member that covers the pump 10 and has a storage portion 12a.
  • the pump cover 12 is bolted and fixed to the lower end surface of the subframe 8.
  • the upper end surface of the pump cover 12 and the lower end surface of the ball bearing 9 are in contact with each other.
  • An oil pipe 17 is located below the pump cover 12. By providing the oil pipe 17 at the lower part of the pump cover 12, the inside of the pump cover 12 and the inside of the oil pipe 17 communicate with each other.
  • the pump casing 11 is a member housed in the housing portion 12a and is fixed by caulking the pump cover 12.
  • the pump casing 11 is provided so as to face the upper surface of the pump 10.
  • a gap ⁇ is provided between the pump casing 11 and the pump 10.
  • a gap ⁇ is provided between the lower surface of the pump casing 11 and the upper surface of the pump 10.
  • the gap ⁇ is provided on the inner side (center side) of the outer shape of the pump casing 11 so that the low pressure portion 20a and the high pressure portion 20b communicate with each other.
  • the rotor 6 When power is supplied to the stator 5, the rotor 6 generates torque and rotates together with the main shaft 4 to cause the orbiting scroll 1 to revolve. As a result, the volume of the compression chamber 30 gradually decreases, and the low-temperature and low-pressure gas refrigerant is discharged as a high-temperature and high-pressure gas refrigerant.
  • the pump shaft 4b rotates when the main shaft 4 rotates, and the pump 10 is driven when the pump shaft 4b rotates.
  • the lubricating oil stored in the oil reservoir 16 is guided to the pump 10 through the oil pipe 17 and the suction port 13a in this order.
  • the lubricating oil guided to the pump 10 is discharged from the pump 10 through the low pressure part 20a and the high pressure part 20b in this order.
  • the lubricating oil supplied from the high pressure part 20b to the low pressure part 20a via the gap ⁇ is mixed with the lubricating oil pumped up through the oil pipe 17 and compressed again by the pump 10. Part of the lubricating oil that has been compressed again is supplied from the high-pressure portion 20b to the low-pressure portion 20a through the gap ⁇ . The remainder of the compressed lubricating oil is discharged from the high-pressure part 20b and supplied to each sliding part through the discharge port 13b and the oil hole 4c in this order.
  • the flow path of the lubricating oil supplied from the high pressure section 20b to the low pressure section 20a is the same as the flow path of the lubricating oil supplied from the suction port 13a to the low pressure section 20a. In this way, the pressure of the lubricating oil flowing through the pump 10 decreases when the oil is discharged from the pump 10.
  • FIG. 3 is a characteristic diagram showing the relationship between the rotational speed of the main shaft 4 of the scroll compressor 100 according to Embodiment 1 of the present invention and the amount of lubricant supplied from the pump 10.
  • the horizontal axis of FIG. 3 indicates the rotational speed [rps] of the main shaft 4, and the vertical axis of FIG. 3 indicates the lubricating oil supply amount [cc / s].
  • the relationship between the rotation speed of the main shaft 4 and the supply amount of the lubricating oil supplied from the pump 10 will be described with reference to FIG.
  • a lubricating oil having a viscosity of 32 cst, a density of 0.9 g / cm 3 to 1.0 g / cm 3 and an oil temperature of ⁇ 20 ° C. to 80 ° C. is used.
  • a scroll compressor 100 using a 0.32 cm 3 / rev one is assumed.
  • FIG. 3 shows the relationship between the rotational speed of the main shaft and the lubricant supply amount in the conventional scroll compressor.
  • (A) in FIG. 3 shows the amount of lubricating oil supplied required when the scroll compressor is operated.
  • the supply amount of the lubricating oil when the gap ⁇ is provided is smaller than the supply amount of the lubricating oil when the gap ⁇ is not provided.
  • the difference between the amount of lubricant supplied when ⁇ is provided and the amount of lubricant supplied when no gap ⁇ is not provided is not large.
  • the rotational speed of the main shaft 4 increases, the difference between the supply amount of the lubricating oil when the gap ⁇ is provided and the supply amount of the lubricant oil when the gap ⁇ is not provided gradually increases.
  • the flow rate of the lubricating oil supplied from the high pressure portion 20b through the gap ⁇ to the low pressure portion 20a is proportional to the flow velocity of the lubricating oil when flowing through the gap ⁇ . Further, since the flow rate of the lubricating oil when flowing through the gap ⁇ depends on the pressure of the lubricating oil, the flow rate of the lubricating oil supplied from the high pressure portion 20b to the low pressure portion 20a through the gap ⁇ is equal to the pressure generated by the pump 10. Dependent.
  • the scroll compressor 100 includes, in the pump 10, the low pressure part 20a that communicates with the inside of the oil pipe 17, and the high pressure part 20b that has a higher pressure than the low pressure part 20a. , And a gap ⁇ is provided between the lower surface of the pump casing 11 and the upper surface of the pump 10 so as to communicate the low pressure portion 20a and the high pressure portion 20b. For this reason, during the operation of the scroll compressor 100, a part of the lubricating oil which has been compressed in the pump 10 and whose pressure has increased is supplied again from the high pressure part 20b to the low pressure part 20a via the gap ⁇ .
  • the gap ⁇ is configured to be provided by lowering the groove provided in the storage portion 12a toward the lower end surface, but is not limited thereto.
  • the gap ⁇ is provided between the lower surface of the pump casing 11 and the upper surface of the pump 10, and is configured to communicate the low pressure portion 20a and the high pressure portion 20b on the inner side (center side) of the outer shape of the pump casing 11. It only has to be.
  • Embodiment 2 unlike the first embodiment, the elastic body 21 is provided without providing the gap ⁇ .
  • items that are not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.
  • FIG. 4 is a cross-sectional view showing a main part of the scroll compressor 100 according to Embodiment 2 of the present invention.
  • FIG. 5 is a cross-sectional view showing a main part of scroll compressor 100 according to Embodiment 2 of the present invention.
  • FIG. 6 is a diagram illustrating an example of the elastic body 21 of the scroll compressor 100 according to Embodiment 2 of the present invention. The rotational speed of the main shaft 4 in FIG. 4 is smaller than the rotational speed of the main shaft 4 in FIG.
  • an elastic body 21 is provided inside the sealed container 100A.
  • the elastic body 21 is constituted by a coil spring having a shape as shown in FIG. 6, for example, and is provided between the pump casing 11 and the pump cover 12 and crimped.
  • One end of the elastic body 21 is located on the upper surface of the pump casing 11, and the other end of the elastic body 21 is located on the lower surface of the pump cover 12.
  • the elastic body 21 has a reference length.
  • the reference length of the elastic body 21 is, for example, a natural length.
  • the elastic body 21 In a state where the elastic body 21 has the reference length, the lower surface of the pump casing 11 and the upper surface of the pump 10 are in contact with each other, and the low pressure part 20a and the high pressure part 20b are not communicated with each other.
  • the elastic body 21 expands and contracts in the axial direction of the main shaft 4.
  • the pump casing 11 and the pump 10 are in contact, and specifically, the lower surface of the pump casing 11 and the upper surface of the pump 10 are in contact.
  • the gap ⁇ is provided as in Embodiment 1, not only the amount of lubricating oil supplied during high-speed operation but also the amount of lubricating oil supplied during low-speed operation is reduced compared to the conventional case. In this case, the lubricating oil may not be sufficiently supplied to each sliding portion.
  • the lubricating oil supply amount at the time of high-speed operation is reduced as compared with the conventional case, while the supply amount of the lubricating oil at the low-speed operation is not reduced, so that the lubricating oil at the low-speed operation is reduced. Is sufficiently supplied to each sliding portion.
  • FIG. 4 has shown the direction through which lubricating oil flows.
  • the same operations as those already described in the first embodiment are omitted as appropriate.
  • the pump casing 11 is pressed by the elastic body 21 during low-speed operation.
  • the pump casing 11 is pushed up and shown in FIG. It will be in a state to be.
  • the elastic body 21 is displaced so as to contract more than the reference length, so that the pump cover 12 and the pump 10 are not displaced. Is formed with a gap ⁇ . A part of the lubricating oil moves from the high pressure part 20b to the low pressure part 20a via the gap ⁇ .
  • the lubricating oil supplied from the high pressure part 20 b to the low pressure part 20 a via the gap ⁇ is mixed with the lubricating oil pumped up through the oil pipe 17 and compressed again by the pump 10.
  • a part of the lubricating oil compressed again is supplied from the high pressure part 20b to the low pressure part 20a through the gap ⁇ .
  • the remainder of the compressed lubricating oil is discharged from the high-pressure part 20b and supplied to each sliding part through the discharge port 13b and the oil hole 4c in this order.
  • the flow path of the lubricating oil supplied from the high pressure section 20b to the low pressure section 20a via the gap ⁇ is the same as the flow path of the lubricating oil supplied from the suction port 13a to the low pressure section 20a. In this way, the pressure of the lubricating oil flowing through the pump 10 decreases when the oil is discharged from the pump 10.
  • the elastic body 21 of the scroll compressor 100 will be described below.
  • the elastic body 21 receives a compressive force due to the pressure in the pump 10.
  • F1 can be calculated using the following (Equation 1).
  • F1 P ⁇ A (Formula 1)
  • P Pressure in the pump 10
  • A Area of the portion where the pump casing 11 and the pump 10 are in contact with each other
  • the pump casing 11 is pressed against the upper end surface of the pump 10 by the reaction force of the elastic body 21.
  • the pump casing 11 is pushed upward in the axial direction of the main shaft 4 by the pressure in the pump 10.
  • a gap ⁇ is formed between the pump casing 11 and the pump 10.
  • the pressure P in the pump 10 can be lowered by deforming the elastic body 21 with a predetermined pressure.
  • the pressure P in the pump 10 is related to the flow rate Q of the pump 10 and can be calculated using the following (Equation 4).
  • P ⁇ ⁇ (Q / C ⁇ A) 2/2 ⁇ ( Equation 4)
  • C Outflow coefficient ⁇ : Lubricating oil density
  • the flow rate Q of the pump 10 can be calculated using the following (Formula 5).
  • Q q ⁇ n (Formula 5)
  • q Discharge amount of the pump 10
  • n Number of rotations of the scroll compressor 100 (main shaft 4)
  • the pressure P at each rotational speed of the main shaft 4 is calculated using the above-described (Formula 1) to (Formula 5), the spring constant k is calculated based on the calculated pressure P, and the material and shape of the elastic body 21 are determined. To do.
  • the flow rate Q of the pump 10 can be calculated as follows using the above (Formula 5).
  • the pressure P can be calculated as follows using the above-described (Formula 4).
  • the outflow coefficient C is 1.
  • the spring constant k can be calculated as follows using (Equation 3) described above.
  • the elastic body 21 is configured with a material and a shape such that the spring constant k is within the above-described value range.
  • FIG. 7 is a characteristic diagram showing the relationship between the rotational speed of the main shaft 4 of the scroll compressor 100 according to Embodiment 2 of the present invention and the supply amount of the lubricating oil supplied from the pump 10.
  • the horizontal axis of FIG. 7 shows the rotational speed [rps] of the main shaft 4, and the vertical axis of FIG. 7 shows the lubricating oil supply amount [cc / s].
  • the relationship between the rotation speed of the main shaft 4 and the supply amount of the lubricating oil supplied from the pump 10 will be described with reference to FIG.
  • a lubricating oil having a viscosity of 32 cst, a density of 0.9 g / cm 3 to 1.0 g / cm 3 and an oil temperature of ⁇ 20 ° C. to 80 ° C. is used.
  • the scroll compressor 100 is assumed to use a pump 10 having a discharge amount of 0.32 cm 3 / rev. Further, in FIG. 7, it is assumed that the scroll compressor 100 has an operating range of 10 rps to 240 rps and an area where the pump casing 11 and the pump 10 are in contact with each other is 415 mm 2 .
  • FIG. 7 shows the relationship between the rotational speed of the main shaft and the lubricant supply amount in a conventional scroll compressor.
  • the relationship between the rotational speed of the main shaft 4 and the lubricant supply amount is shown.
  • (A) in FIG. 7 has shown the amount of lubricating oil supply requested
  • the supply amount of lubricating oil in the scroll compressor 100 of the second embodiment and the conventional scroll compressor is substantially the same until the pump casing 11 is pushed up.
  • the rotation speed of the main shaft 4 when the pump casing 11 is not pushed up is, for example, in the range of 10 rps to 100 rps.
  • the pressure of the pump 10 increases and the pump casing 11 is pushed up.
  • the pump casing 11 is pushed up when the rotational speed of the main shaft 4 exceeds 100 rps.
  • the operation of the scroll compressor 100 is performed.
  • a lubricating oil supply amount close to the required lubricating oil supply amount can be obtained.
  • the scroll compressor 100 is attached so that one end is located on the lower surface of the pump cover 12 and the other end is located on the upper surface of the pump casing 11 and has an elastic length having a reference length.
  • the pump 10 is provided with a low-pressure part 20a communicating with the inside of the oil pipe 17, and a high-pressure part 20b having a higher pressure than the low-pressure part 20a.
  • the elastic body 21 is longer than the reference length.
  • the lubricating oil can be sufficiently supplied to each sliding portion without reducing the amount of the lubricating oil supplied during low-speed operation. .
  • the example using a coil spring was demonstrated as the elastic body 21, it is not limited to this.
  • a spring spring or the like may be used as the elastic body 21.
  • the specific numerical value of the rotation speed of the main shaft 4 is not limited to this.
  • the structure in which the lubricating oil is moved from the high-pressure portion 20b in the pump 10 to the low-pressure portion 20a through the gap ⁇ is not limited to this.
  • the discharge path 22 may be provided.
  • FIG. 8 is a cross-sectional view showing a main part of the scroll compressor 100 according to Embodiment 2 of the present invention, which is a modification of FIG.
  • the discharge path 22 is formed so that the lubricating oil flows out of the pump cover 12 through the gap ⁇ when the pump casing 11 is pushed up to form the gap ⁇ . .
  • the discharge path 22 is provided so as to penetrate the pump cover 12 in the horizontal direction at the same height as the gap ⁇ and to communicate with the outside of the pump cover 12. As a result, the amount of lubricating oil that moves from the high-pressure portion 20b to the low-pressure portion 20a via the gap ⁇ is reduced, and the recompression loss can be improved.
  • 1 swing scroll 1a base plate, 1b spiral tooth, 2 fixed scroll, 2a base plate, 2b spiral tooth, 3 frame, 3a main bearing, 4 main shaft, 4b pump shaft, 4c oil hole, 5 stator, 6 rotor, 8 Sub frame, 9 ball bearing, 10 pump, 11 pump casing, 12 pump cover, 12a storage part, 13a intake port, 13b discharge port, 16 oil reservoir, 17 oil pipe, 20a low pressure part, 20b high pressure part, 21 elastic body 22 discharge path, 30 compression chamber, 100 scroll compressor, 100A airtight container, C outflow coefficient, L height dimension, P pressure, Q flow rate, k spring constant, ⁇ , ⁇ gap.

Landscapes

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

Abstract

A scroll compressor is provided with: a closed container 100A having an oil sump 16; a main shaft 4 provided within the closed container 100A; a pump 10 driven when the main shaft 4 is rotated; a pump casing 11 provided above the pump 10; and an oil pipe 17 through which lubricating oil stored in the oil sump 16 flows. Inside the pump 10, there are provided: a low-pressure section 20a in communication with the inside of the oil pipe 17; and a high-pressure section 20b having a higher pressure than the low-pressure section 20a. An air gap δ is provided between the lower surface of the pump casing 11 and the upper surface of the pump 10 so as to connect the low-pressure section 20a and the high-pressure section 20b.

Description

スクロール圧縮機Scroll compressor
　本発明は、スクロール圧縮機に関する。 The present invention relates to a scroll compressor.
　従来、「主軸と、この主軸の上部を支持する主軸受を有するフレームと、前記主軸の下部を支持する副軸受を有するサブフレームと、前記主軸の下端側に設けられ、ポンプケーシングを有するポンプを備えたスクロール流体機械において、前記ポンプケーシングは上端面に一端が前記主軸の外径より内側で止まりとし、他端が外周に開口した放射溝を備え、前記サブフレームはそのポンプ要素収納部の底側に前記放射溝と連通する環状溝及びこの環状溝に一方が開口し、他方がその下端面に開口する副軸受排油路を備え、前記主軸はその下端面を前記ポンプケーシングの上端面に当接させた」スクロール流体圧縮機があった（例えば、特許文献１参照）。 Conventionally, “a main shaft, a frame having a main bearing for supporting the upper portion of the main shaft, a sub frame having a sub bearing for supporting the lower portion of the main shaft, and a pump provided on the lower end side of the main shaft and having a pump casing. In the scroll fluid machine provided, the pump casing is provided with a radial groove whose one end stops on the inner side of the outer diameter of the main shaft on the upper end surface and whose other end is open to the outer periphery, and the subframe is a bottom of the pump element housing portion. An annular groove communicating with the radiation groove on the side and a secondary bearing oil drainage passage with one opening at the annular groove and the other opening at the lower end surface thereof, the main shaft having the lower end surface at the upper end surface of the pump casing There was a scroll fluid compressor abutted (see, for example, Patent Document 1).
特開平５－２３１３５７号公報（［請求項１］、図１）JP-A-5-231357 ([Claim 1], FIG. 1)
　ここで、特許文献１に記載のスクロール流体圧縮機は、主軸を回転させることでポンプを駆動するようになっているため、潤滑油の供給量は主軸の回転数に依存する。このため、主軸の回転数が速くなるにつれて潤滑油の供給量も増加し、必要以上の潤滑油が軸受及び渦巻に供給されて油上りが増加し、軸受及び渦巻に供給された潤滑油が密閉容器の外部に吐出される場合がある。したがって、密閉容器の内部に貯留される潤滑油の量が減少し、軸受損傷及び焼付き等の機械損失が発生するという課題があった。 Here, since the scroll fluid compressor described in Patent Document 1 drives the pump by rotating the main shaft, the supply amount of the lubricating oil depends on the rotational speed of the main shaft. For this reason, the supply amount of the lubricating oil increases as the rotational speed of the main shaft increases, so that an excessive amount of lubricating oil is supplied to the bearing and the swirl to increase the oil rise, and the lubricating oil supplied to the bearing and the swirl is sealed. It may be discharged outside the container. Accordingly, there is a problem that the amount of lubricating oil stored in the sealed container is reduced, and mechanical loss such as bearing damage and seizure occurs.
　本発明は、上述のような課題を背景としてなされたものであり、機械損失を低減させ、高速運転可能なスクロール圧縮機を得ることを目的としている。 The present invention has been made against the background of the above-described problems, and an object thereof is to obtain a scroll compressor capable of reducing mechanical loss and operating at high speed.
　本発明に係るスクロール圧縮機は、油溜め部を有する密閉容器と、前記密閉容器の内部に設けられる主軸と、前記主軸が回転することで駆動されるポンプと、前記ポンプの上方に設けられるポンプケーシングと、前記油溜め部に溜められる潤滑油を通す油パイプと、を備え、前記ポンプの内部には、前記油パイプの内部と連通する低圧部と、前記低圧部よりも高圧となる高圧部と、が設けられ、前記ポンプケーシングの下面と前記ポンプの上面との間には、前記低圧部と前記高圧部とを連通するように空隙が設けられているものである。 A scroll compressor according to the present invention includes a sealed container having an oil reservoir, a main shaft provided inside the sealed container, a pump driven by rotation of the main shaft, and a pump provided above the pump. A casing, and an oil pipe through which the lubricating oil stored in the oil reservoir is passed, a low-pressure part communicating with the inside of the oil pipe inside the pump, and a high-pressure part having a higher pressure than the low-pressure part And a gap is provided between the lower surface of the pump casing and the upper surface of the pump so as to communicate the low pressure portion and the high pressure portion.
　本発明によれば、ポンプケーシングの下面とポンプの上面との間には、低圧部と高圧部とを連通するように空隙が設けられている。このため、スクロール圧縮機の運転時において、ポンプ内で圧縮されて圧力が上昇した潤滑油の一部は、高圧部から空隙を介して再び低圧部に供給される。したがって、密閉容器の内部に貯留される潤滑油が減少することを抑制でき、軸受損傷及び焼付き等の機械損失を低減させることができ、高速運転可能なスクロール圧縮機を得ることができる。 According to the present invention, a gap is provided between the lower surface of the pump casing and the upper surface of the pump so as to communicate the low pressure portion and the high pressure portion. For this reason, during the operation of the scroll compressor, a part of the lubricating oil that has been compressed in the pump and increased in pressure is supplied again from the high-pressure part to the low-pressure part via the gap. Accordingly, it is possible to suppress a decrease in the lubricating oil stored in the closed container, to reduce mechanical loss such as bearing damage and seizure, and to obtain a scroll compressor capable of high speed operation.
本発明の実施の形態１に係るスクロール圧縮機１００の断面図である。It is sectional drawing of the scroll compressor 100 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係るスクロール圧縮機１００の要部を示す断面図である。It is sectional drawing which shows the principal part of the scroll compressor 100 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係るスクロール圧縮機１００の主軸４の回転数とポンプ１０から供給される潤滑油の供給量との関係を示した特性図である。It is a characteristic view showing the relationship between the rotation speed of the main shaft 4 of the scroll compressor 100 according to Embodiment 1 of the present invention and the supply amount of lubricating oil supplied from the pump 10. 本発明の実施の形態２に係るスクロール圧縮機１００の要部を示す断面図である。It is sectional drawing which shows the principal part of the scroll compressor 100 which concerns on Embodiment 2 of this invention. 本発明の実施の形態２に係るスクロール圧縮機１００の要部を示す断面図である。It is sectional drawing which shows the principal part of the scroll compressor 100 which concerns on Embodiment 2 of this invention. 本発明の実施の形態２に係るスクロール圧縮機１００の弾性体２１の例を示す図である。It is a figure which shows the example of the elastic body 21 of the scroll compressor 100 which concerns on Embodiment 2 of this invention. 本発明の実施の形態２に係るスクロール圧縮機１００の主軸４の回転数とポンプ１０から供給される潤滑油の供給量との関係を示した特性図である。It is a characteristic view showing the relationship between the rotation speed of the main shaft 4 of the scroll compressor 100 according to Embodiment 2 of the present invention and the supply amount of lubricating oil supplied from the pump 10. 本発明の実施の形態２に係るスクロール圧縮機１００の要部を示す断面図であり、図５の変形例である。It is sectional drawing which shows the principal part of the scroll compressor 100 which concerns on Embodiment 2 of this invention, and is a modification of FIG.
　以下、本発明のスクロール圧縮機１００について、図面を用いて詳細に説明する。なお、以下の図面では各構成部材の大きさの関係が実際のものとは異なる場合がある。また、以下の図面において、同一の符号を付したものは、同一又はこれに相当するものであり、このことは明細書の全文において共通することとする。さらに、明細書全文に表わされている構成要素の形態は、あくまでも例示であって、これらの記載に限定されるものではない。 Hereinafter, the scroll compressor 100 of the present invention will be described in detail with reference to the drawings. In the following drawings, the size relationship of each component may be different from the actual one. In the following drawings, the same reference numerals denote the same or corresponding parts, and this is common throughout the entire specification. Furthermore, the forms of the constituent elements shown in the entire specification are merely examples, and are not limited to these descriptions.
実施の形態１．
　図１は本発明の実施の形態１に係るスクロール圧縮機１００の断面図である。図１に示されるように、スクロール圧縮機１００は、揺動スクロール１と、固定スクロール２と、フレーム３と、主軸４と、ステータ５と、ロータ６と、サブフレーム８と、玉軸受９と、ポンプ１０と、油パイプ１７と、を備える。スクロール圧縮機１００の外郭は、密閉容器１００Ａで構成される。 Embodiment 1 FIG.
FIG. 1 is a cross-sectional view of a scroll compressor 100 according to Embodiment 1 of the present invention. As shown in FIG. 1, the scroll compressor 100 includes an orbiting scroll 1, a fixed scroll 2, a frame 3, a main shaft 4, a stator 5, a rotor 6, a subframe 8, and ball bearings 9. The pump 10 and the oil pipe 17 are provided. The outer shell of the scroll compressor 100 is composed of a sealed container 100A.
　揺動スクロール１は、台板１ａ及び渦巻歯１ｂを有する部材である。固定スクロール２は、台板２ａ及び渦巻歯２ｂを有する部材である。揺動スクロール１及び固定スクロール２は、組み合わされて圧縮室３０を形成する。揺動スクロール１及び固定スクロール２は、フレーム３に収納されている。 The orbiting scroll 1 is a member having a base plate 1a and spiral teeth 1b. The fixed scroll 2 is a member having a base plate 2a and spiral teeth 2b. The swing scroll 1 and the fixed scroll 2 are combined to form a compression chamber 30. The swing scroll 1 and the fixed scroll 2 are accommodated in a frame 3.
　フレーム３は、密閉容器１００Ａの内部の上部において密閉容器１００Ａに固定されている部材であり、主軸受３ａを有する。主軸受３ａは、主軸４の上部を回転可能に支持するものである。主軸４は、密閉容器１００Ａの上下方向に延びる部材であり、ポンプ１０に回転力を伝達するポンプ軸４ｂを有する。主軸４には、潤滑油を通す油穴４ｃが設けられている。主軸４の外面よりも外側には、ステータ５及びロータ６が設けられている。 The frame 3 is a member fixed to the sealed container 100A in the upper part of the sealed container 100A, and has a main bearing 3a. The main bearing 3a supports the upper part of the main shaft 4 rotatably. The main shaft 4 is a member extending in the vertical direction of the sealed container 100 </ b> A, and has a pump shaft 4 b that transmits a rotational force to the pump 10. The main shaft 4 is provided with an oil hole 4c through which lubricating oil is passed. A stator 5 and a rotor 6 are provided outside the outer surface of the main shaft 4.
　ステータ５は、例えば、略筒状に構成される部材であり、密閉容器１００Ａに固定されている。ロータ６は、例えば、略筒状に構成される部材であり、主軸４が挿通される。ステータ５及びロータ６は、スクロール圧縮機１００の電動機部を構成する。ステータ５及びロータ６よりも下方にはサブフレーム８が設けられている。 The stator 5 is a member configured in a substantially cylindrical shape, for example, and is fixed to the sealed container 100A. The rotor 6 is a member configured in a substantially cylindrical shape, for example, and the main shaft 4 is inserted therethrough. The stator 5 and the rotor 6 constitute an electric motor part of the scroll compressor 100. A subframe 8 is provided below the stator 5 and the rotor 6.
　サブフレーム８は、密閉容器１００Ａの内部の下部において密閉容器１００Ａに固定されている部材であり、玉軸受９を有する。玉軸受９は、主軸４の下部を回転可能に支持するものである。玉軸受９の下端面にはポンプ１０が固定されている。 The subframe 8 is a member fixed to the sealed container 100A at the lower part inside the sealed container 100A, and has a ball bearing 9. The ball bearing 9 supports the lower part of the main shaft 4 rotatably. A pump 10 is fixed to the lower end surface of the ball bearing 9.
　ポンプ１０は、油溜め部１６に溜められた潤滑油を吸引して各摺動部に潤滑油を供給する部材であり、例えば、容積型のポンプで構成される。ポンプ１０については図２を用いて詳しく説明する。油溜め部１６は、潤滑油が溜められる部分であり、密閉容器１００Ａの底部に設けられている。油溜め部１６には、油パイプ１７が浸漬されている。油パイプ１７は、例えば、上下面が貫通する筒状の部材で構成されている。 The pump 10 is a member that sucks the lubricating oil stored in the oil reservoir 16 and supplies the lubricating oil to each sliding portion, and is constituted by a positive displacement pump, for example. The pump 10 will be described in detail with reference to FIG. The oil sump 16 is a part where lubricating oil is stored, and is provided at the bottom of the sealed container 100A. An oil pipe 17 is immersed in the oil reservoir 16. The oil pipe 17 is configured by, for example, a cylindrical member that passes through the upper and lower surfaces.
　図２は本発明の実施の形態１に係るスクロール圧縮機１００の要部を示す断面図である。図２に示されるように、ポンプ１０には、低圧部２０ａ及び高圧部２０ｂが設けられている。また、図２に示されるように、ポンプ１０の下方にはポンプカバー１２が設けられ、ポンプ１０の上方にはポンプケーシング１１が設けられている。 FIG. 2 is a cross-sectional view showing a main part of the scroll compressor 100 according to Embodiment 1 of the present invention. As shown in FIG. 2, the pump 10 is provided with a low pressure part 20a and a high pressure part 20b. As shown in FIG. 2, a pump cover 12 is provided below the pump 10, and a pump casing 11 is provided above the pump 10.
　低圧部２０ａは、ポンプ１０を流れる潤滑油のうち圧縮される前の潤滑油が流れる空間であり、ポンプ１０の上下面の一部を貫通するように設けられる。低圧部２０ａは吸入ポート１３ａと連通している。吸入ポート１３ａは、油パイプ１７から排出された潤滑油を低圧部２０ａに通すための空間である。 The low-pressure part 20a is a space through which the lubricant before compression among the lubricant flowing through the pump 10 flows, and is provided so as to penetrate part of the upper and lower surfaces of the pump 10. The low pressure part 20a communicates with the suction port 13a. The suction port 13a is a space for allowing the lubricating oil discharged from the oil pipe 17 to pass through the low pressure portion 20a.
　高圧部２０ｂは、ポンプ１０を流れる潤滑油のうち圧縮された後の潤滑油が流れる空間であり、ポンプ１０の上下面の一部を貫通するように設けられる。高圧部２０ｂは吐出ポート１３ｂと連通している。吐出ポート１３ｂは、高圧部２０ｂから排出された潤滑油を油穴４ｃに通すための空間である。 The high-pressure portion 20b is a space through which the compressed lubricating oil out of the lubricating oil flowing through the pump 10 flows, and is provided so as to penetrate part of the upper and lower surfaces of the pump 10. The high pressure portion 20b communicates with the discharge port 13b. The discharge port 13b is a space for allowing the lubricating oil discharged from the high pressure portion 20b to pass through the oil hole 4c.
　ポンプカバー１２は、ポンプ１０を覆う部材であり、収納部１２ａを有する。ポンプカバー１２は、サブフレーム８の下端面においてボルト締め固定されている。ポンプカバー１２の上端面と玉軸受９の下端面とは当接している。ポンプカバー１２の下部には油パイプ１７が位置している。油パイプ１７がポンプカバー１２の下部に設けられることで、ポンプカバー１２の内部と油パイプ１７の内部とが連通する。 The pump cover 12 is a member that covers the pump 10 and has a storage portion 12a. The pump cover 12 is bolted and fixed to the lower end surface of the subframe 8. The upper end surface of the pump cover 12 and the lower end surface of the ball bearing 9 are in contact with each other. An oil pipe 17 is located below the pump cover 12. By providing the oil pipe 17 at the lower part of the pump cover 12, the inside of the pump cover 12 and the inside of the oil pipe 17 communicate with each other.
　ポンプケーシング１１は、収納部１２ａに収納されている部材であり、ポンプカバー１２をカシメることで固定されている。ポンプケーシング１１は、ポンプ１０の上面と対向するように設けられている。ポンプケーシング１１とポンプ１０との間には空隙δが設けられている。具体的には、ポンプケーシング１１の下面とポンプ１０の上面との間には空隙δが設けられている。空隙δは、ポンプケーシング１１の外形よりも内側（中心側）において、低圧部２０ａと高圧部２０ｂとが連通するように設けられる。空隙δは、主軸４の軸方向におけるポンプ１０の高さをＬとした場合に、例えば、δ＝０．０４Ｌ以上０．０６Ｌ以下である。 The pump casing 11 is a member housed in the housing portion 12a and is fixed by caulking the pump cover 12. The pump casing 11 is provided so as to face the upper surface of the pump 10. A gap δ is provided between the pump casing 11 and the pump 10. Specifically, a gap δ is provided between the lower surface of the pump casing 11 and the upper surface of the pump 10. The gap δ is provided on the inner side (center side) of the outer shape of the pump casing 11 so that the low pressure portion 20a and the high pressure portion 20b communicate with each other. The gap δ is, for example, δ = 0.04 L or more and 0.06 L or less, where L is the height of the pump 10 in the axial direction of the main shaft 4.
　以下に、本実施の形態１のスクロール圧縮機１００の作用及び潤滑油の流れについて図２を用いて説明する。なお、図２の矢印は潤滑油が流れる方向を示している。 Hereinafter, the operation of the scroll compressor 100 according to the first embodiment and the flow of the lubricating oil will be described with reference to FIG. In addition, the arrow of FIG. 2 has shown the direction through which lubricating oil flows.
　ステータ５に給電されると、ロータ６は、トルクを発生して主軸４とともに回転し、揺動スクロール１を公転運動させる。これにより、圧縮室３０の容積は順次減少していき、低温低圧のガス冷媒は高温高圧なガス冷媒となって吐出される。また、主軸４が回転することでポンプ軸４ｂが回転し、ポンプ軸４ｂが回転することでポンプ１０が駆動される。これにより、油溜め部１６に溜められている潤滑油が、油パイプ１７、吸入ポート１３ａを順に通ってポンプ１０に導かれる。ポンプ１０に導かれた潤滑油は、低圧部２０ａ、高圧部２０ｂを順に通って、ポンプ１０から排出される。 When power is supplied to the stator 5, the rotor 6 generates torque and rotates together with the main shaft 4 to cause the orbiting scroll 1 to revolve. As a result, the volume of the compression chamber 30 gradually decreases, and the low-temperature and low-pressure gas refrigerant is discharged as a high-temperature and high-pressure gas refrigerant. Moreover, the pump shaft 4b rotates when the main shaft 4 rotates, and the pump 10 is driven when the pump shaft 4b rotates. Thereby, the lubricating oil stored in the oil reservoir 16 is guided to the pump 10 through the oil pipe 17 and the suction port 13a in this order. The lubricating oil guided to the pump 10 is discharged from the pump 10 through the low pressure part 20a and the high pressure part 20b in this order.
　このとき、低圧部２０ａと高圧部２０ｂとを連通するように空隙δが設けられているため、ポンプ１０から排出された潤滑油の一部は、高圧部２０ｂから空隙δを介して低圧部２０ａに移動する。潤滑油の一部が、高圧部２０ｂから空隙δを通って低圧部２０ａに移動すると、潤滑油がポンプ１０から吐出される際の潤滑油の圧力が低下し、油穴４ｃから排出される潤滑油の供給量が減少する。ポンプ１０から排出された潤滑油の残りは、吐出ポート１３ｂに吐出されて油穴４ｃに汲み上げられる。油穴４ｃに汲み上げられた潤滑油は、各摺動部に供給される。 At this time, since the gap δ is provided so that the low pressure part 20a and the high pressure part 20b communicate with each other, a part of the lubricating oil discharged from the pump 10 passes through the gap δ from the high pressure part 20b. Move to. When a part of the lubricating oil moves from the high pressure portion 20b through the gap δ to the low pressure portion 20a, the pressure of the lubricating oil when the lubricating oil is discharged from the pump 10 decreases, and the lubricating oil discharged from the oil hole 4c. Oil supply decreases. The remainder of the lubricating oil discharged from the pump 10 is discharged to the discharge port 13b and pumped up to the oil hole 4c. The lubricating oil pumped up in the oil hole 4c is supplied to each sliding part.
　高圧部２０ｂから空隙δを介して低圧部２０ａに供給された潤滑油は、油パイプ１７を通って汲み上げられた潤滑油と混合し、ポンプ１０によって再度圧縮される。再度圧縮された潤滑油の一部は、高圧部２０ｂから空隙δを介して低圧部２０ａへ供給される。再度圧縮された潤滑油の残りは、高圧部２０ｂから排出され、吐出ポート１３ｂ、油穴４ｃを順に通って各摺動部へ供給される。なお、高圧部２０ｂから低圧部２０ａへ供給された潤滑油の流路は、吸入ポート１３ａから低圧部２０ａへ供給された潤滑油の流路と同様である。このようにして、ポンプ１０内を流れる潤滑油の圧力はポンプ１０から排出される際に低下する。 The lubricating oil supplied from the high pressure part 20b to the low pressure part 20a via the gap δ is mixed with the lubricating oil pumped up through the oil pipe 17 and compressed again by the pump 10. Part of the lubricating oil that has been compressed again is supplied from the high-pressure portion 20b to the low-pressure portion 20a through the gap δ. The remainder of the compressed lubricating oil is discharged from the high-pressure part 20b and supplied to each sliding part through the discharge port 13b and the oil hole 4c in this order. The flow path of the lubricating oil supplied from the high pressure section 20b to the low pressure section 20a is the same as the flow path of the lubricating oil supplied from the suction port 13a to the low pressure section 20a. In this way, the pressure of the lubricating oil flowing through the pump 10 decreases when the oil is discharged from the pump 10.
　図３は本発明の実施の形態１に係るスクロール圧縮機１００の主軸４の回転数とポンプ１０から供給される潤滑油の供給量との関係を示した特性図である。図３の横軸には主軸４の回転数［ｒｐｓ］を示し、図３の縦軸には潤滑油供給量［ｃｃ／ｓ］を示している。以下に、図３を用いて、主軸４の回転数とポンプ１０から供給される潤滑油の供給量との関係について説明する。 FIG. 3 is a characteristic diagram showing the relationship between the rotational speed of the main shaft 4 of the scroll compressor 100 according to Embodiment 1 of the present invention and the amount of lubricant supplied from the pump 10. The horizontal axis of FIG. 3 indicates the rotational speed [rps] of the main shaft 4, and the vertical axis of FIG. 3 indicates the lubricating oil supply amount [cc / s]. Below, the relationship between the rotation speed of the main shaft 4 and the supply amount of the lubricating oil supplied from the pump 10 will be described with reference to FIG.
　なお、図３においては、潤滑油は、粘度３２ｃｓｔ、密度０．９ｇ／ｃｍ３以上１．０ｇ／ｃｍ３以下、油温－２０℃以上８０℃以下のものを使用し、ポンプ１０は吐出量０．３２ｃｍ３／ｒｅｖのものを使用したスクロール圧縮機１００を想定している。 In FIG. 3, a lubricating oil having a viscosity of 32 cst, a density of 0.9 g / cm 3 to 1.0 g / cm 3 and an oil temperature of −20 ° C. to 80 ° C. is used. A scroll compressor 100 using a 0.32 cm 3 / rev one is assumed.
　図３における（ａ）は、従来のスクロール圧縮機における主軸の回転数と潤滑油供給量との関係を示している。
　また、図３における（ｂ）は、本発明のスクロール圧縮機１００においてδ＝０．０４Ｌである場合における主軸４の回転数と潤滑油供給量との関係を示している。
　また、図３における（ｃ）は、本発明のスクロール圧縮機１００においてδ＝０．０６Ｌである場合における主軸４の回転数と潤滑油供給量との関係を示している。
　また、図３における（Ａ）は、スクロール圧縮機の運転に際して要求される潤滑油供給量を示している。 (A) in FIG. 3 shows the relationship between the rotational speed of the main shaft and the lubricant supply amount in the conventional scroll compressor.
FIG. 3B shows the relationship between the rotational speed of the main shaft 4 and the amount of lubricating oil supplied when δ = 0.04 L in the scroll compressor 100 of the present invention.
FIG. 3C shows the relationship between the rotational speed of the main shaft 4 and the amount of lubricating oil supplied when δ = 0.06 L in the scroll compressor 100 of the present invention.
Further, (A) in FIG. 3 shows the amount of lubricating oil supplied required when the scroll compressor is operated.
　図３に示されるように、主軸４の回転数が低い場合において、空隙δを設けたときの潤滑油の供給量は、空隙δを設けないときの潤滑油の供給量よりも小さいものの、空隙δを設けたときの潤滑油の供給量と、空隙δを設けないときの潤滑油の供給量と、の差は大きくない。一方で、主軸４の回転数が高くなるにつれて、空隙δを設けたときの潤滑油の供給量と、空隙δを設けないときの潤滑油の供給量と、の差は次第に大きくなる。 As shown in FIG. 3, when the rotational speed of the main shaft 4 is low, the supply amount of the lubricating oil when the gap δ is provided is smaller than the supply amount of the lubricating oil when the gap δ is not provided. The difference between the amount of lubricant supplied when δ is provided and the amount of lubricant supplied when no gap δ is not provided is not large. On the other hand, as the rotational speed of the main shaft 4 increases, the difference between the supply amount of the lubricating oil when the gap δ is provided and the supply amount of the lubricant oil when the gap δ is not provided gradually increases.
　ここで、空隙δの面積が一定であるため、高圧部２０ｂから空隙δを通って低圧部２０ａに供給される潤滑油の流量は、空隙δを流れる際の潤滑油の流速に比例する。また、空隙δを流れる際の潤滑油の流速は潤滑油の圧力に依存するため、高圧部２０ｂから空隙δを通って低圧部２０ａに供給される潤滑油の流量はポンプ１０によって発生する圧力に依存する。したがって、主軸４の回転数が増加し、ポンプ１０によって発生する圧力が増加するほど、高圧部２０ｂから空隙δを通って低圧部２０ａに供給される潤滑油の流量は増加する。このようにして、上述したように、主軸４の回転数が高くなるにつれて、空隙δを設けたときの潤滑油の供給量と、空隙δを設けないときの潤滑油の供給量と、の差は次第に大きくなる。 Here, since the area of the gap δ is constant, the flow rate of the lubricating oil supplied from the high pressure portion 20b through the gap δ to the low pressure portion 20a is proportional to the flow velocity of the lubricating oil when flowing through the gap δ. Further, since the flow rate of the lubricating oil when flowing through the gap δ depends on the pressure of the lubricating oil, the flow rate of the lubricating oil supplied from the high pressure portion 20b to the low pressure portion 20a through the gap δ is equal to the pressure generated by the pump 10. Dependent. Therefore, as the rotational speed of the main shaft 4 increases and the pressure generated by the pump 10 increases, the flow rate of the lubricating oil supplied from the high pressure portion 20b through the gap δ to the low pressure portion 20a increases. Thus, as described above, as the rotational speed of the main shaft 4 increases, the difference between the supply amount of the lubricating oil when the gap δ is provided and the supply amount of the lubricant oil when the gap δ is not provided. Gradually grows.
　以上のように、本実施の形態１に係るスクロール圧縮機１００は、ポンプ１０の内部には、油パイプ１７の内部と連通する低圧部２０ａと、低圧部２０ａよりも高圧となる高圧部２０ｂと、が設けられ、ポンプケーシング１１の下面とポンプ１０の上面との間に、低圧部２０ａと高圧部２０ｂとを連通するように空隙δを設けている。このため、スクロール圧縮機１００の運転時において、ポンプ１０内で圧縮されて圧力が上昇した潤滑油の一部は、高圧部２０ｂから空隙δを介して再び低圧部２０ａに供給される。したがって、低速運転時に必要な潤滑油の供給量を確保しつつ、高速運転時において過剰な潤滑油の供給量を抑制することができる。このようにして、機械損失を低減させることができ、高速運転可能なスクロール圧縮機１００を得ることができる。そして、スクロール圧縮機１００の運転条件次第では、２４０ｒｐｓの高速運転であっても運転を行うことができる。 As described above, the scroll compressor 100 according to the first embodiment includes, in the pump 10, the low pressure part 20a that communicates with the inside of the oil pipe 17, and the high pressure part 20b that has a higher pressure than the low pressure part 20a. , And a gap δ is provided between the lower surface of the pump casing 11 and the upper surface of the pump 10 so as to communicate the low pressure portion 20a and the high pressure portion 20b. For this reason, during the operation of the scroll compressor 100, a part of the lubricating oil which has been compressed in the pump 10 and whose pressure has increased is supplied again from the high pressure part 20b to the low pressure part 20a via the gap δ. Therefore, it is possible to suppress an excessive supply amount of the lubricating oil during the high speed operation while securing a supply amount of the lubricating oil necessary during the low speed operation. In this way, the mechanical loss can be reduced, and the scroll compressor 100 capable of high speed operation can be obtained. Depending on the operating conditions of the scroll compressor 100, the operation can be performed even at a high speed operation of 240 rps.
　なお、本実施の形態１においては、空隙δは、収納部１２ａに設けられる溝を下端面側に下げることで設けられるように構成しているが、これに限定されない。空隙δは、ポンプケーシング１１の下面とポンプ１０の上面との間に設けられ、ポンプケーシング１１の外形よりも内側（中心側）において、低圧部２０ａと高圧部２０ｂとを連通させるように構成されていればよい。 In the first embodiment, the gap δ is configured to be provided by lowering the groove provided in the storage portion 12a toward the lower end surface, but is not limited thereto. The gap δ is provided between the lower surface of the pump casing 11 and the upper surface of the pump 10, and is configured to communicate the low pressure portion 20a and the high pressure portion 20b on the inner side (center side) of the outer shape of the pump casing 11. It only has to be.
実施の形態２．
　本実施の形態２においては、実施の形態１とは異なり、空隙δを設けないで弾性体２１を設けるようにしたものである。なお、本実施の形態２において、特に記述しない項目については実施の形態１と同様とし、同一の機能や構成については同一の符号を用いて述べることとする。 Embodiment 2. FIG.
In the second embodiment, unlike the first embodiment, the elastic body 21 is provided without providing the gap δ. In the second embodiment, items that are not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.
　図４は本発明の実施の形態２に係るスクロール圧縮機１００の要部を示す断面図である。図５は本発明の実施の形態２に係るスクロール圧縮機１００の要部を示す断面図である。図６は本発明の実施の形態２に係るスクロール圧縮機１００の弾性体２１の例を示す図である。なお、図４における主軸４の回転数は、図５における主軸４の回転数よりも小さい。 FIG. 4 is a cross-sectional view showing a main part of the scroll compressor 100 according to Embodiment 2 of the present invention. FIG. 5 is a cross-sectional view showing a main part of scroll compressor 100 according to Embodiment 2 of the present invention. FIG. 6 is a diagram illustrating an example of the elastic body 21 of the scroll compressor 100 according to Embodiment 2 of the present invention. The rotational speed of the main shaft 4 in FIG. 4 is smaller than the rotational speed of the main shaft 4 in FIG.
　図４，図５に示されるように、密閉容器１００Ａの内部には弾性体２１が設けられている。弾性体２１は、例えば図６のような形状を有するコイルバネで構成され、ポンプケーシング１１とポンプカバー１２との間に設けられてカシメられている。弾性体２１の一端はポンプケーシング１１の上面に位置し、弾性体２１の他端はポンプカバー１２の下面に位置している。弾性体２１の一端がポンプケーシング１１の上面に位置し、弾性体２１の他端がポンプカバー１２の下面に位置した状態において、弾性体２１は基準長を有している。弾性体２１が有する基準長は、例えば自然長である。弾性体２１が基準長を有している状態において、ポンプケーシング１１の下面とポンプ１０の上面とは当接しており、低圧部２０ａと高圧部２０ｂとは連通しないようになっている。ポンプ１０内の圧力が変化してポンプケーシング１１が主軸４の軸方向に移動すると、弾性体２１は主軸４の軸方向に伸縮する。 4 and 5, an elastic body 21 is provided inside the sealed container 100A. The elastic body 21 is constituted by a coil spring having a shape as shown in FIG. 6, for example, and is provided between the pump casing 11 and the pump cover 12 and crimped. One end of the elastic body 21 is located on the upper surface of the pump casing 11, and the other end of the elastic body 21 is located on the lower surface of the pump cover 12. In a state where one end of the elastic body 21 is located on the upper surface of the pump casing 11 and the other end of the elastic body 21 is located on the lower surface of the pump cover 12, the elastic body 21 has a reference length. The reference length of the elastic body 21 is, for example, a natural length. In a state where the elastic body 21 has the reference length, the lower surface of the pump casing 11 and the upper surface of the pump 10 are in contact with each other, and the low pressure part 20a and the high pressure part 20b are not communicated with each other. When the pressure in the pump 10 changes and the pump casing 11 moves in the axial direction of the main shaft 4, the elastic body 21 expands and contracts in the axial direction of the main shaft 4.
　スクロール圧縮機１００の低速運転時において、ポンプケーシング１１とポンプ１０とは当接しており、具体的には、ポンプケーシング１１の下面とポンプ１０の上面とが当接している。ここで、実施の形態１のように空隙δを設けた場合には、従来よりも、高速運転時における潤滑油供給量だけでなく低速運転時における潤滑油供給量も減少するため、低速運転時において、潤滑油が各摺動部に十分に供給されない場合が起こり得る。そこで、本実施の形態２においては、従来よりも、高速運転時における潤滑油供給量を減少させる一方で低速運転時における潤滑油の供給量を減少させないようにして、低速運転時において、潤滑油が各摺動部に十分に供給されるようにしている。 During the low-speed operation of the scroll compressor 100, the pump casing 11 and the pump 10 are in contact, and specifically, the lower surface of the pump casing 11 and the upper surface of the pump 10 are in contact. Here, when the gap δ is provided as in Embodiment 1, not only the amount of lubricating oil supplied during high-speed operation but also the amount of lubricating oil supplied during low-speed operation is reduced compared to the conventional case. In this case, the lubricating oil may not be sufficiently supplied to each sliding portion. Therefore, in the second embodiment, the lubricating oil supply amount at the time of high-speed operation is reduced as compared with the conventional case, while the supply amount of the lubricating oil at the low-speed operation is not reduced, so that the lubricating oil at the low-speed operation is reduced. Is sufficiently supplied to each sliding portion.
　以下に、本実施の形態２のスクロール圧縮機１００の作用及び潤滑油の流れについて説明する。なお、図４，図５の矢印は潤滑油が流れる方向を示している。また、以後の説明においては、実施の形態１において既に説明した動作と同一の動作については適宜省略する。 Hereinafter, the operation of the scroll compressor 100 of the second embodiment and the flow of the lubricating oil will be described. In addition, the arrow of FIG. 4, FIG. 5 has shown the direction through which lubricating oil flows. In the following description, the same operations as those already described in the first embodiment are omitted as appropriate.
　図４に示されるように、低速運転時においては、ポンプケーシング１１は弾性体２１により押さえつけられており、この状態でポンプ１０内の圧力が上昇すると、ポンプケーシング１１が押し上げられて図５に示されるような状態となる。図５に示されるように、高速運転時においては、ポンプケーシング１１が押し上げられることで、弾性体２１は基準長よりも収縮するように変位し、これにより、ポンプカバー１２とポンプ１０との間には空隙εが形成される。潤滑油の一部は、高圧部２０ｂから空隙εを介して低圧部２０ａに移動する。潤滑油の一部が、高圧部２０ｂから空隙εを介して低圧部２０ａに移動すると、潤滑油がポンプ１０から吐出される際の潤滑油の圧力が低下し、油穴４ｃからの潤滑油の供給量が減少する。 As shown in FIG. 4, the pump casing 11 is pressed by the elastic body 21 during low-speed operation. When the pressure in the pump 10 rises in this state, the pump casing 11 is pushed up and shown in FIG. It will be in a state to be. As shown in FIG. 5, when the pump casing 11 is pushed up during high-speed operation, the elastic body 21 is displaced so as to contract more than the reference length, so that the pump cover 12 and the pump 10 are not displaced. Is formed with a gap ε. A part of the lubricating oil moves from the high pressure part 20b to the low pressure part 20a via the gap ε. When a part of the lubricating oil moves from the high pressure portion 20b to the low pressure portion 20a through the gap ε, the pressure of the lubricating oil when the lubricating oil is discharged from the pump 10 decreases, and the lubricating oil from the oil hole 4c is reduced. Supply volume decreases.
　高圧部２０ｂから空隙εを介して低圧部２０ａに供給された潤滑油は、油パイプ１７を通って汲み上げられた潤滑油と混合し、ポンプ１０によって再度圧縮される。再度圧縮された潤滑油の一部は、高圧部２０ｂから空隙εを介して低圧部２０ａへ供給される。再度圧縮された潤滑油の残りは、高圧部２０ｂから排出され、吐出ポート１３ｂ、油穴４ｃを順に通って各摺動部へ供給される。なお、高圧部２０ｂから空隙εを介して低圧部２０ａへ供給された潤滑油の流路は、吸入ポート１３ａから低圧部２０ａへ供給された潤滑油の流路と同様である。このようにして、ポンプ１０内を流れる潤滑油の圧力はポンプ１０から排出される際に低下する。 The lubricating oil supplied from the high pressure part 20 b to the low pressure part 20 a via the gap ε is mixed with the lubricating oil pumped up through the oil pipe 17 and compressed again by the pump 10. A part of the lubricating oil compressed again is supplied from the high pressure part 20b to the low pressure part 20a through the gap ε. The remainder of the compressed lubricating oil is discharged from the high-pressure part 20b and supplied to each sliding part through the discharge port 13b and the oil hole 4c in this order. The flow path of the lubricating oil supplied from the high pressure section 20b to the low pressure section 20a via the gap ε is the same as the flow path of the lubricating oil supplied from the suction port 13a to the low pressure section 20a. In this way, the pressure of the lubricating oil flowing through the pump 10 decreases when the oil is discharged from the pump 10.
　以下に、本実施の形態２に係るスクロール圧縮機１００の弾性体２１について説明する。弾性体２１は、ポンプ１０内の圧力によって圧縮力を受ける。この圧縮力をＦ１とすると、Ｆ１は以下の（式１）を用いて算出することができる。
　Ｆ１＝Ｐ×Ａ・・・（式１）
　　Ｐ：ポンプ１０内の圧力
　　Ａ：ポンプケーシング１１とポンプ１０とが当接している部分の面積 The elastic body 21 of the scroll compressor 100 according to the second embodiment will be described below. The elastic body 21 receives a compressive force due to the pressure in the pump 10. When this compression force is F1, F1 can be calculated using the following (Equation 1).
F1 = P × A (Formula 1)
P: Pressure in the pump 10 A: Area of the portion where the pump casing 11 and the pump 10 are in contact with each other
　これに対し、弾性体２１には、ポンプケーシング１１をポンプ１０側に押さえつける力が作用し、この弾性体の反力をＦ２とすると、Ｆ２は以下の（式２）を用いて算出することができる。
　Ｆ２＝ｋ×Δｘ・・・（式２）
　　ｋ：弾性体２１のばね定数
　Δｘ：弾性体２１の変位 On the other hand, a force that presses the pump casing 11 against the pump 10 acts on the elastic body 21, and when the reaction force of this elastic body is F2, F2 can be calculated using the following (Equation 2). it can.
F2 = k × Δx (Expression 2)
k: spring constant of the elastic body 21 Δx: displacement of the elastic body 21
　ここで、Ｆ１＜Ｆ２の場合には、ポンプケーシング１１は、弾性体２１の反力によってポンプ１０の上端面に押さえつけられた状態となる。そして、Ｆ１＜Ｆ２の場合において、ポンプ１０内の圧力が上昇してＦ１＞Ｆ２となったとき、ポンプケーシング１１はポンプ１０内の圧力によって主軸４の軸方向上方に押し上げられる。これにより、ポンプケーシング１１とポンプ１０との間には空隙εが形成される。このように空隙εが形成されることでポンプ１０内の圧力が低下する。 Here, in the case of F1 <F2, the pump casing 11 is pressed against the upper end surface of the pump 10 by the reaction force of the elastic body 21. In the case of F1 <F2, when the pressure in the pump 10 rises to F1> F2, the pump casing 11 is pushed upward in the axial direction of the main shaft 4 by the pressure in the pump 10. As a result, a gap ε is formed between the pump casing 11 and the pump 10. Thus, the pressure in the pump 10 is reduced by forming the gap ε.
　なお、Ｆ１＝Ｆ２の場合には、上述のばね定数ｋは、以下の（式３）を用いて算出することができる。
　ｋ＝Ｐ×Ａ／Δｘ・・・（式３） When F1 = F2, the above-described spring constant k can be calculated using the following (Equation 3).
k = P × A / Δx (Formula 3)
　このため、主軸４の各回転数におけるポンプ１０内の圧力Ｐが分かれば、所定の圧力で弾性体２１を変形させることで、ポンプ１０内の圧力Ｐを下げることができる。ここで、ポンプ１０内の圧力Ｐはポンプ１０の流量Ｑに関係し、以下の（式４）を用いて算出することができる。
　Ｐ＝ρ×（Ｑ／Ｃ×Ａ）２／２・・・（式４）
　Ｃ：流出係数
　ρ：潤滑油の密度 For this reason, if the pressure P in the pump 10 at each rotational speed of the main shaft 4 is known, the pressure P in the pump 10 can be lowered by deforming the elastic body 21 with a predetermined pressure. Here, the pressure P in the pump 10 is related to the flow rate Q of the pump 10 and can be calculated using the following (Equation 4).
P = ρ × (Q / C × A) 2/2 ··· ( Equation 4)
C: Outflow coefficient ρ: Lubricating oil density
　ここで、ポンプ軸４ｂは主軸４と一体成形されているため、ポンプ１０の流量Ｑは、以下の（式５）を用いて算出することができる。
　Ｑ＝ｑ×ｎ・・・（式５）
　ｑ：ポンプ１０の吐出量
　ｎ：スクロール圧縮機１００（主軸４）の回転数 Here, since the pump shaft 4b is integrally formed with the main shaft 4, the flow rate Q of the pump 10 can be calculated using the following (Formula 5).
Q = q × n (Formula 5)
q: Discharge amount of the pump 10 n: Number of rotations of the scroll compressor 100 (main shaft 4)
　上述の（式１）～（式５）を用いて主軸４の各回転数における圧力Ｐを算出し、算出した圧力Ｐに基づいてばね定数ｋを算出し、弾性体２１の材料及び形状を決定する。 The pressure P at each rotational speed of the main shaft 4 is calculated using the above-described (Formula 1) to (Formula 5), the spring constant k is calculated based on the calculated pressure P, and the material and shape of the elastic body 21 are determined. To do.
　ここで、弾性体２１は、例えば、図６に示すようなコイルばねであり、スクロール圧縮機１００の運転停止時の弾性体２１の変位を０．２０ｍｍのものである。また、弾性体２１は、例えば、ポンプ１０の圧力により変形する構造であり、Ｆ１＝Ｆ２の状態からＦ１＞Ｆ２の状態となるときの主軸４の回転数が１００ｒｐｓ以上１５０ｒｐｓ以下となるように設計されている。 Here, the elastic body 21 is, for example, a coil spring as shown in FIG. 6 and has a displacement of 0.20 mm when the operation of the scroll compressor 100 is stopped. Further, the elastic body 21 has a structure that is deformed by the pressure of the pump 10, for example, and is designed so that the rotational speed of the main shaft 4 is 100 rps or more and 150 rps or less when F1 = F2 is changed to F1> F2. Has been.
　このとき、ポンプ１０の流量Ｑは、上述の（式５）を用いて以下のように算出できる。
　Ｑ＝ｑ×ｎ＝３２［ｃｍ３／ｓ］以上４８［ｃｍ３／ｓ］以下 At this time, the flow rate Q of the pump 10 can be calculated as follows using the above (Formula 5).
Q = q × n = 32 [cm 3 / s] or more and 48 [cm 3 / s] or less
　また、圧力Ｐは、上述の（式４）を用いて以下のように算出できる。なお、ここでは流出係数Ｃが１である場合を想定する。
　Ｐ＝ρ×（Ｑ／Ｃ×Ａ）２／２＝２．６８［Ｐａ］以上６．６９［Ｐａ］以下 Further, the pressure P can be calculated as follows using the above-described (Formula 4). Here, it is assumed that the outflow coefficient C is 1.
P = ρ × (Q / C × A) 2 /2=2.68 [Pa] or more and 6.69 [Pa] or less
　したがって、ばね定数ｋは、上述の（式３）を用いて以下のように算出できる。
　ｋ＝Ｐ×Ａ／Δｘ＝５．５６［Ｎ／ｍ］以上１３．９［Ｎ／ｍ］以下 Therefore, the spring constant k can be calculated as follows using (Equation 3) described above.
k = P × A / Δx = 5.56 [N / m] or more and 13.9 [N / m] or less
　本実施の形態２におけるスクロール圧縮機１００において、弾性体２１は、ばね定数ｋが上述の値の範囲内となるような材料及び形状で構成される。 In the scroll compressor 100 according to the second embodiment, the elastic body 21 is configured with a material and a shape such that the spring constant k is within the above-described value range.
　図７は本発明の実施の形態２に係るスクロール圧縮機１００の主軸４の回転数とポンプ１０から供給される潤滑油の供給量との関係を示した特性図である。図７の横軸には主軸４の回転数［ｒｐｓ］を示し、図７の縦軸には潤滑油供給量［ｃｃ／ｓ］を示している。以下に、図７を用いて、主軸４の回転数とポンプ１０から供給される潤滑油の供給量との関係について説明する。 FIG. 7 is a characteristic diagram showing the relationship between the rotational speed of the main shaft 4 of the scroll compressor 100 according to Embodiment 2 of the present invention and the supply amount of the lubricating oil supplied from the pump 10. The horizontal axis of FIG. 7 shows the rotational speed [rps] of the main shaft 4, and the vertical axis of FIG. 7 shows the lubricating oil supply amount [cc / s]. Below, the relationship between the rotation speed of the main shaft 4 and the supply amount of the lubricating oil supplied from the pump 10 will be described with reference to FIG.
　なお、図７においては、図３と同様に、潤滑油は、粘度３２ｃｓｔ、密度０．９ｇ／ｃｍ３以上１．０ｇ／ｃｍ３以下、油温－２０℃以上８０℃以下のものを使用し、ポンプ１０は吐出量０．３２ｃｍ３／ｒｅｖのものを使用したスクロール圧縮機１００を想定している。さらに、図７においては、運転範囲が１０ｒｐｓ以上２４０ｒｐｓ以下で、ポンプケーシング１１とポンプ１０とが当接している部分の面積が４１５ｍｍ２であるスクロール圧縮機１００を想定している。 In FIG. 7, as in FIG. 3, a lubricating oil having a viscosity of 32 cst, a density of 0.9 g / cm 3 to 1.0 g / cm 3 and an oil temperature of −20 ° C. to 80 ° C. is used. The scroll compressor 100 is assumed to use a pump 10 having a discharge amount of 0.32 cm 3 / rev. Further, in FIG. 7, it is assumed that the scroll compressor 100 has an operating range of 10 rps to 240 rps and an area where the pump casing 11 and the pump 10 are in contact with each other is 415 mm 2 .
　図７における（ａ）は、従来のスクロール圧縮機における主軸の回転数と潤滑油供給量との関係を示している。
　また、図７における（ｂ）は、本発明のスクロール圧縮機１００において、主軸４の回転数が１５０ｒｐｓの場合にＦ１＝Ｆ２の状態からＦ１＞Ｆ２の状態となるような弾性体２１を用いた場合における主軸４の回転数と潤滑油供給量との関係を示している。
　また、図７における（ｃ）は、本発明のスクロール圧縮機１００において、主軸４の回転数が１２０ｒｐｓの場合にＦ１＝Ｆ２の状態からＦ１＞Ｆ２の状態となるような弾性体２１を用いた場合における主軸４の回転数と潤滑油供給量との関係を示している。
　また、図７における（ｄ）は、本発明のスクロール圧縮機１００において、主軸４の回転数が１００ｒｐｓの場合にＦ１＝Ｆ２の状態からＦ１＞Ｆ２の状態となるような弾性体２１を用いた場合における主軸４の回転数と潤滑油供給量との関係を示している。
　また、図７における（Ａ）は、スクロール圧縮機の運転に際して要求される潤滑油供給量を示している。 (A) in FIG. 7 shows the relationship between the rotational speed of the main shaft and the lubricant supply amount in a conventional scroll compressor.
7B, the scroll compressor 100 according to the present invention uses an elastic body 21 that changes from F1 = F2 to F1> F2 when the rotational speed of the main shaft 4 is 150 rps. In this case, the relationship between the rotational speed of the main shaft 4 and the lubricant supply amount is shown.
7 (c), the scroll compressor 100 of the present invention uses an elastic body 21 that changes from F1 = F2 to F1> F2 when the rotational speed of the main shaft 4 is 120 rps. In this case, the relationship between the rotational speed of the main shaft 4 and the lubricant supply amount is shown.
7D, the scroll compressor 100 according to the present invention uses an elastic body 21 that changes from F1 = F2 to F1> F2 when the rotational speed of the main shaft 4 is 100 rps. In this case, the relationship between the rotational speed of the main shaft 4 and the lubricant supply amount is shown.
Moreover, (A) in FIG. 7 has shown the amount of lubricating oil supply requested | required at the time of a driving | operation of a scroll compressor.
　まず、主軸４の回転数が小さい場合には、本実施の形態２のスクロール圧縮機１００及び従来のスクロール圧縮機における潤滑油の供給量は、ポンプケーシング１１が押し上げられるまで略同一である。なお、ポンプケーシング１１が押し上げられない場合の主軸４の回転数は、例えば、１０ｒｐｓ以上１００ｒｐｓ以下の範囲内である。 First, when the rotational speed of the main shaft 4 is small, the supply amount of lubricating oil in the scroll compressor 100 of the second embodiment and the conventional scroll compressor is substantially the same until the pump casing 11 is pushed up. The rotation speed of the main shaft 4 when the pump casing 11 is not pushed up is, for example, in the range of 10 rps to 100 rps.
　次に、主軸４の回転数を次第に上昇させていくと、ポンプ１０の圧力が上昇してポンプケーシング１１が押し上げられる。例えば、主軸４の回転数が１００ｒｐｓを上回った場合に、ポンプケーシング１１が押し上げられる。 Next, when the rotational speed of the main shaft 4 is gradually increased, the pressure of the pump 10 increases and the pump casing 11 is pushed up. For example, the pump casing 11 is pushed up when the rotational speed of the main shaft 4 exceeds 100 rps.
　図７において、主軸４の回転数が１５０ｒｐｓを上回る場合における同一回転数である潤滑油供給量は、多い順に、（ｂ）、（ｃ）、（ｄ）となっている。このことから、Ｆ１＝Ｆ２の状態からＦ１＞Ｆ２の状態となるときの主軸４の回転数が大きくなるように弾性体２１を設計するほど、潤滑油の供給量は多くなることが分かる。そして、主軸４の回転数が１５０ｒｐｓの場合にＦ１＝Ｆ２の状態からＦ１＞Ｆ２となるような弾性体２１を用いた場合には（図７の（ｂ））、スクロール圧縮機１００の運転に際して要求される潤滑油供給量に近い潤滑油供給量を得ることができる。 In FIG. 7, the lubricating oil supply amount that is the same rotational speed when the rotational speed of the main shaft 4 exceeds 150 rps is (b), (c), and (d) in descending order. From this, it can be seen that the amount of lubricant supplied increases as the elastic body 21 is designed to increase the rotational speed of the main shaft 4 when F1 = F2 and F1> F2. When the elastic body 21 that satisfies F1> F2 from the state of F1 = F2 when the rotational speed of the main shaft 4 is 150 rps (FIG. 7B), the operation of the scroll compressor 100 is performed. A lubricating oil supply amount close to the required lubricating oil supply amount can be obtained.
　以上のように、本実施の形態２に係るスクロール圧縮機１００は、ポンプカバー１２の下面に一端が位置し且つポンプケーシング１１の上面に他端が位置するように取り付けられて基準長を有する弾性体２１を備え、ポンプ１０の内部には、油パイプ１７の内部と連通する低圧部２０ａと、低圧部２０ａよりも高圧となる高圧部２０ｂと、が設けられ、弾性体２１が基準長よりも収縮するようにポンプケーシング１１が上方に押圧されると、低圧部２０ａと高圧部２０ｂとを連通するように空隙εが設けられる。このため、スクロール圧縮機１００の運転時において、ポンプ１０内で圧縮されて圧力が上昇した潤滑油の一部は、高圧部２０ｂから空隙εを介して再び低圧部２０ａに供給される。したがって、低速運転時に必要な潤滑油の供給量を確保しつつ、高速運転時において過剰な潤滑油の供給量を抑制することができる。このようにして、機械損失を低減させることができ、高速運転可能なスクロール圧縮機１００を得ることができる。また、本実施の形態２においては、本実施の形態１と比べて、低速運転時における潤滑油の供給量を減少させないようにして、潤滑油を各摺動部に十分に供給することができる。 As described above, the scroll compressor 100 according to the second embodiment is attached so that one end is located on the lower surface of the pump cover 12 and the other end is located on the upper surface of the pump casing 11 and has an elastic length having a reference length. The pump 10 is provided with a low-pressure part 20a communicating with the inside of the oil pipe 17, and a high-pressure part 20b having a higher pressure than the low-pressure part 20a. The elastic body 21 is longer than the reference length. When the pump casing 11 is pressed upward so as to contract, a gap ε is provided so as to communicate the low pressure portion 20a and the high pressure portion 20b. For this reason, during the operation of the scroll compressor 100, a part of the lubricating oil which has been compressed in the pump 10 and whose pressure has increased is supplied again from the high pressure part 20b to the low pressure part 20a via the gap ε. Therefore, it is possible to suppress an excessive supply amount of the lubricating oil during the high speed operation while securing a supply amount of the lubricating oil necessary during the low speed operation. In this way, the mechanical loss can be reduced, and the scroll compressor 100 capable of high speed operation can be obtained. Further, in the second embodiment, as compared with the first embodiment, the lubricating oil can be sufficiently supplied to each sliding portion without reducing the amount of the lubricating oil supplied during low-speed operation. .
　なお、本実施の形態２においては、弾性体２１として、コイルばねを用いる例について説明したが、これに限定されない。例えば、弾性体２１として、さらばね等を使用してもよい。また、本実施の形態２においては、Ｆ１＝Ｆ２の状態からＦ１＞Ｆ２の状態となる場合における主軸４の回転数が１００ｒｐｓ、１２０ｒｐｓ、１５０ｒｐｓとなるように弾性体２１を設計する例について説明したが、主軸４の回転数の具体的な数値はこれに限定されない。 In addition, in this Embodiment 2, although the example using a coil spring was demonstrated as the elastic body 21, it is not limited to this. For example, a spring spring or the like may be used as the elastic body 21. Further, in the second embodiment, an example in which the elastic body 21 is designed so that the rotation speed of the main shaft 4 is 100 rps, 120 rps, and 150 rps when F1 = F2 is changed to F1> F2 has been described. However, the specific numerical value of the rotation speed of the main shaft 4 is not limited to this.
　また、本実施の形態２においては、ポンプ１０内の高圧部２０ｂから空隙εを介して低圧部２０ａへ潤滑油を移動させる構造について説明したが、これに限定されない。例えば、図８に示されるように、排出経路２２を設ける構造としてもよい。図８は本発明の実施の形態２に係るスクロール圧縮機１００の要部を示す断面図であり、図５の変形例である。図８に示されるように、排出経路２２は、ポンプケーシング１１が押し上げられて空隙εが形成された場合に、潤滑油が空隙εを介してポンプカバー１２の外部に流出するように形成される。排出経路２２は、例えば、空隙εが形成される高さと同一高さにおいてポンプカバー１２を水平方向に貫通し、空隙εとポンプカバー１２の外部とが連通するように設けられる。これにより、高圧部２０ｂから空隙εを介して低圧部２０ａに移動する潤滑油の量が減少し、再圧縮ロスを改善することができる。 In the second embodiment, the structure in which the lubricating oil is moved from the high-pressure portion 20b in the pump 10 to the low-pressure portion 20a through the gap ε is not limited to this. For example, as shown in FIG. 8, the discharge path 22 may be provided. FIG. 8 is a cross-sectional view showing a main part of the scroll compressor 100 according to Embodiment 2 of the present invention, which is a modification of FIG. As shown in FIG. 8, the discharge path 22 is formed so that the lubricating oil flows out of the pump cover 12 through the gap ε when the pump casing 11 is pushed up to form the gap ε. . For example, the discharge path 22 is provided so as to penetrate the pump cover 12 in the horizontal direction at the same height as the gap ε and to communicate with the outside of the pump cover 12. As a result, the amount of lubricating oil that moves from the high-pressure portion 20b to the low-pressure portion 20a via the gap ε is reduced, and the recompression loss can be improved.
　１　揺動スクロール、１ａ　台板、１ｂ　渦巻歯、２　固定スクロール、２ａ　台板、２ｂ　渦巻歯、３　フレーム、３ａ　主軸受、４　主軸、４ｂ　ポンプ軸、４ｃ　油穴、５　ステータ、６　ロータ、８　サブフレーム、９　玉軸受、１０　ポンプ、１１　ポンプケーシング、１２　ポンプカバー、１２ａ　収納部、１３ａ　吸入ポート、１３ｂ　吐出ポート、１６　油溜め部、１７　油パイプ、２０ａ　低圧部、２０ｂ　高圧部、２１　弾性体、２２　排出経路、３０　圧縮室、１００　スクロール圧縮機、１００Ａ　密閉容器、Ｃ　流出係数、Ｌ　高さ寸法、Ｐ　圧力、Ｑ　流量、ｋ　ばね定数、δ，ε　空隙。 1 swing scroll, 1a base plate, 1b spiral tooth, 2 fixed scroll, 2a base plate, 2b spiral tooth, 3 frame, 3a main bearing, 4 main shaft, 4b pump shaft, 4c oil hole, 5 stator, 6 rotor, 8 Sub frame, 9 ball bearing, 10 pump, 11 pump casing, 12 pump cover, 12a storage part, 13a intake port, 13b discharge port, 16 oil reservoir, 17 oil pipe, 20a low pressure part, 20b high pressure part, 21 elastic body 22 discharge path, 30 compression chamber, 100 scroll compressor, 100A airtight container, C outflow coefficient, L height dimension, P pressure, Q flow rate, k spring constant, δ, ε gap.

Claims (12)

  1. 　油溜め部を有する密閉容器と、
    　前記密閉容器の内部に設けられる主軸と、
    　前記主軸が回転することで駆動されるポンプと、
    　前記ポンプの上方に設けられるポンプケーシングと、
    　前記油溜め部に溜められる潤滑油を通す油パイプと、を備え、
    　前記ポンプの内部には、
    　前記油パイプの内部と連通する低圧部と、
    　前記低圧部よりも高圧となる高圧部と、が設けられ、
    　前記ポンプケーシングの下面と前記ポンプの上面との間には、前記低圧部と前記高圧部とを連通するように空隙が設けられている
    　スクロール圧縮機。     A sealed container having an oil sump;
    A main shaft provided inside the sealed container;
    A pump driven by rotation of the main shaft;
    A pump casing provided above the pump;
    An oil pipe for passing lubricating oil stored in the oil reservoir,
    Inside the pump,
    A low pressure portion communicating with the inside of the oil pipe;
    A high pressure part having a higher pressure than the low pressure part,
    An air gap is provided between the lower surface of the pump casing and the upper surface of the pump so as to communicate the low pressure portion and the high pressure portion.
  2. 　前記主軸の軸方向における前記空隙の大きさをδ、前記主軸の軸方向における前記ポンプの高さをＬとしたとき、
    　δ＝０．０４Ｌ以上０．０６Ｌ以下である
    　請求項１に記載のスクロール圧縮機。     When the size of the gap in the axial direction of the main shaft is δ, and the height of the pump in the axial direction of the main shaft is L,
    The scroll compressor according to claim 1, wherein δ is 0.04L or more and 0.06L or less.
  3. 　前記ポンプは、吐出量０．３２ｃｍ３／ｒｅｖのものであり、
    　前記潤滑油は、粘度３２ｃｓｔ、密度０．９ｇ／ｃｍ３以上１．０ｇ／ｃｍ３以下、油温－２０℃以上８０℃以下のものである
    　請求項１又は請求項２に記載のスクロール圧縮機。     The pump has a discharge rate of 0.32 cm 3 / rev,
    The scroll compressor according to claim 1, wherein the lubricating oil has a viscosity of 32 cst, a density of 0.9 g / cm 3 to 1.0 g / cm 3 , and an oil temperature of -20 ° C to 80 ° C. .
  4. 　前記主軸の回転数は１０ｒｐｓ以上２４０ｒｐｓ以下である
    　請求項１～請求項３の何れか一項に記載のスクロール圧縮機。     The scroll compressor according to any one of claims 1 to 3, wherein the rotation speed of the main shaft is not less than 10 rps and not more than 240 rps.
  5. 　油溜め部を有する密閉容器と、
    　前記密閉容器の内部に設けられる主軸と、
    　前記主軸が回転することで駆動されるポンプと、
    　前記ポンプの上方に設けられるポンプケーシングと、
    　前記ポンプケーシングの上方に設けられるポンプカバーと、
    　前記油溜め部に溜められる潤滑油を通す油パイプと、
    　前記ポンプカバーの下面に一端が位置し且つ前記ポンプケーシングの上面に他端が位置するように取り付けられて基準長を有する弾性体と、を備え、
    　前記ポンプの内部には、
    　前記油パイプの内部と連通する低圧部と、
    　前記低圧部よりも高圧の高圧部と、が設けられ、
    　前記弾性体が前記基準長よりも収縮するように前記ポンプケーシングが上方に押圧されると、前記低圧部と前記高圧部とを連通するように空隙が設けられる
    　スクロール圧縮機。     A sealed container having an oil sump;
    A main shaft provided inside the sealed container;
    A pump driven by rotation of the main shaft;
    A pump casing provided above the pump;
    A pump cover provided above the pump casing;
    An oil pipe for passing lubricating oil stored in the oil reservoir,
    An elastic body having a reference length attached so that one end is located on the lower surface of the pump cover and the other end is located on the upper surface of the pump casing;
    Inside the pump,
    A low pressure portion communicating with the inside of the oil pipe;
    A high pressure part having a pressure higher than that of the low pressure part,
    When the pump casing is pressed upward so that the elastic body contracts with respect to the reference length, a gap is provided so as to communicate the low pressure part and the high pressure part.
  6. 　前記弾性体は、
    　前記主軸の回転数１００ｒｐｓ以上１５０ｒｐｓ以下の範囲内で弾性変形し且つ前記主軸の軸方向に移動可能に構成されている
    　請求項５に記載のスクロール圧縮機。     The elastic body is
    6. The scroll compressor according to claim 5, wherein the scroll compressor is configured to be elastically deformed and movable in an axial direction of the main shaft within a range of a rotational speed of the main shaft of 100 rps to 150 rps.
  7. 　前記ポンプは、吐出量が０．３２ｃｍ３／ｒｅｖのものであり、
    　前記潤滑油は、粘度３２ｃｓｔ、密度０．９ｇ／ｃｍ３以上１．０ｇ／ｃｍ３以下、油温－２０℃以上８０℃以下のものである
    　請求項５又は請求項６に記載のスクロール圧縮機。     The pump has a discharge rate of 0.32 cm 3 / rev,
    The scroll compressor according to claim 5 or 6, wherein the lubricating oil has a viscosity of 32 cst, a density of 0.9 g / cm 3 to 1.0 g / cm 3 , and an oil temperature of -20 ° C to 80 ° C. .
  8. 　前記弾性体のばね定数は５．５６Ｎ／ｍ以上１３．９Ｎ／ｍ以下である
    　請求項５～請求項７の何れか一項に記載のスクロール圧縮機。     The scroll compressor according to any one of claims 5 to 7, wherein a spring constant of the elastic body is not less than 5.56 N / m and not more than 13.9 N / m.
  9. 　前記弾性体はコイルばねである
    　請求項５～請求項８の何れか一項に記載のスクロール圧縮機。     The scroll compressor according to any one of claims 5 to 8, wherein the elastic body is a coil spring.
  10. 　前記弾性体はさらばねである
    　請求項５～請求項８の何れか一項に記載のスクロール圧縮機。     The scroll compressor according to any one of claims 5 to 8, wherein the elastic body is a spring spring.
  11. 　前記空隙と前記ポンプカバーとを連通するように排出経路が設けられている
    　請求項５～請求項１０の何れか一項に記載のスクロール圧縮機。     The scroll compressor according to any one of claims 5 to 10, wherein a discharge path is provided to communicate the gap and the pump cover.
  12. 　前記主軸の回転数は１０ｒｐｓ以上２４０ｒｐｓ以下である
    　請求項５～請求項１１の何れか一項に記載のスクロール圧縮機。     The scroll compressor according to any one of claims 5 to 11, wherein the rotation speed of the main shaft is not less than 10 rps and not more than 240 rps.
PCT/JP2014/079577 2014-11-07 2014-11-07 Scroll compressor WO2016072013A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2014/079577 WO2016072013A1 (en) 2014-11-07 2014-11-07 Scroll compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2014/079577 WO2016072013A1 (en) 2014-11-07 2014-11-07 Scroll compressor

Publications (1)

Publication Number Publication Date
WO2016072013A1 true WO2016072013A1 (en) 2016-05-12

Family

ID=55908765

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2014/079577 WO2016072013A1 (en) 2014-11-07 2014-11-07 Scroll compressor

Country Status (1)

Country Link
WO (1) WO2016072013A1 (en)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02267378A (en) * 1989-04-10 1990-11-01 Mitsubishi Electric Corp Scroll type compressor
JPH0430285U (en) * 1990-07-04 1992-03-11
JPH1082393A (en) * 1996-09-06 1998-03-31 Matsushita Electric Ind Co Ltd Closed type compressor
US6287099B1 (en) * 1999-01-19 2001-09-11 Lg Electronics, Inc. Scroll compressor
JP2005042577A (en) * 2003-07-25 2005-02-17 Hitachi Home & Life Solutions Inc Closed type electric compressor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02267378A (en) * 1989-04-10 1990-11-01 Mitsubishi Electric Corp Scroll type compressor
JPH0430285U (en) * 1990-07-04 1992-03-11
JPH1082393A (en) * 1996-09-06 1998-03-31 Matsushita Electric Ind Co Ltd Closed type compressor
US6287099B1 (en) * 1999-01-19 2001-09-11 Lg Electronics, Inc. Scroll compressor
JP2005042577A (en) * 2003-07-25 2005-02-17 Hitachi Home & Life Solutions Inc Closed type electric compressor

Similar Documents

Publication Publication Date Title
US9784271B2 (en) Scroll compressor
US9850904B2 (en) Scroll compressor
US9732752B2 (en) Scroll compressor having a back pressure chamber assembly disposed on a fixed scroll plate and an elastic member disposed between a floating plate and a discharge cover
EP2390507B1 (en) Shaft bearing clearances for an hermetic compressor
KR101947305B1 (en) Scroll compressor
EP3214312B1 (en) Two-cylinder hermetic compressor
JP2010525240A (en) Compressor and oil supply structure thereof
KR100924203B1 (en) Scroll compressor
JP2010190167A (en) Scroll compressor
JP6555543B2 (en) Scroll compressor
JP6180630B2 (en) Compressor
JP5261227B2 (en) Scroll compressor
EP2947320B1 (en) Scroll compressor
JP6134903B2 (en) Positive displacement compressor
WO2017158665A1 (en) Scroll compressor
JP6625218B2 (en) Compressor
EP2905469A1 (en) Hermetic scroll compressor
WO2016072013A1 (en) Scroll compressor
US9970438B2 (en) Scroll compressor
JP2014136985A (en) Scroll type compressor
JP7051005B2 (en) Compressor
JP2019190468A (en) Scroll compressor
JPWO2020148857A1 (en) Scroll compressor
JP2013139714A (en) Scroll compressor
US11536272B2 (en) Lubricating oil supply apparatus and compressor using lubricating oil supply apparatus

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 14905355

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

NENP Non-entry into the national phase

Ref country code: JP

122 Ep: pct application non-entry in european phase

Ref document number: 14905355

Country of ref document: EP

Kind code of ref document: A1