WO2021124500A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2021124500A1
WO2021124500A1 PCT/JP2019/049737 JP2019049737W WO2021124500A1 WO 2021124500 A1 WO2021124500 A1 WO 2021124500A1 JP 2019049737 W JP2019049737 W JP 2019049737W WO 2021124500 A1 WO2021124500 A1 WO 2021124500A1
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WO
WIPO (PCT)
Prior art keywords
swivel
scroll
pressure
scroll compressor
crankshaft
Prior art date
Application number
PCT/JP2019/049737
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English (en)
Japanese (ja)
Inventor
遼太 飯島
柳瀬　裕一
近野　雅嗣
小山田　具永
Original Assignee
日立ジョンソンコントロールズ空調株式会社
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.)
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Publication date
Application filed by 日立ジョンソンコントロールズ空調株式会社 filed Critical 日立ジョンソンコントロールズ空調株式会社
Priority to PCT/JP2019/049737 priority Critical patent/WO2021124500A1/fr
Publication of WO2021124500A1 publication Critical patent/WO2021124500A1/fr

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    • 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

Definitions

  • the present invention relates to a scroll compressor that handles HFC-based refrigerants, natural refrigerants such as air and carbon dioxide, and other compressible gases, and in particular, is mainly provided on a swivel bearing and a frame provided on the back surface of a swivel scroll.
  • the present invention relates to a scroll compressor used in a refrigeration cycle device for refrigeration and air conditioning that uses a sliding bearing as a bearing.
  • scroll compressors are required to have a wide range of variable discharge capacity.
  • it is effective to expand the operating speed range of the scroll compressor.
  • increasing the maximum operating speed it is possible to increase the maximum discharge capacity without enlarging the dimensions of the compressor.
  • increasing the speed of the scroll compressor is important for realizing miniaturization and cost reduction.
  • the centrifugal force increases in the high speed range, the shaft bends, and one-sided contact occurs in the slide bearing portion such as the main bearing and the swing bearing, so that the friction loss increases and the reliability decreases.
  • the axial distance (axial span) between the swivel bearing that supports the swivel motion of the swivel scroll and the main bearing that supports the crankshaft that transmits the rotation of the electric motor is set.
  • a double slide bearing (double slide bearing) structure that can be shortened is effective.
  • a swivel shaft is provided on the swivel scroll side and inserted into the eccentric hole of the crankshaft via the swivel bearing, and the main bearing is further arranged outside the swivel bearing.
  • the axial span of the swing bearing and the main bearing can be shortened, so that the axial dimension of the scroll compressor can be reduced to reduce the size.
  • the balance weight can be reduced, so that the shaft deflection due to centrifugal force can be reduced and the one-sided contact in the main bearing during high-speed operation can be suppressed.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 64-41689
  • a motor unit, a compression mechanism unit, and a drive shaft for transmitting the rotational force of the electric motor to the compression mechanism unit are housed in a closed container, and each of the compression mechanism units is described.
  • a closed operating chamber in which the fixed scroll and the swivel scroll, which are upright on the end plate and have a spiral scroll wrap formed, are engaged with each other with the scroll wrap facing inward, and an old dam ring mechanism for preventing the swivel scroll from rotating.
  • the drive shaft is assumed to have a stepped portion formed by a large-diameter portion having the eccentric hole and a small-diameter portion directly connected to the rotor of the electric motor portion, and the swivel scroll shaft is formed in the eccentric hole.
  • a first thrust bearing having a diameter smaller than that of the large diameter of the drive shaft is provided between the end face of the large diameter portion of the drive shaft on the swivel scroll side and the back surface of the end plate on the opposite side of the swivel scroll.
  • a second thrust bearing having a diameter larger than that of the thrust bearing 1 is provided between the back surface of the end plate of the swivel scroll and the frame, and a third thrust bearing is provided between the stepped portion of the drive shaft and the frame.
  • a first thrust bearing is provided between the crankshaft and the back surface of the swivel scroll, and between the back surface of the swivel scroll and the frame.
  • a second thrust bearing is provided, and a third thrust bearing is further provided between the stepped portion provided on the crankshaft and the frame.
  • the bearing clearance in the thrust bearing has a constant size determined by the accuracy of processing and assembling the parts of the scroll compressor, high accuracy in processing and assembling is required to adjust the bearing clearance to an appropriate value. It is required and the productivity of the scroll compressor is reduced. In addition, it is not possible to deal with a wide range of deformations due to heat and pressure of parts such as the crankshaft, which change depending on the operating conditions of the scroll compressor, and the load acting on the swivel scroll. Therefore, it is difficult to avoid an increase in friction loss and a decrease in reliability.
  • An object of the present invention is to obtain a scroll compressor capable of suppressing stress concentration acting on one-sided contact in a main bearing or a swivel bearing or the root of a swivel shaft of a swivel scroll.
  • the present application includes a plurality of means for solving the above object, for example, a closed container, a frame fixed to the closed container, and a base plate and the base plate provided in the closed container.
  • a fixed scroll having a spiral wrap standing on the base plate
  • a swivel scroll having a base plate and a spiral wrap standing on the base plate, and meshing with the fixed scroll to form a compression chamber, and the swivel scroll.
  • a scroll compressor including a crankshaft that swivels the crankshaft, the main shaft portion provided at the swivel scroll side end portion of the crankshaft, and a swivel shaft provided protruding on the opposite side of the swivel scroll.
  • the swivel bearing provided between the swivel shaft and the eccentric hole, and the crankshaft and the frame.
  • a main bearing provided at substantially the same position in the axial direction as the swivel bearing to support the main shaft portion of the crankshaft, and a swivel support provided at the end portion of the crankshaft on the swivel scroll side to support the back surface of the swivel scroll.
  • the crankshaft is configured to be axially movable to a position where the swivel support portion supports the swivel scroll, and the crankshaft is configured to be axially movable to a position where the swivel support portion supports the swivel scroll. It is in a scroll compressor characterized by being configured to press on the back of a swivel scroll.
  • a scroll compressor capable of suppressing stress concentration acting on one-sided contact in a main bearing or a swivel bearing or the root of a swivel shaft of a swivel scroll.
  • FIG. 3 is a perspective view of the swivel support plate shown in FIG.
  • FIG. 1 is an enlarged view of a main part showing an enlarged configuration in the vicinity of the swivel support plate in FIG. 1, and is a diagram illustrating a refueling path and a distribution of pressure acting on the crankshaft and the swivel support plate.
  • FIG. 1 is an enlarged view of a main part showing an enlarged configuration near a swivel support plate in FIG. 1, and is a diagram for explaining a load generated on a swivel scroll, a crankshaft, and the like.
  • FIG. 5 is a plan view of the swivel support plate according to the first embodiment shown in FIG. 1, illustrating a preferable position of a pressure support space.
  • FIG. 1 is a vertical sectional view showing Example 1 of the scroll compressor of the present invention
  • FIG. 2 is a perspective view of the swivel support plate shown in FIG. 1
  • FIG. 3 is an enlarged view of the configuration in the vicinity of the swivel support plate in FIG.
  • the enlarged view of the main part is a diagram for explaining the refueling path and the distribution of the pressure acting on the crankshaft and the swivel support plate
  • FIG. 4 is an enlarged view of the main part showing the configuration near the swivel support plate in FIG. FIG.
  • FIG. 5 is a view for explaining the load generated on the swivel scroll, the crankshaft, and the like
  • FIG. 5 is a plan view of the swivel support plate according to the first embodiment shown in FIG. 1, and is a diagram for explaining a preferable position of the pressure support space.
  • the scroll compressor of the first embodiment shown in FIG. 1 supplies the lubricating oil of the oil sump to the bottom of the eccentric hole by a differential pressure lubrication method utilizing the pressure difference in the closed container, and the lubricating oil swirls from here. It is configured as a differential pressure lubrication type scroll compressor that flows to the bearing and main bearing, and then the lubricating oil flows out to the back pressure chamber.
  • the scroll compressor 1 is configured by housing the compression mechanism unit 2 and the drive unit 3 in a closed container 4.
  • the compression mechanism unit 2 is composed of a fixed scroll 21, a swivel scroll 22, a frame 23 fixed to the closed container 4, an old dam ring 24 and the like that constitute a rotation prevention mechanism of the swivel scroll 22.
  • the fixed scroll 21 has a base plate 21a and a spiral wrap (fixed wrap) 21b vertically erected on the end plate surface of the base plate 21a, and a discharge port 21c is provided at the center of the wrap 21b. It is formed and fixed to the frame 23 by a plurality of bolts 25.
  • the swivel scroll 22 has a base plate 22a and a spiral wrap (swivel wrap) 22b that stands vertically on the end plate surface of the base plate 22a, and is on the opposite side (rear side) of the base plate 22a.
  • a substantially cylindrical swivel shaft 22c is provided in the center so as to project.
  • the compression chamber 26 is formed by engaging the fixed scroll 21 and the swivel scroll 22, and the swivel scroll 22 moves in the center direction to reduce the volume of the compression chamber 26, so that the compression operation is performed. It is done.
  • a working fluid such as a refrigerant gas passes through a suction pipe 5 provided in the upper part of the closed container 4 and a suction port 5a provided coaxially with the suction pipe 5.
  • the working fluid sucked into the compression chamber 26 is sucked into the discharge space 6 in the closed container 4 from the discharge port 21c of the fixed scroll 21 through the compression stroke.
  • the working fluid discharged into the discharge space 6 then passes through flow paths (not shown) formed on the outer peripheral surface of the base plate 21a of the fixed scroll 21 and the outer peripheral surface of the frame 23, respectively, and the drive unit 3 Flows into the space 7 in which the is arranged, and is further discharged from the closed container 4 to the refrigeration cycle or the like via the discharge pipe 8 located below the frame 23.
  • the space inside the closed container 4 is maintained at a substantially discharge pressure.
  • the drive unit 3 that swivels the swivel scroll 22 is a stator (stator) 31a fixed to the closed container 4 by press fitting or welding, and a rotor (rotor) rotatably arranged inside the stator 31a. It is composed of an electric motor 31 including a rotor) 31b, a crankshaft 32 which is fixed to the center of the rotor 31b and rotates integrally to drive the swivel scroll 22 and the like.
  • a main bearing 27 that supports the main shaft portion 32a on the upper end side (swivel scroll side) of the crankshaft 32 is provided on the inner peripheral surface of the frame 23. Further, an eccentric hole 32b into which the swivel shaft 22c of the swivel scroll 22 is inserted is provided at the end of the crankshaft 32, and a swivel bearing 28 is provided between the swivel shaft 22c and the eccentric hole 32b. It is provided.
  • the swivel bearing 28 is inserted into the swivel shaft 22c, and is movable and rotatably arranged in the direction of the rotation axis with respect to the swivel shaft 22c and the eccentric hole 32b.
  • the scroll compressor 1 of this embodiment has a double slide bearing structure in which the main bearing 27 and the swing bearing 28 are provided at substantially the same positions in the axial direction. That is, the swivel bearing 28 is arranged so as to be included in the main bearing 27.
  • the spindle portion 32a on the upper end portion side of the crankshaft 32 is configured to have a diameter larger than the diameter of the crankshaft 32 other than the spindle portion 32a, and the spindle portion 32a is used as the spindle portion 27. It is rotationally supported by.
  • the lower shaft portion 32c on the lower end side (counter-turning scroll side) of the crankshaft 32 is rotationally supported by the lower bearing 9.
  • the lower bearing 9 is provided in the lower bearing housing 10, and the lower bearing housing 10 is fixed to the lower frame 11 fixed to the closed container 4.
  • the main bearing 27 and the lower bearing 9 that rotatably support the crankshaft 32 are on the compression mechanism portion 2 side and the oil sump portion 12 side provided on the bottom of the closed container 4 with respect to the motor 31. It is arranged in and respectively.
  • the eccentric hole 32b is formed in the spindle portion 32a and is open to the swivel scroll 22 side.
  • the swivel shaft 22c of the swivel scroll 22 is inserted into the eccentric hole 32b via the swivel bearing 28.
  • the crankshaft 32 rotates, the eccentric hole 32b swivels, and the swivel scroll 22 swivels without rotating due to the action of the old dam ring 24.
  • the swivel shaft 22c is rotatably engaged with the eccentric hole 32b so as to be movable in the axial direction.
  • the old dam ring 24 engages with the swivel scroll 22 and the key groove provided in the frame 23 to play the role of a rotation prevention mechanism of the swivel scroll 22. That is, the Oldam ring 24 is provided with two sets of orthogonal keys, one set slides on the key groove formed in the frame 23, and the remaining one set provides the key groove formed on the back surface of the swivel scroll 22. It is configured to slide. As a result, the swivel scroll 22 is configured to revolve in response to the eccentric motion of the eccentric hole 32b formed in the spindle portion 32a of the crankshaft 32 without rotating.
  • a refueling piece (refueling pipe) 32d is provided at the lower end of the crankshaft 32 so that the oil in the oil sump portion 12 is pumped up by a differential pressure and supplied to the refueling passage 32e formed at the center of the crankshaft 32. It is configured.
  • the scroll compressor 1 in the present embodiment has a swivel support plate (swivel support portion) 13 that rotates integrally with the crankshaft 32 on the end surface of the crankshaft 32 on the swivel scroll 22 side, that is, the upper end surface of the spindle portion 32a. Is attached by press fitting.
  • FIG. 2 is a perspective view showing only the swivel support plate 13 shown in FIG. 1 taken out, and is an external view showing an example of the swivel support plate 13.
  • the outer diameter of the swivel support plate 13 is larger than the outer diameter of the main shaft portion 32a of the crankshaft 32.
  • a cylindrical fitting portion 13a that is fitted and fixed to the outer peripheral surface of the end portion of the main shaft portion 32a by press fitting is provided, and the swivel scroll on the outer peripheral side of the fitting portion 13a is provided.
  • the 22-side end surface is configured as a flat swivel support surface 13b that supports the back surface of the base plate 22a of the swivel scroll 22.
  • a part of the cylindrical fitting portion 13a on the outer peripheral side, that is, a part of the swivel support surface 13b on the inner peripheral side is recessed in the axial direction from the swivel support surface 13b.
  • the pressure support space 13c is formed in a cylindrical shape.
  • the area S1 shown by the broken line indicates the area surrounded by the outer circumference of the swivel support plate 13, and the area S3 shown by the broken line shows the area surrounded by the outer circumference of the pressure support space 13c.
  • the pressure support space 13c is formed by being surrounded by the swivel support plate 13, the back surface of the swivel scroll 22, the swivel shaft 22c, the spindle portion 32a, and the swivel bearing 28, and is lower than the discharge pressure.
  • the pressure is configured to be higher than the pressure of the back pressure chamber.
  • the area of the pressure support space 13c is smaller than the cross-sectional area of the spindle portion 32a supported by the main bearing 27.
  • the crankshaft 32 is not completely constrained in the axial direction, and can move upward (swivel scroll side) in the axial direction until the swivel support surface 13b and the swivel scroll 22 come into contact with each other.
  • it is configured to be movable downward in the axial direction (on the anti-swivel scroll side) until it comes into contact with the thrust bearing 14 provided in the lower bearing housing 10. That is, the axial movement of the crankshaft 32 is regulated by the swivel scroll 22 and the thrust bearing 14.
  • the swivel support plate 13 is fixed to the crankshaft 32 separately from the crankshaft 32, but instead of the swivel support plate 13, it has the same shape as the swivel support plate 13. It may be integrally formed with the upper end portion of the crankshaft 32 to form a swivel support portion.
  • FIG. 3A is an enlarged view of part A shown in FIG. 1, showing a configuration in the vicinity of the swivel support plate 13.
  • the lubricating oil in the oil sump portion 12 at the bottom of the closed container 4 has an atmosphere of discharge pressure, and the pressure in the back pressure chamber 29 is a pressure (intermediate pressure) between the discharge pressure and the suction pressure. .. Utilizing this pressure difference, the lubricating oil in the oil sump portion 12 is pumped up to the upper eccentric hole 32b via the lubrication piece 32d and the lubrication passage 32e.
  • the arrow in FIG. 3A indicates the flow of lubricating oil, and the lubricating oil pumped up in the eccentric hole 32b is distributed to the main bearing 27 and the swivel bearing 28 to lubricate them.
  • the oil that lubricates the main bearing 27 flows into the back pressure chamber 29.
  • the oil that lubricates the swivel bearing 28 flows into the pressure support space 13c formed of the swivel support plate 13 and the like, and then the gap between the swivel support surface 13b of the swivel support plate 13 and the back surface of the swivel scroll 22. Lubricate between them while passing through the back pressure chamber 29.
  • a horizontal lubrication hole 32f is formed in the spindle portion 32a in order to allow a part of the lubricating oil supplied to the eccentric hole 32b to flow to the main bearing 27.
  • the lubricating oil is mixed with the refrigerant gas in the compression chamber 26 and discharged from the discharge port 21c into the discharge space 6.
  • the lubricating oil discharged into the discharge space 6 is separated from the refrigerant gas in the process in which the refrigerant gas flows from the discharge space 6 to the space 7 in which the motor 31 is arranged and is discharged from the discharge pipe 8.
  • the lower bearing 9 is lubricated through a horizontal lubrication hole 32g formed in the lower shaft portion 32c by a part of the lubricating oil flowing through the lubrication passage 32e formed in the crankshaft 32.
  • S1 is surrounded by the outer circumference of the swivel support plate 13 (the area surrounded by the outer circumference of the swivel support surface 13b), and S3 is surrounded by the outer circumference of the pressure support space 13c. Shows the area.
  • S2 shown in FIG. 3 shows the cross-sectional area of the main shaft portion 32a, and S4 shows the cross-sectional area of the eccentric hole 32b.
  • Pd indicates the discharge pressure
  • Pb indicates the pressure of the back pressure chamber 29 (back pressure)
  • Pi indicates the pressure in the pressure support space 13c.
  • Equation 1 is established from the configuration of the refueling route described above.
  • Equation 1 the thrust force (force acting in the axial direction) acting on the crankshaft 32 will be described.
  • FIG. 3B shows the distribution of pressure acting on the crankshaft 32 in the axial direction. From FIG. 3B, the relational expression of the axial force acting on the crankshaft 32 can be expressed as the following equation 2.
  • F is the reaction force on the contact surface between the swivel support plate 13 and the swivel scroll 22
  • Fg is the gravity acting on a rotating body that rotates integrally with the crankshaft 32, such as the crankshaft 32 and the rotor 31b. is there.
  • Fg is usually considerably smaller than the axial force generated by the pressure difference, Fg will be ignored in the following description.
  • the condition for generating a contact force between the crankshaft 32 and the swivel scroll 22 from the above equation 2, that is, the condition for satisfying F> 0 can be arranged as follows. -(Pi-Pb) / 2 x S1 + (Pd-Pb) x S2- (Pi-Pb) / 2 ⁇ S3- (Pd-Pi) ⁇ S4> 0... (Equation 3) Regarding this equation, considering that the relationship of Equation 1 and that S2 and S4 are values determined by the bearing specifications, F> 0 can be satisfied by reducing S1 and S3. That is, the crankshaft 32 can be floated and pressed against the swivel scroll 22 to support it in the thrust direction.
  • Equation 3 For the purpose of securing the support area of the swivel support plate 13, it is desirable to satisfy the relationship of Equation 3 and levitate the crankshaft 32 by making S3 particularly small ( ⁇ S2) rather than making S1 small.
  • S3 particularly small
  • S2 the same effect can be obtained by setting the pressure Pi of the pressure support space 13c low by adjusting the gap of the swivel bearing 28 or the like. This can be understood from the pressure distribution in FIG. 3 (b).
  • FIG. 4 is an enlarged view of part A of FIG. 1 and is a diagram for explaining a load generated on the swivel scroll 22, the crankshaft 32, and the like.
  • the back surface of the swivel scroll 22 can be supported in the thrust direction (axial direction) by the pressure in the swivel support plate 13 and the pressure support space 13c, so that as shown by the arrow c in FIG. A load can be generated in a direction that suppresses the overturning of the swivel scroll 22. As a result, it is possible to reduce the one-sided contact of the swivel shaft 22c.
  • FIG. 5 is a plan view of the swivel support plate 13 viewed from above (swivel scroll 22 side), and is a diagram illustrating a preferable position of the pressure support space 13c.
  • A indicates the center of the crankshaft 32
  • B indicates the center of the eccentric hole 32b
  • C indicates the center of the pressure support space 13c.
  • the direction from the center A of the crankshaft 32 toward the center B of the eccentric hole 32b is the eccentric direction.
  • the crankshaft 32 will be described below assuming that the crankshaft 32 rotates in the direction of the arrow described as the rotation direction in FIG.
  • the swivel shaft 22c of the swivel scroll 22 Since the central axis of the swivel shaft 22c of the swivel scroll 22 coincides with the center B of the eccentric hole 32b, the swivel shaft 22c swivels to the left in FIG. 5 from the position of the center B, and the swivel scroll 22 Compresses the refrigerant gas. As a reaction to this, a load acts on the swivel scroll 22 in the right direction (arrow d direction) of the drawing, and the right side of the swivel scroll 22 is in the back direction of the paper (vertically downward direction or the approaching direction to the swivel support surface 13b). ) Is generated.
  • the pressure support space 13c in the swivel support plate 13 so as to be eccentric so that the center C is at the position of the arrow d direction (the load direction acting on the swivel scroll 22), the pressure of the pressure support space 13c is increased. It can be supported so as to prevent the swivel scroll 22 from overturning. Therefore, it is possible to more effectively reduce the one-sided contact of the swivel shaft 22c.
  • the center C of the pressure support space 13c is preferably provided within a range of 0 ° to 90 ° in the counter-rotation direction around the center B from the arrow e in the eccentric direction starting from the center B of the eccentric hole 32b.
  • a tangential gas load W1 and a radial gas load W2 act on the swivel scroll 22 due to the compression operation by the swivel scroll 22.
  • a load V due to centrifugal force acts on the swivel scroll 22. Therefore, the resultant force T due to the loads W1, W2, V acts on the turning scroll 22, the turning scroll 22 is inclined in the direction of the resultant force T, and the turning scroll 22 is most separated from the fixed scroll 21 in the direction of the resultant force T. It will be easy to do.
  • the centrifugal force V becomes large, so that "radial gas load ⁇ centrifugal force" holds. Therefore, the resultant force T is located within a range of 0 ° to 90 ° in the counter-rotation direction around the center B from the arrow e in the eccentric direction starting from the center B of the eccentric hole 32b shown in FIG. Therefore, if the center of the pressure support space 13c is provided within a range of 0 ° to 90 ° in the counter-rotation direction around the center of the eccentric hole from the eccentric direction starting from the center of the eccentric hole 32b, the swivel scroll 22 capsizes. Can be effectively reduced to reduce the one-sided contact of the swivel shaft 22c.
  • the swivel support plate 13 is provided to raise the crankshaft 32 by the pressure difference, and the swivel scroll 22 is tilted. Since it is configured to suppress, in addition to the one-sided contact suppressing effect in the main bearing 27 portion, the one-sided contact in the swivel bearing 28 portion can also be suppressed. Further, since the tilt of the swivel scroll 22 can be suppressed, the stress concentration generated at the root portion of the swivel shaft 22c can also be suppressed. Therefore, according to this embodiment, it is possible to realize a highly efficient and highly reliable scroll compressor that can be operated up to a high speed range and has a small friction loss.
  • FIG. 6 is a perspective view of the swivel support plate in the second embodiment, and is the same as that of the first embodiment except for the configuration of the swivel support plate. Therefore, the description of the configuration other than the swivel support plate will be omitted.
  • the swivel support plate (swivel support portion) 13 shown in FIG. 1 is configured as the swivel support plate (swivel support portion) 13'shown in FIG.
  • the swivel support plate 13'in the second embodiment is provided with an arcuate oil groove 13d on the swivel support surface 13b along the outer peripheral side of the pressure support space 13c of the swivel support plate 13'. Is.
  • the oil groove 13d is configured to reach the outer periphery of the swivel support surface 13b and does not communicate with the pressure support space 13c.
  • the oil groove 13d can not only supply oil to the swivel support surface 13b which is a sliding surface in communication with the back pressure chamber 29 shown in FIG. 1 and the like, but also oil.
  • the pressure at the groove 13d and the swivel support surface 13b outside the oil groove 13d can be reduced to the pressure (back pressure) Pb of the back pressure chamber 29. Therefore, the force for ascending the crankshaft 32 described in the first embodiment can be further increased.
  • the apparent area S1 can be reduced. More specifically, on the swivel support surface 13b, the range in which the pressure between the pressure Pi and the back pressure Pb in the pressure support space 13c acts is reduced, and the range in which the lower back pressure Pb acts is expanded. Because.
  • the present invention is not limited to the above-described embodiment, and includes various modifications. Further, the above-described embodiment has been described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to the one including all the described configurations.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne un compresseur à spirale comprenant un contenant hermétique, un cadre, une spirale fixe, une spirale orbitale et un vilebrequin. Le compresseur à spirale comprend également : une partie d'arbre principal disposée sur une section d'extrémité côté spirale orbitale du vilebrequin ; un arbre orbital disposé de manière à faire saillie en direction d'un côté de contre-recouvrement de la spirale orbitale ; un trou excentré qui est disposé dans une section d'extrémité de partie d'arbre principal du vilebrequin et dans lequel est introduit l'arbre orbital ; un palier d'arbre orbital disposé entre l'arbre orbital et le trou excentré ; un palier d'arbre principal qui est disposé entre le vilebrequin et le cadre, sensiblement dans la même position dans la direction axiale que le palier d'arbre orbital, et qui supporte la partie d'arbre principal du vilebrequin ; et une partie de support orbital qui est disposée sur une section d'extrémité côté spirale orbitale du vilebrequin et qui supporte la surface arrière de la spirale orbitale. Le vilebrequin est conçu pour être déplacé dans la direction axiale jusqu'à la position dans laquelle la partie de support orbital supporte la spirale orbitale et est conçu pour comprimer la surface arrière de la spirale orbitale par l'intermédiaire de la partie de support orbital grâce à un différentiel de pression dans la direction axiale s'exerçant sur le vilebrequin.
PCT/JP2019/049737 2019-12-19 2019-12-19 Compresseur à spirale WO2021124500A1 (fr)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11852144B2 (en) 2021-09-03 2023-12-26 Danfoss (Tianjin) Ltd. Scroll compressor

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH029973A (ja) * 1988-06-28 1990-01-12 Daikin Ind Ltd スクロール型流体装置
JPH04284193A (ja) * 1991-03-11 1992-10-08 Matsushita Electric Ind Co Ltd スクロール圧縮機
JPH06317271A (ja) * 1993-05-06 1994-11-15 Hitachi Ltd 密閉形スクロール圧縮機
JP2011196265A (ja) * 2010-03-19 2011-10-06 Daikin Industries Ltd スクロール圧縮機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH029973A (ja) * 1988-06-28 1990-01-12 Daikin Ind Ltd スクロール型流体装置
JPH04284193A (ja) * 1991-03-11 1992-10-08 Matsushita Electric Ind Co Ltd スクロール圧縮機
JPH06317271A (ja) * 1993-05-06 1994-11-15 Hitachi Ltd 密閉形スクロール圧縮機
JP2011196265A (ja) * 2010-03-19 2011-10-06 Daikin Industries Ltd スクロール圧縮機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11852144B2 (en) 2021-09-03 2023-12-26 Danfoss (Tianjin) Ltd. Scroll compressor

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