WO2020136786A1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
WO2020136786A1
WO2020136786A1 PCT/JP2018/048052 JP2018048052W WO2020136786A1 WO 2020136786 A1 WO2020136786 A1 WO 2020136786A1 JP 2018048052 W JP2018048052 W JP 2018048052W WO 2020136786 A1 WO2020136786 A1 WO 2020136786A1
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WO
WIPO (PCT)
Prior art keywords
pressure
chamber
control valve
unload
space
Prior art date
Application number
PCT/JP2018/048052
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French (fr)
Japanese (ja)
Inventor
角田　昌之
渉 岩竹
佐々木　圭
雷人 河村
関屋　慎
英人 中尾
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.)
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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/JP2018/048052 priority Critical patent/WO2020136786A1/en
Priority to JP2020562036A priority patent/JP7012881B2/en
Publication of WO2020136786A1 publication Critical patent/WO2020136786A1/en

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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 used for refrigeration or air conditioning.
  • the relief mechanism for performing overcompression relief by high-pressure bypass is a relief port and a relief valve provided in the fixed scroll, which is completed in a closed container.
  • the unloading mechanism that performs unloading by low-pressure bypass requires a pipe that penetrates the closed container to connect the pipe and the compression mechanism portion, and also needs to include valves.
  • an increase in cost was unavoidable.
  • the present invention has been made in view of the above circumstances, and an object thereof is to obtain a scroll compressor capable of performing unloading by low-pressure bypass without connecting a pipe from the outside of the closed container to the compression mechanism section.
  • the scroll compressor of the present invention has a closed container, a separator that divides the closed container into a high-pressure space and a low-pressure space, a fixed scroll and an orbiting scroll, and is formed by engaging the fixed scroll and the orbiting scroll.
  • the compression mechanism that sucks fluid from the low-pressure space into the compression chamber and compresses it, and discharges it to the high-pressure space, and the unloading that limits the discharge amount by bypassing the fluid from the compression chamber to the low-pressure space.
  • a back pressure chamber communicating with the compression chamber in the middle of compression is formed between the separator and the end surface of the fixed scroll on the side opposite to the oscillating scroll, and through the extraction hole formed in the fixed scroll.
  • an unload that connects the back pressure chamber including the back pressure chamber communication passage, the control valve small diameter outer peripheral space, and the low pressure space communication passage to the low pressure space.
  • the unloading mechanism is equipped with a control valve that opens and closes the unloading path by moving the position in the unloading hole, and during operation, the low pressure space is provided on one end face in the moving direction of the control valve.
  • the low pressure of the control valve acts on the other end surface of the control valve, which is guided from the closed container to a pressure higher than that of the low pressure space, and the pressure difference between the two end surfaces of the control valve changes according to the operating conditions. It moves to open and close the unloading path.
  • the unloading that restricts the discharge amount is completed in the closed container, and the piping from the closed container to the compression mechanism part is completed. It can be done without a connection.
  • FIG. 1 is a schematic vertical sectional view of a scroll compressor according to Embodiment 1 of the present invention. It is a figure which shows the compression process accompanying the eccentric rotation of the orbiting scroll of the scroll compressor of FIG.
  • FIG. 3 is a schematic cross-sectional view of essential parts of the scroll compressor according to Embodiment 1 of the present invention when it is unloaded.
  • FIG. 3 is an enlarged schematic diagram of an unload mechanism section during unloading of the scroll compressor according to the first embodiment of the present invention.
  • FIG. 3 is a schematic cross-sectional view of a main part of the scroll compressor according to Embodiment 1 of the present invention when it is not unloaded.
  • FIG. 3 is an enlarged schematic diagram of an unload mechanism unit when the scroll compressor according to Embodiment 1 of the present invention is not unloading.
  • FIG. 6 is a schematic vertical sectional view of a scroll compressor according to Embodiment 2 of the present invention.
  • FIG. 6 is a schematic cross-sectional view of a main part of a scroll compressor according to Embodiment 2 of the present invention.
  • FIG. 9 is an enlarged schematic diagram of an unload mechanism section during unloading of the scroll compressor according to the second embodiment of the present invention.
  • FIG. 9 is an enlarged schematic diagram of an unload mechanism section when a scroll compressor according to Embodiment 2 of the present invention is not unloaded. It is the figure which looked at the fixed scroll of FIG. 7 from the spiral side.
  • FIG. 6 is a plan view showing a spiral combined state when a scroll compressor according to Embodiment 2 of the present invention is unloaded.
  • FIG. 16 is an enlarged shape view of the unload mechanism section of FIG. 15. It is a shape figure of the control valve which is an unload mechanism part of Drawing 7. It is a shape figure of the spring seat which is an unload mechanism part of FIG. It is a shape figure of the plug which is an unload mechanism part of Drawing 7.
  • FIG. 7 is a plan view showing a spiral combined state of the scroll compressor according to Embodiment 2 of the present invention when it is not unloaded. It is an enlarged shape figure of the unloading mechanism part of FIG.
  • Embodiment 1. 1 is a schematic vertical sectional view of a scroll compressor according to a first embodiment of the present invention.
  • the same reference numerals are the same or equivalent, and this is common to all the texts of the specification.
  • the forms of the constituent elements appearing in the entire text of the specification are merely examples, and the present invention is not limited to these descriptions.
  • the level of the temperature and the pressure the level is not fixed particularly in relation to the absolute value, but is relatively set in the state and operation of the system and the device. Further, the schematic diagram does not faithfully present the structure in which the workability and the assemblability of the embodiment are taken into consideration, but is a simple one for simply explaining the configuration.
  • the scroll compressor 1 has a function of sucking a fluid such as a refrigerant, compressing the fluid, and discharging the fluid in a high-pressure state.
  • a fluid such as a refrigerant
  • the motor 18 Inside the closed container 21 that constitutes the outer shell, the compression mechanism section 10, the motor 18, and other components. Store the components of.
  • the compression mechanism 10 and the motor 18 are connected by a shaft 15.
  • the compression mechanism portion 10 is arranged above, and the motor 18 is arranged below the compression mechanism portion 10.
  • Below the closed container 21 is an oil sump, in which the lubricating oil 22 is stored.
  • the frame 14 and the sub-frame 19 are arranged inside the closed container 21.
  • the frame 14 is disposed above the motor 18 and is located between the motor 18 and the compression mechanism unit 10.
  • the sub-frame 19 is located below the motor 18.
  • the frame 14 and the sub-frame 19 are fixed to a closed container 21.
  • a main bearing 14a is provided at the center of the frame 14, and a sub bearing 19a is provided at the center of the sub-frame 19.
  • a shaft 15 is rotatably supported by the main bearing 14a and the sub bearing 19a.
  • a separator 29 that partitions the inside of the closed container 21 into a high-pressure space 211 and a low-pressure space 212 is arranged above the compression mechanism unit 10.
  • a high pressure space 211 is above the separator 29, and a low pressure space 212 is below.
  • the separator 29 is fixed to the closed container 21.
  • a discharge chamber 291a communicating with the first discharge port 111 formed in the fixed scroll 11 is formed between the separator 29 and the end surface of the fixed scroll 11 on the side opposite to the orbiting scroll 12.
  • a second discharge port 292 for discharging the fluid compressed in the compression chamber 9 to the high pressure space 211 is formed in the center of the separator 29, the inlet side of which opens into the discharge chamber 291a and the outlet side of which opens into the high pressure space 211. ing.
  • a discharge valve 25 that opens and closes the second discharge port 292 in order to prevent backflow of the fluid to the discharge chamber 291a, and a discharge valve stopper 25b that limits the lift amount of the discharge valve 25.
  • the discharge valve 25 When the fluid is compressed to a predetermined pressure in the compression chamber 9, the discharge valve 25 is lifted up against its elastic force, the compressed fluid is discharged from the second discharge port 292 into the high pressure space 211, and the discharge pipe 24 And is discharged to the outside of the scroll compressor 1.
  • the separator 29 is further provided with a relief mechanism 220, an unload mechanism 230, etc., but the configuration of these will be described in detail again.
  • the airtight container 21 is provided with a suction pipe 23 that communicates with the low pressure space 212 to suck the fluid, and a discharge pipe 24 that communicates with the high pressure space 211 and discharge the fluid.
  • the compression mechanism unit 10 compresses the fluid sucked from the suction pipe 23 and discharges it into the high-pressure space 211 formed above the inside of the closed container 21.
  • the compression mechanism unit 10 includes a fixed scroll 11 and an orbiting scroll 12. As shown in FIG. 1, the fixed scroll 11 is arranged on the upper side and the orbiting scroll 12 is arranged on the lower side.
  • the fixed scroll 11 is composed of a fixed base plate 11a and fixed spiral teeth 11b which are spiral protrusions provided upright on one surface of the fixed base plate 11a.
  • the oscillating scroll 12 includes an oscillating base plate 12a and oscillating spiral teeth 12b, which are spiral protrusions provided upright on one surface of the oscillating base plate 12a.
  • the fixed spiral tooth 11b and the oscillating spiral tooth 12b are formed, for example, according to an involute curve, and the fixed spiral tooth 11b and the oscillating spiral tooth 12b are meshed with each other so that the fixed spiral tooth 11b and the oscillating spiral tooth 12b are combined.
  • a plurality of compression chambers 9 are formed between the compression chambers 12 and 12b.
  • the fixed scroll 11 and the orbiting scroll 12 are arranged between the separator 29 and the frame 14.
  • the planar position and the posture of the fixed scroll 11 are regulated by a plurality of radial guide members 28 arranged on the outer circumference of the fixed scroll 11.
  • the fixed base plate 11a of the fixed scroll 11 is formed with a pair of bleed holes 112, one end of which opens into the compression chamber 9 and the other end of which opens into a back pressure chamber 291b described later.
  • a cylindrical boss 121 is formed in the center of the surface of the orbiting scroll 12 opposite to the surface on which the orbiting spiral teeth 12b are formed.
  • the oscillating scroll 12 has an eccentric portion 15a, which will be described later, provided at the upper end of the shaft 15 fitted into the boss portion 121, and performs an eccentric orbiting motion without rotating with respect to the fixed scroll 11.
  • the motor 18 includes a stator 18a and a rotor 18b fixed to a shaft 15 that is rotatable on the inner peripheral side of the stator 18a.
  • the stator 18a rotates the rotor 18b by being energized.
  • the outer peripheral surface of the stator 18a is fixedly supported by the closed container 21 by shrink fitting or the like.
  • the rotor 18b rotates by energizing the stator 18a, and drives the shaft 15.
  • the shaft 15 has an eccentric part 15a formed at the upper end, and the eccentric part 15a is fitted to the boss part 121 of the orbiting scroll 12, and the orbiting scroll 12 makes an eccentric orbital motion by the rotation of the shaft 15.
  • a first balancer 16 is attached to the shaft 15 above the motor 18. Further, the second balancer 17 is attached to the lower side of the rotor 18b. The first balancer 16 is attached so that the eccentric direction is opposite to that of the eccentric portion 15a.
  • An oil supply pump 27 is attached to the lower end of the shaft 15.
  • the oil supply pump 27 supplies the lubricating oil 22 held in the oil sump to each sliding portion through an oil supply hole 152 provided inside the shaft 15 as the shaft 15 rotates.
  • an attitude regulating means 13 such as an Oldham ring for preventing rotation of the orbiting scroll 12 during eccentric orbiting movement is provided.
  • the posture restricting means 13 is arranged between the frame 14 and the orbiting scroll 12, and prevents the orbiting movement of the orbiting scroll 12 and enables an eccentric orbiting movement which is an orbiting movement.
  • the unbalance due to the movement of the orbiting scroll 12 is balanced by the first balancer 16 attached to the shaft 15 and the second balancer 17 attached to the rotor 18b.
  • the rotation of the shaft 15 causes the lubricating oil 22 stored in the lower portion of the closed container 21 to be pumped up by the oil supply pump 27 and supplied to each sliding portion from the oil supply hole 152 provided in the shaft 15.
  • the gas sucked into the closed container 21 from the suction pipe 23 is taken into the outermost compression chamber 9 among the plurality of compression chambers 9 along with the eccentric orbiting motion of the orbiting scroll 12.
  • the compression chamber 9 that has taken in gas compresses the fluid by reducing the volume while moving from the outer peripheral portion toward the center along with the eccentric orbiting motion of the orbiting scroll 12.
  • the compressed fluid is pushed up the discharge valve 25 from the first discharge port 111 provided in the fixed scroll 11 and the second discharge port 292 provided in the separator 29 to be discharged into the high pressure space 211, and discharged from the discharge pipe 24 to the outside of the closed container 21. Is discharged to.
  • FIG. 2 is a diagram showing a compression stroke accompanying eccentric rotation of the orbiting scroll of the scroll compressor of FIG.
  • the innermost compression chamber 9 is the innermost chamber 9a
  • the outermost compression chamber 9 is the outermost chamber 9c
  • the compression between the innermost chamber 9a and the outermost chamber 9c is performed.
  • the chamber 9 is called a second chamber 9b in the sense that it is the second compression chamber counted from the inside.
  • FIG. 2 shows an example of a spiral specification of about 2.5 turns.
  • Fig. 2(b) shows the state where the crank angle is the intake completion angle. That is, the suction of the fluid in the outermost compression chamber 9 is completed, and as the plurality of compression chambers 9 formed by the fixed spiral teeth 11b and the swing spiral teeth 12b, the innermost chamber 9a and the pair of innermost chambers 9a are arranged in order from the inside. The place where the second chamber 9b and the pair of outermost chambers 9c are formed is shown.
  • the suction completion angle refers to the crank angle when the suction of the compression chamber 9 is completed on the winding end side of the spiral tooth.
  • Fig. 2(c) shows a state in which the crank angle is the communication angle.
  • the fixed spiral tooth 11b and the oscillating spiral tooth 12b contact each other on the winding start side to form the seal forming point 130, so that the innermost chamber 9a and the pair of second chambers 9b are formed. And are formed.
  • the second chamber 9b merges with the innermost chamber 9a to become one chamber immediately before the seal forming point 130 is separated.
  • the communication angle refers to the crank angle when the second chamber 9b merges with the innermost chamber 9a to form one chamber.
  • FIG. 2D shows a state in which the seal forming point 130 is separated and the second chamber 9b is combined with the innermost chamber 9a to form one chamber, and the innermost chamber 9a and the outermost chamber 9c are two chambers. ing.
  • the compression chamber 9 becomes two or three chambers depending on the magnitude of the crank angle with respect to the suction completion angle and the communication angle during one rotation of the eccentric rotation of the orbiting scroll 12 having a crank angle of 0 to 2 ⁇ . That is, there are three chambers, the outermost chamber 9c, the second chamber 9b, and the innermost chamber 9a, between the suction completion angle and the communication angle. Between the communication angle and the suction completion angle, there are two chambers, the outermost chamber 9c and the innermost chamber 9a. Then, a new outermost chamber 9c is formed at the suction completion angle, and the outermost chamber 9c up to that point becomes the second chamber 9b, and becomes the outermost chamber 9c, the second chamber 9b, and the innermost chamber 9a. ..
  • the outermost chamber 9c of which suction has been completed in FIG. 2(b) is eccentrically swung by the orbiting scroll 12 so that the outermost chamber 9c of FIG. 2(c), FIG. 2(e), FIG. 2(f), and FIG. 2(a), the volume is reduced, whereby the fluid is compressed. Then, the outermost chamber 9c is newly formed by reaching FIG. 2B again, so that the outermost chamber 9c thus far becomes the second chamber 9b.
  • the second chamber 9b starts to join the innermost chamber 9a at the communication angle in FIG. 2(c).
  • the pair of bleed holes 112 are provided along the inward/outward surfaces of the fixed spiral teeth 11b, respectively, and extend from the winding end portion 11ba and the winding end portion 11bb (see FIG. 2(b)) of each of the inward/outward surfaces. It is located inside about 2.5 ⁇ at the open angle.
  • the eccentric orbiting motion of the orbiting scroll 12 proceeds, After the merging of the second chamber 9b and the innermost chamber 9a at the communication angle, the extraction hole 112 opens in the innermost chamber 9a.
  • the bleed hole 112 opens to the second chamber when the seal forming point passes through the bleed hole position.
  • the outermost chamber 9c that is approaching is opened, and then the outermost chamber 9c is opened through the second chamber 9b to the innermost chamber 9a. After that, the operation of opening the outermost chamber 9c approaching next is repeated.
  • the bleeding hole 112 is always open to one of the compression chambers 9, that is, the intermediate pressure compression chamber 37 during one eccentric rotation of the orbiting scroll 12, and supplies the pressure in the compression chamber 9 to the back pressure chamber 291b described later. According to FIG. 2, the bleed hole 112 is blocked by the oscillating spiral teeth 12b, and strictly speaking, there is a time during which it does not open to the compression chamber 9, but the time during which it does not open is small, and it is substantially always It opens to the compression chamber 9.
  • the built-in volume ratio that is, (suction completion volume)/(volume of the second chamber when the communication angle is reached) is determined by determining the spiral specifications.
  • the orbiting scroll 12 makes one rotation eccentric orbital motion and reaches the suction completion angle again to reach the suction completion angle 9c.
  • the orbiting scroll 12 Becomes the second chamber 9b, and the orbiting scroll 12 further eccentrically orbits to reach the communication angle, whereby the second chamber 9b joins the innermost chamber 9a.
  • the compression chamber 9 has high operating conditions. The compression takes place regardless of the low pressure.
  • the compression ratio or pressure ratio is an index showing how much a certain compression chamber has been compressed from the time when suction is completed, focusing on the pressure increase resulting from the volume reduction. It depends on the amount. It is more rational to define the spiral volume as a built-in volume ratio.
  • the built-in volume ratio is a fixed value. Therefore, under operating conditions where the pressure difference between the suction pressure and the discharge pressure is relatively small, for example, overcompression occurs in which the refrigerant is compressed too much by the compression mechanism section. That is, as described above, since the orbiting scroll makes one rotation eccentric orbital movement from the suction completion angle and further continues to be compressed in the compression chamber until the communication angle is reached, when compression is performed up to the built-in volume ratio, When the pressure in the compression chamber exceeds the high pressure, a loss due to excessive pressure increase, so-called overcompression loss occurs.
  • One of the means is a so-called relief mechanism that discharges from the compression chamber before reaching the communication angle to the high pressure side, that is, performs high pressure bypass.
  • a relief port 295 and a relief valve 26, which will be described later, are used as the relief mechanism. Etc. are provided.
  • FIG. 3 is a schematic cross-sectional view of essential parts of the scroll compressor according to Embodiment 1 of the present invention when it is unloaded.
  • FIG. 4 is an enlarged schematic view of the unload mechanism during unloading of the scroll compressor according to the first embodiment of the present invention.
  • FIG. 5 is a schematic cross-sectional view of a main part of the scroll compressor according to the first embodiment of the present invention when it is not unloaded.
  • FIG. 6 is an enlarged schematic view of the unload mechanism of the scroll compressor according to the first embodiment of the present invention when it is not unloading.
  • a back pressure chamber 291b is formed between the separator 29 and the end surface of the fixed scroll 11 opposite to the orbiting scroll 12.
  • the back pressure chamber 291b is formed of an annular recess formed on the surface of the separator 29 on the low pressure space 212 side.
  • An annular seal member 33 is arranged in the groove of the inner peripheral surface 118 of the back pressure chamber 291b.
  • An annular seal member 34 is arranged in the groove of the outer peripheral surface 119 of the back pressure chamber 291b.
  • the discharge chamber 291a communicates with the first discharge port 111, and a high pressure is generated by the fluid discharged from the first discharge port 111.
  • the back pressure chamber 291b communicates with the compression chamber 9 in the middle of compression, that is, the intermediate pressure compression chamber 37 through the extraction hole 112 formed in the fixed scroll 11, and has an intermediate pressure.
  • the separator 29 is provided with a relief port 295, a relief valve 26, and a relief valve stopper 26b for limiting the lift amount of the relief valve 26 as a relief mechanism 220 for performing overcompression relief.
  • the relief port 295 has an inlet side opening to the back pressure chamber 291b and an outlet side opening to the high pressure space 211.
  • the relief valve 26 and the relief valve stopper 26b are provided on the outlet side of the relief port 295.
  • the spiral tooth tips may come into contact with the opposite base plate of the scroll on the opposite side due to deformation and thermal expansion of the spiral teeth or the base plate during operation. May interfere. In the end, there is a possibility that seizure of the spiral tooth tip or seizure of the mating base plate may occur eventually. Had to set.
  • the tooth clearance set at the time of assembly is a factor for reducing the efficiency of the compressor because it serves as a fluid leakage path.
  • the intermediate pressure is introduced into the back pressure chamber 291b and the discharge pressure is introduced into the discharge chamber 291a, thereby applying an axial force to the fixed scroll 11.
  • the structure is such that it is pressed against the orbiting scroll 12. Since the so-called axial compliant system is adopted, it is not necessary to set the tooth tip clearance during assembly in advance. As a result, the tooth tip clearance can be minimized and the leakage loss can be reduced.
  • the separator 29 is further equipped with an unload mechanism 230 that switches between unloading which limits the discharge amount of the scroll compressor 1 by bypassing the fluid from the compression chamber 9 to the low pressure side and full load with a discharge amount of 100%. ing.
  • full load may be referred to as non-unload.
  • the unload mechanism 230 has a spool-shaped control valve 31 and an elastic body 32 such as a spring arranged in an unload hole 296 formed in the separator 29 in the radial direction.
  • a convex portion 29a that prevents the control valve 31 from closing the high-pressure introducing hole 294a is formed at the radially inner end of the unload hole 296.
  • the radially outer end of the unload hole 296 is closed by a plug 35c.
  • the unloading mechanism 230 bypasses the fluid in the intermediate pressure compression chamber 37 into the low pressure space 212 via the extraction hole 112, the back pressure chamber 291b, and the unloading path formed in the separator 29, Unload.
  • the unload path includes a back pressure chamber communication passage 293a whose one end opens in the back pressure chamber 291b, a low pressure space communication passage 293b whose one end opens in the low pressure space 212, and a control valve small diameter portion outer peripheral space 293c in the unload hole 296. Composed of and.
  • the control valve 31 is slidably arranged in the unload hole 296, and by sliding in the unload hole 296, the position of the control valve small diameter portion outer peripheral space 293c in the unload hole 296 is moved. That is, the control valve 31 moves to a position (FIG. 4) in which the back pressure chamber communication passage 293a opens with respect to the control valve small diameter portion outer peripheral space 293c and a closed position (FIG. 6) to open and close the unloading path, Switch between unloading and non-unloading.
  • the separator 29 is formed with a high-pressure introduction hole 294a and a low-pressure introduction hole 294b which open to the unload hole 296.
  • One end of the high-pressure introduction hole 294a is opened to the high-pressure space 211 and the other end is opened to the unload hole 296, so that the high-pressure fluid in the high-pressure space 211 flows through the unload hole 296 at one end surface 31a in the moving direction of the control valve 31.
  • the low-pressure introduction hole 294b has one end opened to the unload hole 296 and the other end opened to the low-pressure space 212, so that the low-pressure fluid in the low-pressure space 212 flows through the unload hole 296 at the other end surface 31b in the moving direction of the control valve 31. It is introduced into the low pressure introduction space 297 on the side.
  • the elastic body 32 is arranged in the low pressure introduction space 297 on the other end surface 31b side of the control valve 31, and urges the control valve 31 to the high pressure side (right side in FIG. 6).
  • the control valve 31 is pressed to the high pressure side by the urging force of the elastic body 32, and one end surface 31a is in contact with the convex portion 29a.
  • the control valve 31 opens the unloading path including the back pressure chamber communication passage 293a, the control valve small diameter outer peripheral space 293c, and the low pressure space communication passage 293b.
  • the elastic body 32 When the operating condition of the scroll compressor 1 is such that the high/low pressure difference is equal to or less than the set value, the elastic body 32 is higher than the differential pressure between the high pressure acting on one end face 31a of the control valve 31 and the low pressure acting on the other end face 31b. The elastic force due to exceeds.
  • the control valve 31 is pressed in the direction of the end surface 31a, and as shown in FIGS. 3 and 4, one end surface 31a of the control valve 31 moves to a position where it comes into contact with the convex portion 29a and then stops.
  • the passage 293a and the control valve small diameter portion outer peripheral space 293c communicate with each other.
  • the unloading path including the back pressure chamber communication passage 293a, the control valve small-diameter portion outer peripheral space 293c, and the low pressure space communication passage 293b is opened.
  • the fluid in the intermediate pressure compression chamber 37 passes through the bleed hole 112, the back pressure chamber 291b, the back pressure chamber communication passage 293a, the control valve small-diameter portion outer peripheral space 293c, and the low pressure space communication passage 293b in this order, and then the low pressure space 212. Is discharged to.
  • the intermediate pressure compression chamber 37 communicates with the extraction hole 112, in other words, until the outer peripheral side seal forming point of the intermediate pressure compression chamber 37 passes through the extraction hole 112, the intermediate pressure compression chamber 37 The compression is not performed and the capacity is controlled, that is, the unload state is set.
  • the differential pressure between the high pressure acting on one end face 31a of the control valve 31 and the low pressure acting on the other end face 31b is equal to the elastic body 32. Exceeds the elastic force.
  • the control valve 31 slides toward the end surface 31b, and the back pressure chamber communication passage 293a is closed by the control valve 31.
  • the unloading path including the back pressure chamber communication passage 293a, the control valve small diameter portion outer peripheral space 293c, and the low pressure space communication passage 293b is closed, and the unloading state is switched to the non-unloading state.
  • the unloading mechanism 230 changes the pressure acting on the one end surface 31a and the other end surface 31b of the control valve 31 in accordance with the operating conditions of the scroll compressor 1, so that the control valve 31 automatically operates. Move and automatically switch between unloading and non-unloading.
  • the above set value which is the switching point between unloading and non-unloading, can be adjusted to a desired value by selecting the spring constant of the elastic body 32 in consideration of the pressure acting on both end surfaces of the control valve 31. Is possible.
  • the unloading mechanism 230 guides high and low pressures acting on both end surfaces of the control valve 31 from inside the closed container 21, it has a structure completed inside the closed container 21, and from the outside of the closed container 21 to the compression mechanism section 10. No need for connecting pipes.
  • the fixed scroll 11 receives the pressures of the discharge chamber 291a and the back pressure chamber 291b, and its planar position and posture are regulated by a plurality of radial guide members 28 (see FIG. 2) arranged on the outer circumference of the fixed scroll 11. , Is pressed in the axial direction toward the orbiting scroll 12 against the pressure in the compression chamber 9.
  • the control valve 31 During operation under the condition that the high/low pressure difference is small, as described above, in the unload mechanism 230, the control valve 31 has the unload path including the back pressure chamber communication passage 293a, the control valve small diameter outer peripheral space 293c, and the low pressure space communication passage 293b. Open. As a result, the fluid in the intermediate pressure compression chamber 37 is discharged into the low pressure space 212 via the bleed hole 112, the back pressure chamber 291b, the unloading path, etc., and becomes in the unloading state.
  • the outermost chamber 9c that is, the intermediate pressure compression chamber 37, performs a compression action that is not necessarily required.
  • this is a region in which the pressure increase width with respect to the volume change immediately after the completion of inhalation is small, so the performance deterioration is limited, and there is no practical problem.
  • the control valve 31 in the unload mechanism 230 includes the back pressure chamber communication passage 293a, the control valve small diameter outer peripheral space 293c, and the low pressure space communication passage 293b as described above.
  • the load path is closed and the unload state is entered.
  • the relief valve 26 is lifted against its elastic force. If the pressure in the second chamber 9b, which is the intermediate pressure compression chamber 37, exceeds the discharge pressure before the orbiting scroll 12 makes one rotation eccentric orbital movement from the suction completion angle and further reaches the communication angle, the relief valve is released. 26 is lifted against its elastic force. Accordingly, the fluid in the back pressure chamber 291b is relieved from the relief port 295 into the high pressure space 211, and the overcompression loss is reduced.
  • the fluid is not discharged directly from the compression chamber 9 to the high pressure space 211 or the low pressure space 212, but is discharged via the back pressure chamber 291b.
  • the back pressure chamber 291b and the flow passages before and after it serve as a buffer.
  • the substantial suction completion of the compression chamber 9 in which the extraction hole 112 is opened is the timing at which the extraction hole 112 does not open. Therefore, the pressure of the pressure rising portion of the compression chamber 9 at the time of unloading and the planar projected area of the compression chamber 9 which is the pressure receiving area thereof are smaller than those at the time of unloading. Therefore, at the time of unloading, the force that pushes the fixed scroll 11 upward in the axial direction to separate it from the orbiting scroll 12 is smaller than that at the time of non-unloading. Therefore, it is necessary to reduce the back pressure during unloading than during non-unloading so that the axially downward force acting on the fixed scroll 11 does not become excessive as compared with the axially upward force.
  • the back pressure chamber 291b is unloaded for some reason while the intermediate pressure remains, the back pressure for pressing the fixed scroll 11 against the orbiting scroll 12 will not decrease.
  • the pressing force of the axial compliant that is, the downward force in the axial direction becomes excessive, which may cause a problem such as an increase in sliding loss and seizure of the tooth tips.
  • the unloading and the pressure release of the back pressure chamber 291b are performed by the same element, that is, the control valve 31, the unloading does not occur when the intermediate pressure remains in the back pressure chamber 291b. It is possible to avoid such a problem.
  • the unload hole 296 is formed in the separator 29, and the unload mechanism 230 that opens and closes the unload path by moving the control valve 31 in the unload hole 296.
  • the unload mechanism 230 that opens and closes the unload path by moving the control valve 31 in the unload hole 296.
  • the low pressure and the high pressure applied to both end surfaces of the control valve 31 to move the position of the control valve 31 are guided from inside the closed container 21, and the structure related to unloading is completed inside the closed container 21. Therefore, the unloading can be performed without connecting the outside of the closed container 21 to the compression mechanism unit 10 by piping. Therefore, it is not necessary to connect the compression mechanism unit 10 to the pipe outside the closed container 21 or to provide the pipe with valves as in the conventional case, and the cost can be reduced.
  • switching between unloading and non-unloading is automatically switched according to operating conditions. That is, the transition from non-unload to unload and the return from unload to non-unload are automatically performed. Therefore, it is possible to avoid an increase in cost due to the pipe connection for the switching operation from the outside, and the operation of the switching valve or the like is unnecessary. As a result, the scroll compressor 1 having a wide capacity and high efficiency can be obtained.
  • control valve 31 closes the unload path when the high/low pressure difference exceeds a preset value, and opens the unload path when the high/low pressure difference is less than or equal to the preset value. In this way, unloading and non-unloading can be switched according to the high/low pressure difference.
  • the unload mechanism 230 includes the elastic body 32 that urges the control valve 31 to the high pressure side to position the control valve 31 at the position where the unload path is opened.
  • the control valve 31 moves from the position where the unloading path is opened to the position where the unloading path is closed when the differential pressure corresponding to the high/low pressure difference that changes according to the operating conditions exceeds the biasing force of the elastic body 32.
  • the unload hole 296 is formed in the separator 29.
  • the unloading path includes a back pressure chamber communication passage 293a having one end opened to the back pressure chamber 291b, a low pressure space communication passage 293b having one end opened to the low pressure space 212, and a control valve small diameter portion outer peripheral space 293c. ..
  • a low pressure introduction hole 294b for introducing the low pressure of the low pressure space 212 into a space facing one end surface 31b of the control valve 31 and a high pressure space of the high pressure space 211 in a space facing the other end surface 31a of the control valve 31.
  • a high pressure introducing hole 294a for introducing With this structure, high pressure and low pressure can be applied to both end surfaces of the control valve 31 from inside the closed container 21.
  • the relief port 295 and the unloading path are formed in the separator 29, and each communicates with the back pressure chamber 291b, and the back pressure chamber 291b passes through the bleed hole 112 provided in the fixed scroll 11. And communicates with the intermediate pressure compression chamber 37.
  • the bleed hole 112 is the only port opened to the compression chamber 9 in both overcompression relief and unloading. Is. Therefore, the number of ports opened to the compression chamber 9 can be minimized as compared with the conventional configuration in which an independent port is required for each of the overcompression relief and the unload.
  • the pressure in the discharge chamber 291a and the back pressure chamber 291b presses the fixed scroll 11 toward the oscillating scroll 12 to minimize the tooth gap, thereby improving the compression efficiency. ..
  • control valve 31 closes the back pressure chamber communication passage 293a to close the unload path including the back pressure chamber communication passage 293a, the control valve small diameter outer peripheral space 293c, and the low pressure space communication passage 293b.
  • the unloading path may be closed by closing the low pressure space communication passage 293b.
  • Embodiment 2 Although the unload hole 296 is formed in the separator 29 in the first embodiment, the unload hole 117 is formed in the fixed scroll 11 in the second embodiment.
  • the points of difference between the second embodiment and the first embodiment will be mainly described.
  • FIG. 7 is a schematic vertical sectional view of a scroll compressor according to the second embodiment of the present invention.
  • FIG. 8 is a schematic sectional view of essential parts of a scroll compressor according to Embodiment 2 of the present invention. The portion surrounded by the dotted line in FIG. 8 corresponds to the unload mechanism 230.
  • FIG. 9 is an enlarged schematic view of an unload mechanism during unloading of the scroll compressor according to the second embodiment of the present invention.
  • FIG. 10 is an enlarged schematic view of the unload mechanism of the scroll compressor according to the second embodiment of the present invention when it is not unloading. 8 to 10, the arrows shown in the operating pressure introducing lateral hole 124 and the pressure receiving pocket 115 indicate the direction of hydraulic pressure.
  • FIG. 11 is a view of the fixed scroll of FIG. 7 viewed from the spiral side.
  • FIG. 12 is a view of the fixed scroll of FIG. 7 viewed from the side opposite to the spiral.
  • FIG. 13 is a view of the orbiting scroll of FIG. 7 viewed from the spiral side.
  • FIG. 14 is a view of the orbiting scroll of FIG. 7 viewed from the side opposite to the spiral.
  • FIG. 15 is a plan view showing a spiral combined state when the scroll compressor according to the second embodiment of the present invention is unloaded.
  • FIG. 16 is an enlarged shape view of the unload mechanism of FIG.
  • FIG. 17 is a shape view of the control valve of the unload mechanism of FIG. 7.
  • FIG. 18 is a shape view of the spring seat 36 of the unload mechanism of FIG. 7.
  • FIG. 19 is a shape view of the plug of the unload mechanism of FIG. 7.
  • FIG. 20 is a plan view showing a spiral combined state when the scroll compressor according to the second embodiment of the present invention is not unloaded.
  • 21 is an enlarged shape view of the unload mechanism of FIG.
  • the spool-shaped control valve 31, the elastic body 32 such as a spring, and the spring seat 36 are formed in the fixed base plate 11 a of the fixed scroll 11 and the unload hole 117 is formed. It is located in.
  • the unload hole 117 is formed from the outer periphery of the fixed base plate 11a of the fixed scroll 11 so as to pass through the fixed base plate 11a without passing through the spiral center.
  • one end side of the unload hole 117 is closed by a plug 35a, and the other end side is closed by a spring seat 36.
  • the unload mechanism 230 causes the fluid in the intermediate pressure compression chamber 37 to flow through the bleed hole 112, the back pressure chamber 291b, and the unload path configured in the unload hole 117 formed in the fixed base plate 11a. Unloading is performed by bypassing the low-pressure space 212.
  • the unload path includes a back pressure chamber communication passage 113 having one end opened to the back pressure chamber 291b, a low pressure space communication passage 114 having one end opened to the low pressure space 212, and the other end of the back pressure chamber communication passage 113 to the low pressure space communication passage 113. It is composed of a control valve small diameter portion outer peripheral space 120 communicating with the other end of the passage 114.
  • the control valve small-diameter portion outer peripheral space 120 is a part of the unload hole 117.
  • the control valve 31 is slidably arranged in the unload hole 117, and an elastic body 32 arranged between the one end face 31a and the spring seat 36 causes the control valve 31 to move toward the plug 35a of the unload hole 117 (left side in FIG. 16). ) Is pressed. As a result, the control valve 31 is arranged in the unload hole 117 with the other end surface 31b in contact with the tip of the plug 35a. As shown in FIGS. 16 and 19, the plug 35a has a tip portion formed to have a smaller diameter than the closing portion of the unload hole 117 at the rear, and closes an operation pressure introducing hole 116, which will be described later, formed in the fixed scroll 11. It is supposed to not. 7 to 9, the shape and the like of the plug 35a is different from the above description, but FIGS. 7 to 9 are schematic views, and the shape shown in FIG. 19 is also an example of a specific shape.
  • the spring seat 36 has a tip portion formed to have a diameter smaller than the diameter of the unload hole 117, and the elastic body 32 is inserted between the outer periphery of the small diameter portion and the inner surface of the unload hole 117.
  • a hole 36a for equalizing pressure penetrates through the center of the spring seat 36.
  • the fixed base plate 11a and the fixed spiral tooth 11b of the fixed scroll 11 are formed with an operation pressure introducing hole 116 penetrating in the standing direction of the fixed spiral tooth 11b.
  • One end of the operating pressure introducing hole 116 opens to the unloading hole 117 in the operating pressure introducing space 298 facing the end surface 31b of the control valve 31 on the plug 35a side.
  • the other end of the operation pressure introducing hole 116 opens into a circular concave pressure receiving pocket 115 formed on the tooth crest surface of the fixed spiral tooth 11b.
  • the diameter of the pressure receiving pocket 115 is set to a diameter that can include the swing locus of the operation pressure introducing vertical hole 125 described later, and the pressure receiving pocket 115 is always in communication with the operation pressure introducing vertical hole 125.
  • the rocking base plate 12 a of the rocking scroll 12 has an operating pressure introducing lateral hole 124 for guiding the hydraulic pressure from the boss portion 121 of the rocking scroll 12 to the pressure receiving pocket 115 of the fixed scroll 11. Also, an operating pressure introducing vertical hole 125 is formed.
  • the operating pressure introducing lateral hole 124 is a lateral hole in the plane direction of the rocking base plate 12a
  • the operating pressure introducing vertical hole 125 is a vertical hole extending vertically from the operating pressure introducing lateral hole 124 and opening on the upper surface of the rocking base plate 12a. is there.
  • the rotation of the shaft 15 drives the oil supply pump 27 to move the lubricating oil 22 up through the oil supply hole 152 and be supplied to the inside of the upper portion of the boss 121.
  • the lubricating oil 22 supplied to the boss portion 121 is supplied to the unload hole 117 via the operating pressure introducing lateral hole 124, the operating pressure introducing vertical hole 125, the pressure receiving pocket 115, and the operating pressure introducing hole 116.
  • the hydraulic pressure according to the resistance from the upper part inside the boss 121 of the orbiting scroll 12 to the downstream side and the pump pressure of the oil supply pump 27 acts on the end surface 31b of the control valve 31 on the operating pressure introducing space 298 side.
  • a low pressure is constantly acting on the end surface 31a of the control valve 31 opposite to the operation pressure introducing space 298. This is because the space facing the end surface 31a of the control valve 31 is pressure-equalized with the low-pressure space 212 by the pores 36a formed in the spring seat 36.
  • the scroll compressor 1 When the scroll compressor 1 is operated at a relatively low speed, that is, when the rotation speed of the shaft 15 is less than or equal to the set rotation speed, the oil supply amount of the oil supply pump 27 is small and the oil supply pressure is low. Therefore, the force derived from the acting pressure to the end surface 31a opposite to the operation pressure introducing space 298 and the elastic force of the elastic body 32 are smaller than the force derived from the acting pressure to the end surface 31b of the control valve 31 on the operating pressure introducing space 298 side. Is more than the total. In this case, as shown in FIGS. 15 and 16, the control valve 31 moves to the plug 35a side and contacts the tip of the plug 35a. As a result, as shown in FIG. 9, the back pressure chamber communication passage 113, the control valve small diameter portion outer peripheral space 120, and the low pressure space communication passage 114 communicate with each other, and the unloading passage is opened.
  • the fluid in the intermediate pressure compression chamber 37 passes through the extraction hole 112, the back pressure chamber 291b, the back pressure chamber communication passage 113, the control valve small-diameter portion outer peripheral space 120, and the low pressure space communication passage 114 in this order, and the low pressure space 212. Is discharged to. Therefore, while the intermediate pressure compression chamber 37 communicates with the extraction hole 112, in other words, until the outer peripheral side seal forming point of the intermediate pressure compression chamber 37 passes through the extraction hole 112, the intermediate pressure compression chamber 37 The compression is not performed and the capacity is controlled, that is, the unload state is set.
  • the force derived from the acting pressure on the end surface 31b of the control valve 31 on the operating pressure introducing space 298 side is the force derived from the acting pressure on the end surface 31a on the side opposite to the operating pressure introducing space 298 and the elastic force of the elastic body 32.
  • the control valve 31 moves away from the plug 35a in the direction of compressing the elastic body 32, and as shown in FIG. Blocked by 31.
  • the unloading path formed by the back pressure chamber communication passage 113, the control valve small diameter portion outer peripheral space 120 and the low pressure space communication passage 114 is closed, and the unloading state is switched to the unloading state.
  • the pressure acting on both end surfaces of the control valve 31 changes according to the operating speed of the scroll compressor 1, so that the control valve 31 automatically moves and the unloading and non-loading operations are performed. Automatically switch between unload and.
  • the set rotational speed which is a switching point between unloading and non-unloading, is adjusted to a desired value by selecting the spring constant of the elastic body 32 in consideration of the pressure acting on both end surfaces of the control valve 31. It is possible.
  • the unload mechanism 230 guides, from the inside of the closed container 21, the hydraulic pressure that is the low pressure and the operating pressure applied to the one end surface 31 a and the other end surface 31 b of the control valve 31.
  • the unloading mechanism 230 has a structure that is completed inside the closed container 21, and does not require piping or the like that connects the outside of the closed container 21 to the compression mechanism unit 10.
  • the reduction of the leakage loss of the tooth tip clearance due to the axial pressing and the reduction of the overcompression loss under the low compression ratio condition by the high pressure side relief can be achieved. You can get the effect.
  • the capacity control by the unloading mechanism completed in the closed container, the configuration with the minimum number of ports opening to the compression chamber, the pressure fluctuation in the compression chamber, and the like can be realized because the pulsations on the relief side and the unload side do not affect each other.
  • the unloading and the pressure release of the back pressure chamber are performed by the operation of the single element of the control valve, which is highly reliable, has a wide operating range, and has a high operating range.
  • An efficient scroll compressor can be obtained at low cost.
  • the capacity control can be used in a wider range as compared with the first embodiment.
  • the high/low pressure depends on the temperature difference between the high temperature heat source and the low temperature heat source of the refrigeration cycle, when the small temperature difference and the air conditioning load decrease are correlated as in the partial load condition described above, the high/low pressure difference of the first embodiment is used. This is effective for a mechanism that shifts to unload operation depending on the dependency. On the other hand, for example, in a system including one outdoor unit and many indoor units, it may be better to unload regardless of the high/low pressure difference. When performing cooling operation of only one indoor unit when the outdoor temperature is high, the high/low pressure difference depending on the indoor/outdoor temperature difference is large, and the air conditioning load is smaller than the outdoor unit capacity due to the decrease in the number of operating indoor units. Therefore, it is desirable to unload.
  • the compressor will operate at low speed, resulting in a decrease in performance due to increased leakage loss as described above.
  • the load for example, bearing load
  • the load derived from the differential pressure that acts on each member of the compression mechanism does not become small. Therefore, in order to avoid the seizure of the bearing due to the low speed high differential pressure operation, etc. Low speed operation beyond the limit cannot be performed. That is, there are operating conditions in which the unloading mechanism that starts depending on the differential pressure is not effective.
  • the scroll compressor 1 includes an oil supply pump 27 at the lower end of the shaft 15.
  • the oil supply pump 27 supplies the lubricating oil 22 stored in the lower portion of the closed container 21 to the compression mechanism unit 10 through the oil supply hole 152 provided through the shaft 15.
  • the oil pressure of the lubricating oil 22 supplied from the oil supply pump 27 acts on the end surface 31b of the control valve 31 on the operating pressure introducing space 298 side.
  • the low pressure of the low pressure space acts on the end surface 31a of the control valve 31 on the side opposite to the operation pressure introducing space 298.
  • control valve 31 closes the unloading path when the rotation speed of the shaft 15 exceeds a preset setting rotation speed, and opens the unloading path when the rotation speed is less than or equal to the setting rotation speed. To do. In this way, unloading and non-unloading can be switched according to the rotation speed of the shaft 15.
  • the unload hole 117 is formed in the fixed scroll 11.
  • the unloading path is composed of a back pressure chamber communication passage 113 having one end opening to the back pressure chamber 291b, a low pressure space communication passage 114 having one end opening to the low pressure space 212, and a control valve small diameter outer peripheral space 120. ..
  • a pore 36a for introducing the low pressure of the low pressure space 212 is formed on the end surface 31a side of the control valve 31, which is the counter operation pressure introducing space side.
  • the fixed scroll 11 is formed with a pressure receiving pocket 115 and an operation pressure introducing hole 116 which are operation pressure introducing paths for supplying hydraulic pressure from the oil supply pump 27 to the operation pressure introducing space 298 on the end surface 31b side of the control valve 31. ing.
  • a low pressure and an operating pressure can be applied to both end faces of the control valve 31 from the inside of the closed container 21.
  • the low pressure space communication passage 114 is closed by the control valve 31 to close the unloading passage including the back pressure chamber communication passage 113, the control valve small diameter outer peripheral space 120, and the low pressure space communication passage 114.
  • the unloading path may be closed by closing the back pressure chamber communication passage 113.

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Abstract

This scroll compressor is provided with an unload mechanism for performing an unload operation in which discharge rate is limited by feeding a fluid through a bypass from a compression chamber to a low-pressure space. Formed in a separator or a fixed scroll is an unload passageway that connects the low-pressure space and a back-pressure chamber which is connected with the compression chamber in midcourse of a compression process. The unload mechanism is provided with a control valve that closes and opens the unload passageway. During operation, a low pressure from the low-pressure space is exerted on one of the end faces of the control valve in the moving direction thereof, while a pressure higher than that in the low-pressure space, and derived from within a sealed container, acts on the other end face of the control valve. By a change in the difference between the pressures acting on the two end faces of the control valve depending on the operating conditions, the control valve is moved so as to cause the unload passageway to be opened or closed.

Description

スクロール圧縮機Scroll compressor
　本発明は冷凍又は空調用途等に用いられるスクロール圧縮機に関する。 The present invention relates to a scroll compressor used for refrigeration or air conditioning.
　広い容量範囲で用いるために、圧縮室内の圧縮ガスを吸込側に戻すバイパス穴を有する容量制御型のスクロール圧縮機がある。この種のスクロール圧縮機では、バイパス穴をバイパス弁で開閉することで、吐出量が１００％のフルロードと、吐出量が低減されたアンロードとに運転状態を切り替えるようにしている。 There is a capacity-controlled scroll compressor that has a bypass hole that returns the compressed gas in the compression chamber to the suction side for use in a wide capacity range. In this type of scroll compressor, the operating state is switched between full load with a discharge amount of 100% and unload with a reduced discharge amount by opening and closing the bypass hole with a bypass valve.
　スクロール圧縮機では、固定値の組込容積比が存在するため、高低圧差が比較的小さい運転条件では、圧縮機構で流体を圧縮し過ぎる、所謂過圧縮が発生する場合がある。このため、圧縮室に開口するリリーフポートを設け、リリーフポートから圧縮室内の圧縮ガスを吐出側に逃す、所謂高圧バイパスによる過圧縮リリーフを行うことで、過圧縮を防止するものがある（例えば、特許文献１参照）。 In scroll compressors, there is a fixed volume ratio, so under operating conditions where the high-low pressure difference is relatively small, the compression mechanism may cause excessive compression of the fluid, which is called overcompression. Therefore, by providing a relief port that opens in the compression chamber and letting the compressed gas in the compression chamber escape to the discharge side from the relief port, there is one that prevents overcompression by performing so-called high-pressure bypass overcompression relief (for example, See Patent Document 1).
特開２０００－０１８１８２号公報Japanese Patent Laid-Open No. 2000-018182
　特許文献１において高圧バイパスによる過圧縮リリーフを行うためのリリーフ機構は、固定スクロールに設けたリリーフポートとリリーフ弁であり、密閉容器内で完結している。しかし、低圧バイパスによるアンロードを行うアンロード機構は、密閉容器に貫通して配管を設け、配管と圧縮機構部とを接続する必要があると共に、更に弁類も備える必要のある構成となっており、コスト増大が避けられなかった。 In Patent Document 1, the relief mechanism for performing overcompression relief by high-pressure bypass is a relief port and a relief valve provided in the fixed scroll, which is completed in a closed container. However, the unloading mechanism that performs unloading by low-pressure bypass requires a pipe that penetrates the closed container to connect the pipe and the compression mechanism portion, and also needs to include valves. However, an increase in cost was unavoidable.
　本発明はこのような点を鑑みなされたもので、低圧バイパスによるアンロードを密閉容器外から圧縮機構部へ配管接続することなく行うことが可能なスクロール圧縮機を得ることを目的とする。 The present invention has been made in view of the above circumstances, and an object thereof is to obtain a scroll compressor capable of performing unloading by low-pressure bypass without connecting a pipe from the outside of the closed container to the compression mechanism section.
　本発明のスクロール圧縮機は、密閉容器と、密閉容器内を高圧空間と低圧空間とに区画するセパレータと、固定スクロール及び揺動スクロールを有し、固定スクロール及び揺動スクロールを噛み合わせて形成された圧縮室に、低圧空間から流体を吸入して圧縮し、高圧空間に吐出する圧縮機構部と、圧縮室内から低圧空間へ流体をバイパスすることにより、吐出量を制限するアンロードを行うアンロード機構とを備え、固定スクロールの揺動スクロールとは反対側の端面とセパレータとの間には、固定スクロールに形成された抽気孔を介して、圧縮途中の圧縮室に連通する背圧室が形成され、セパレータ又は固定スクロールに形成されたアンロード孔内及びその前後に、背圧室連通路、制御弁小径部外周空間、低圧空間連通路からなる背圧室と低圧空間とを連通するアンロード経路が構成されており、アンロード機構は、アンロード孔内での位置が移動することでアンロード経路を開閉する制御弁を備え、運転中、制御弁の移動方向の一方の端面に低圧空間の低圧が作用すると共に、他方の端面に密閉容器内から導かれて低圧空間よりも高い圧力が作用し、運転条件に応じて、制御弁の両端面の差圧が変化することで制御弁が移動してアンロード経路を開閉するものである。 The scroll compressor of the present invention has a closed container, a separator that divides the closed container into a high-pressure space and a low-pressure space, a fixed scroll and an orbiting scroll, and is formed by engaging the fixed scroll and the orbiting scroll. The compression mechanism that sucks fluid from the low-pressure space into the compression chamber and compresses it, and discharges it to the high-pressure space, and the unloading that limits the discharge amount by bypassing the fluid from the compression chamber to the low-pressure space. A back pressure chamber communicating with the compression chamber in the middle of compression is formed between the separator and the end surface of the fixed scroll on the side opposite to the oscillating scroll, and through the extraction hole formed in the fixed scroll. In the unload hole formed in the separator or the fixed scroll, and before and after the unload hole, an unload that connects the back pressure chamber including the back pressure chamber communication passage, the control valve small diameter outer peripheral space, and the low pressure space communication passage to the low pressure space. The unloading mechanism is equipped with a control valve that opens and closes the unloading path by moving the position in the unloading hole, and during operation, the low pressure space is provided on one end face in the moving direction of the control valve. The low pressure of the control valve acts on the other end surface of the control valve, which is guided from the closed container to a pressure higher than that of the low pressure space, and the pressure difference between the two end surfaces of the control valve changes according to the operating conditions. It moves to open and close the unloading path.
　本発明によれば、圧縮室内から低圧空間へ流体をバイパスすることにより、吐出量を制限するアンロードを、アンロードに係る構造が密閉容器内で完結し、密閉容器外から圧縮機構部へ配管接続することなく行うことができる。 According to the present invention, by bypassing the fluid from the compression chamber to the low-pressure space, the unloading that restricts the discharge amount is completed in the closed container, and the piping from the closed container to the compression mechanism part is completed. It can be done without a connection.
本発明の実施の形態１によるスクロール圧縮機の縦断面模式図である。1 is a schematic vertical sectional view of a scroll compressor according to Embodiment 1 of the present invention. 図１のスクロール圧縮機の揺動スクロールの偏心旋回に伴う圧縮行程を示す図である。It is a figure which shows the compression process accompanying the eccentric rotation of the orbiting scroll of the scroll compressor of FIG. 本発明の実施の形態１によるスクロール圧縮機のアンロード時の要部断面模式図である。FIG. 3 is a schematic cross-sectional view of essential parts of the scroll compressor according to Embodiment 1 of the present invention when it is unloaded. 本発明の実施の形態１によるスクロール圧縮機のアンロード時のアンロード機構部の拡大模式図である。FIG. 3 is an enlarged schematic diagram of an unload mechanism section during unloading of the scroll compressor according to the first embodiment of the present invention. 本発明の実施の形態１によるスクロール圧縮機の非アンロード時の要部断面模式図である。FIG. 3 is a schematic cross-sectional view of a main part of the scroll compressor according to Embodiment 1 of the present invention when it is not unloaded. 本発明の実施の形態１によるスクロール圧縮機の非アンロード時のアンロード機構部の拡大模式図である。FIG. 3 is an enlarged schematic diagram of an unload mechanism unit when the scroll compressor according to Embodiment 1 of the present invention is not unloading. 本発明の実施の形態２によるスクロール圧縮機の縦断面模式図である。FIG. 6 is a schematic vertical sectional view of a scroll compressor according to Embodiment 2 of the present invention. 本発明の実施の形態２によるスクロール圧縮機の要部断面模式図である。FIG. 6 is a schematic cross-sectional view of a main part of a scroll compressor according to Embodiment 2 of the present invention. 本発明の実施の形態２によるスクロール圧縮機のアンロード時のアンロード機構部の拡大模式図である。FIG. 9 is an enlarged schematic diagram of an unload mechanism section during unloading of the scroll compressor according to the second embodiment of the present invention. 本発明の実施の形態２によるスクロール圧縮機の非アンロード時のアンロード機構部の拡大模式図である。FIG. 9 is an enlarged schematic diagram of an unload mechanism section when a scroll compressor according to Embodiment 2 of the present invention is not unloaded. 図７の固定スクロールを渦巻側から見た図である。It is the figure which looked at the fixed scroll of FIG. 7 from the spiral side. 図７の固定スクロールを反渦巻側から見た図である。It is the figure which looked at the fixed scroll of FIG. 7 from the anti-spiral side. 図７の揺動スクロールを渦巻側から見た図である。It is the figure which looked at the orbiting scroll of FIG. 7 from the spiral side. 図７の揺動スクロールを反渦巻側から見た図である。It is the figure which looked at the orbiting scroll of FIG. 7 from the anti-spiral side. 本発明の実施の形態２によるスクロール圧縮機のアンロード時の渦巻組み合わせ状態を示す平面形状図である。FIG. 6 is a plan view showing a spiral combined state when a scroll compressor according to Embodiment 2 of the present invention is unloaded. 図１５のアンロード機構部の拡大形状図である。FIG. 16 is an enlarged shape view of the unload mechanism section of FIG. 15. 図７のアンロード機構部品である制御弁の形状図である。It is a shape figure of the control valve which is an unload mechanism part of Drawing 7. 図７のアンロード機構部品であるばね座の形状図である。It is a shape figure of the spring seat which is an unload mechanism part of FIG. 図７のアンロード機構部品であるプラグの形状図である。It is a shape figure of the plug which is an unload mechanism part of Drawing 7. 本発明の実施の形態２によるスクロール圧縮機の非アンロード時の渦巻組み合わせ状態を示す平面形状図である。FIG. 7 is a plan view showing a spiral combined state of the scroll compressor according to Embodiment 2 of the present invention when it is not unloaded. 図２０のアンロード機構部の拡大形状図である。It is an enlarged shape figure of the unloading mechanism part of FIG.
実施の形態１．
　図１は、本発明の実施の形態１によるスクロール圧縮機の縦断面模式図である。図１及び後述の各図において、同一の符号を付したものは、同一の又はこれに相当するものであり、これは明細書の全文において共通している。更に、明細書全文に表れている構成要素の形態は、あくまで例示であってこれらの記載に限定されるものではない。また、温度及び圧力の高低については、特に絶対的な値との関係で高低が定まっているものではなく、システム及び装置等における状態及び動作等において相対的に定まるものとする。また、模式図は、実施の形態の加工性及び組立性まで考慮した構造を忠実に提示するものではなく、構成をシンプルに説明するための簡易的なものである。 Embodiment 1.
1 is a schematic vertical sectional view of a scroll compressor according to a first embodiment of the present invention. In FIG. 1 and each of the drawings described later, the same reference numerals are the same or equivalent, and this is common to all the texts of the specification. Furthermore, the forms of the constituent elements appearing in the entire text of the specification are merely examples, and the present invention is not limited to these descriptions. Regarding the level of the temperature and the pressure, the level is not fixed particularly in relation to the absolute value, but is relatively set in the state and operation of the system and the device. Further, the schematic diagram does not faithfully present the structure in which the workability and the assemblability of the embodiment are taken into consideration, but is a simple one for simply explaining the configuration.
　このスクロール圧縮機１は、冷媒等の流体を吸入し、圧縮して高圧の状態として吐出させる機能を有し、外殻を構成する密閉容器２１の内部に、圧縮機構部１０、モータ１８及びその他の構成部品を収納する。圧縮機構部１０とモータ１８とは軸１５で連結されている。図１に示すように、密閉容器２１内において、圧縮機構部１０が上方に、モータ１８は圧縮機構部１０の下側に、それぞれ配置されている。密閉容器２１の下方は油溜めとなっており、潤滑油２２が貯留されている。 The scroll compressor 1 has a function of sucking a fluid such as a refrigerant, compressing the fluid, and discharging the fluid in a high-pressure state. Inside the closed container 21 that constitutes the outer shell, the compression mechanism section 10, the motor 18, and other components. Store the components of. The compression mechanism 10 and the motor 18 are connected by a shaft 15. As shown in FIG. 1, in the closed container 21, the compression mechanism portion 10 is arranged above, and the motor 18 is arranged below the compression mechanism portion 10. Below the closed container 21 is an oil sump, in which the lubricating oil 22 is stored.
　密閉容器２１の内部には、フレーム１４とサブフレーム１９とが配置されている。フレーム１４は、モータ１８の上側に配置されてモータ１８と圧縮機構部１０との間に位置している。サブフレーム１９は、モータ１８の下側に位置している。フレーム１４及びサブフレーム１９は、密閉容器２１に固着されている。フレーム１４の中央部には主軸受１４ａが設けられており、サブフレーム１９の中央部には副軸受１９ａが設けられている。主軸受１４ａ及び副軸受１９ａに軸１５が回転自在に支持されている。 The frame 14 and the sub-frame 19 are arranged inside the closed container 21. The frame 14 is disposed above the motor 18 and is located between the motor 18 and the compression mechanism unit 10. The sub-frame 19 is located below the motor 18. The frame 14 and the sub-frame 19 are fixed to a closed container 21. A main bearing 14a is provided at the center of the frame 14, and a sub bearing 19a is provided at the center of the sub-frame 19. A shaft 15 is rotatably supported by the main bearing 14a and the sub bearing 19a.
　密閉容器２１の内部を高圧空間２１１と低圧空間２１２とに区画するセパレータ２９が圧縮機構部１０の上側に配置されている。セパレータ２９よりも上方が高圧空間２１１、下方が低圧空間２１２となっている。セパレータ２９は、密閉容器２１に固着されている。 A separator 29 that partitions the inside of the closed container 21 into a high-pressure space 211 and a low-pressure space 212 is arranged above the compression mechanism unit 10. A high pressure space 211 is above the separator 29, and a low pressure space 212 is below. The separator 29 is fixed to the closed container 21.
　固定スクロール１１の揺動スクロール１２とは反対側の端面とセパレータ２９との間には、固定スクロール１１に形成された第１吐出ポート１１１に連通する吐出室２９１ａが形成されている。セパレータ２９の中央部には、入口側が吐出室２９１ａに開口し、出口側が高圧空間２１１に開口し、圧縮室９内で圧縮された流体を高圧空間２１１へ吐出する第２吐出ポート２９２が形成されている。第２吐出ポート２９２の出口側には、吐出室２９１ａへの流体の逆流を防ぐため、第２吐出ポート２９２を開閉する吐出弁２５と、吐出弁２５のリフト量を制限する吐出弁ストッパ２５ｂとが設けられている。圧縮室９内で流体が所定圧力まで圧縮されると、吐出弁２５がその弾性力に逆らって持ち上げられ、圧縮された流体が第２吐出ポート２９２から高圧空間２１１内に吐出され、吐出管２４を通ってスクロール圧縮機１の外部に吐出される。 A discharge chamber 291a communicating with the first discharge port 111 formed in the fixed scroll 11 is formed between the separator 29 and the end surface of the fixed scroll 11 on the side opposite to the orbiting scroll 12. A second discharge port 292 for discharging the fluid compressed in the compression chamber 9 to the high pressure space 211 is formed in the center of the separator 29, the inlet side of which opens into the discharge chamber 291a and the outlet side of which opens into the high pressure space 211. ing. On the outlet side of the second discharge port 292, a discharge valve 25 that opens and closes the second discharge port 292 in order to prevent backflow of the fluid to the discharge chamber 291a, and a discharge valve stopper 25b that limits the lift amount of the discharge valve 25. Is provided. When the fluid is compressed to a predetermined pressure in the compression chamber 9, the discharge valve 25 is lifted up against its elastic force, the compressed fluid is discharged from the second discharge port 292 into the high pressure space 211, and the discharge pipe 24 And is discharged to the outside of the scroll compressor 1.
　セパレータ２９には更に、リリーフ機構２２０及びアンロード機構２３０等が設けられているが、これらの構成については改めて詳述する。 The separator 29 is further provided with a relief mechanism 220, an unload mechanism 230, etc., but the configuration of these will be described in detail again.
　密閉容器２１には、低圧空間２１２に連通し流体を吸入するための吸入管２３と、高圧空間２１１に連通し流体を吐出するための吐出管２４が設けられている。 The airtight container 21 is provided with a suction pipe 23 that communicates with the low pressure space 212 to suck the fluid, and a discharge pipe 24 that communicates with the high pressure space 211 and discharge the fluid.
　圧縮機構部１０は、吸入管２３から吸入した流体を圧縮し、密閉容器２１内の上方に形成されている高圧空間２１１に排出する。圧縮機構部１０は、固定スクロール１１と揺動スクロール１２とを備え、図１に示すように、固定スクロール１１は上側に、揺動スクロール１２は下側に配置されている。固定スクロール１１は、固定台板１１ａと、固定台板１１ａの一方の面に立設された渦巻状突起である固定渦巻歯１１ｂとで構成されている。揺動スクロール１２は、揺動台板１２ａと、揺動台板１２ａの一方の面に立設された渦巻状突起である揺動渦巻歯１２ｂとで構成されている。 The compression mechanism unit 10 compresses the fluid sucked from the suction pipe 23 and discharges it into the high-pressure space 211 formed above the inside of the closed container 21. The compression mechanism unit 10 includes a fixed scroll 11 and an orbiting scroll 12. As shown in FIG. 1, the fixed scroll 11 is arranged on the upper side and the orbiting scroll 12 is arranged on the lower side. The fixed scroll 11 is composed of a fixed base plate 11a and fixed spiral teeth 11b which are spiral protrusions provided upright on one surface of the fixed base plate 11a. The oscillating scroll 12 includes an oscillating base plate 12a and oscillating spiral teeth 12b, which are spiral protrusions provided upright on one surface of the oscillating base plate 12a.
　固定渦巻歯１１ｂ及び揺動渦巻歯１２ｂは、例えばインボリュート曲線にならって形成されており、固定渦巻歯１１ｂ及び揺動渦巻歯１２ｂが噛み合って組み合わされることで、固定渦巻歯１１ｂと揺動渦巻歯１２ｂとの間に、複数の圧縮室９が形成される。 The fixed spiral tooth 11b and the oscillating spiral tooth 12b are formed, for example, according to an involute curve, and the fixed spiral tooth 11b and the oscillating spiral tooth 12b are meshed with each other so that the fixed spiral tooth 11b and the oscillating spiral tooth 12b are combined. A plurality of compression chambers 9 are formed between the compression chambers 12 and 12b.
　固定スクロール１１と揺動スクロール１２はセパレータ２９とフレーム１４との間に配置されている。固定スクロール１１は、固定スクロール１１の外周に複数配置された径方向ガイド部材２８によって平面位置と姿勢とが規制される。固定スクロール１１の固定台板１１ａには、一端が圧縮室９に開口し、他端が後述の背圧室２９１ｂに開口する一対の抽気孔１１２が形成されている。 The fixed scroll 11 and the orbiting scroll 12 are arranged between the separator 29 and the frame 14. The planar position and the posture of the fixed scroll 11 are regulated by a plurality of radial guide members 28 arranged on the outer circumference of the fixed scroll 11. The fixed base plate 11a of the fixed scroll 11 is formed with a pair of bleed holes 112, one end of which opens into the compression chamber 9 and the other end of which opens into a back pressure chamber 291b described later.
　揺動スクロール１２において揺動渦巻歯１２ｂの形成面とは反対側の面の中心部に、円筒形状のボス部１２１が形成されている。揺動スクロール１２は、このボス部１２１に軸１５の上端に設けられた後述の偏心部１５ａが嵌入されて、固定スクロール１１に対して自転することなく偏心旋回運動を行う。 A cylindrical boss 121 is formed in the center of the surface of the orbiting scroll 12 opposite to the surface on which the orbiting spiral teeth 12b are formed. The oscillating scroll 12 has an eccentric portion 15a, which will be described later, provided at the upper end of the shaft 15 fitted into the boss portion 121, and performs an eccentric orbiting motion without rotating with respect to the fixed scroll 11.
　モータ１８は、ステータ１８ａと、ステータ１８ａの内周側で回転可能な軸１５に固定されたロータ１８ｂからなる。ステータ１８ａは、通電されることによってロータ１８ｂを回転させる。ステータ１８ａは、外周面が焼き嵌め等により密閉容器２１に固着支持されている。ロータ１８ｂは、ステータ１８ａに通電がされることにより回転し、軸１５を駆動する。 The motor 18 includes a stator 18a and a rotor 18b fixed to a shaft 15 that is rotatable on the inner peripheral side of the stator 18a. The stator 18a rotates the rotor 18b by being energized. The outer peripheral surface of the stator 18a is fixedly supported by the closed container 21 by shrink fitting or the like. The rotor 18b rotates by energizing the stator 18a, and drives the shaft 15.
　軸１５は、上端部に偏心部１５ａが形成されており、偏心部１５ａが揺動スクロール１２のボス部１２１に嵌合され、軸１５の回転により揺動スクロール１２が偏心旋回運動する。 The shaft 15 has an eccentric part 15a formed at the upper end, and the eccentric part 15a is fitted to the boss part 121 of the orbiting scroll 12, and the orbiting scroll 12 makes an eccentric orbital motion by the rotation of the shaft 15.
　軸１５には、モータ１８の上側に第１バランサ１６が取り付けられている。また、ロータ１８ｂの下側に第２バランサ１７が取り付けられている。第１バランサ１６は、偏心部１５ａと偏心方向が逆向きになるように取り付けられている。 A first balancer 16 is attached to the shaft 15 above the motor 18. Further, the second balancer 17 is attached to the lower side of the rotor 18b. The first balancer 16 is attached so that the eccentric direction is opposite to that of the eccentric portion 15a.
　軸１５の下端部には、給油ポンプ２７が装着されている。給油ポンプ２７は軸１５の回転に従い、油溜めに保有している潤滑油２２を軸１５内部に設けられた給油孔１５２を通して各摺動部に供給する。 An oil supply pump 27 is attached to the lower end of the shaft 15. The oil supply pump 27 supplies the lubricating oil 22 held in the oil sump to each sliding portion through an oil supply hole 152 provided inside the shaft 15 as the shaft 15 rotates.
　圧縮機構部１０内には、揺動スクロール１２の偏心旋回運動中における自転運動を阻止するためのオルダムリング等の姿勢規制手段１３が配設されている。この姿勢規制手段１３は、フレーム１４と揺動スクロール１２との間に配設され、揺動スクロール１２の自転運動を阻止すると共に、公転運動である偏心旋回運動を可能とする。 In the compression mechanism section 10, an attitude regulating means 13 such as an Oldham ring for preventing rotation of the orbiting scroll 12 during eccentric orbiting movement is provided. The posture restricting means 13 is arranged between the frame 14 and the orbiting scroll 12, and prevents the orbiting movement of the orbiting scroll 12 and enables an eccentric orbiting movement which is an orbiting movement.
　図１において、密閉容器２１に設けられた図示省略の電源端子に通電されると、ステータ１８ａとロータ１８ｂとの間にトルクが発生し、主軸受１４ａと副軸受１９ａとで支持された軸１５が回転する。軸１５の回転により、揺動スクロール１２が姿勢規制手段１３により自転を規制されて偏心旋回運動する。 In FIG. 1, when a power supply terminal (not shown) provided in the closed container 21 is energized, a torque is generated between the stator 18a and the rotor 18b, and the shaft 15 supported by the main bearing 14a and the sub bearing 19a. Rotates. Due to the rotation of the shaft 15, the orbiting scroll 12 is eccentrically orbitally rotated by the rotation of the posture restricting means 13 being restricted.
　揺動スクロール１２の運動に伴うアンバランスは、軸１５に取り付けられた第１バランサ１６とロータ１８ｂに取り付けられた第２バランサ１７とによって釣り合わせるようになっている。軸１５の回転により、密閉容器２１の下部に貯留した潤滑油２２が給油ポンプ２７で汲み上げられ、軸１５内に設けられた給油孔１５２から各摺動部に供給される。 The unbalance due to the movement of the orbiting scroll 12 is balanced by the first balancer 16 attached to the shaft 15 and the second balancer 17 attached to the rotor 18b. The rotation of the shaft 15 causes the lubricating oil 22 stored in the lower portion of the closed container 21 to be pumped up by the oil supply pump 27 and supplied to each sliding portion from the oil supply hole 152 provided in the shaft 15.
　吸入管２３から密閉容器２１内に吸入されたガスは、揺動スクロール１２の偏心旋回運動に伴い、複数の圧縮室９のうち最外周の圧縮室９に取り込まれる。 The gas sucked into the closed container 21 from the suction pipe 23 is taken into the outermost compression chamber 9 among the plurality of compression chambers 9 along with the eccentric orbiting motion of the orbiting scroll 12.
　ガスを取り込んだ圧縮室９は、揺動スクロール１２の偏心旋回運動に伴い、外周部から中心方向に移動しながら容積を減じ、流体を圧縮する。圧縮された流体は、固定スクロール１１に設けた第１吐出ポート１１１及びセパレータ２９に設けた第２吐出ポート２９２から吐出弁２５を押し上げて高圧空間２１１に吐出され、吐出管２４から密閉容器２１外に排出される。 The compression chamber 9 that has taken in gas compresses the fluid by reducing the volume while moving from the outer peripheral portion toward the center along with the eccentric orbiting motion of the orbiting scroll 12. The compressed fluid is pushed up the discharge valve 25 from the first discharge port 111 provided in the fixed scroll 11 and the second discharge port 292 provided in the separator 29 to be discharged into the high pressure space 211, and discharged from the discharge pipe 24 to the outside of the closed container 21. Is discharged to.
　以下、渦巻の動作及び抽気孔１１２の位置に関する記述は実施の形態１及び実施の形態２に共通である。 The following description of the swirling operation and the position of the bleed hole 112 is common to the first and second embodiments.
　図２は、図１のスクロール圧縮機の揺動スクロールの偏心旋回に伴う圧縮行程を示す図である。図２において、複数の圧縮室９のうち、最も内側の圧縮室９を最内室９ａ、最も外側の圧縮室９を最外室９ｃ、最内室９ａと最外室９ｃとの間の圧縮室９を、内側から数えて２つ目の圧縮室という意味で第２室９ｂという。図２には、２．５巻程度の渦巻仕様の例を示している。 FIG. 2 is a diagram showing a compression stroke accompanying eccentric rotation of the orbiting scroll of the scroll compressor of FIG. In FIG. 2, among the plurality of compression chambers 9, the innermost compression chamber 9 is the innermost chamber 9a, the outermost compression chamber 9 is the outermost chamber 9c, and the compression between the innermost chamber 9a and the outermost chamber 9c is performed. The chamber 9 is called a second chamber 9b in the sense that it is the second compression chamber counted from the inside. FIG. 2 shows an example of a spiral specification of about 2.5 turns.
　図２（ｂ）は、クランク角が吸入完了角の状態を示している。すなわち、最も外側の圧縮室９における流体の吸入が完了し、固定渦巻歯１１ｂと揺動渦巻歯１２ｂとによって形成される複数の圧縮室９として、内側から順に、最内室９ａと、一対の第２室９ｂと、一対の最外室９ｃとが形成されたところを示している。以下、吸入完了角とは、渦巻歯の巻き終わり側で圧縮室９の吸入が完了したときのクランク角を指す。 Fig. 2(b) shows the state where the crank angle is the intake completion angle. That is, the suction of the fluid in the outermost compression chamber 9 is completed, and as the plurality of compression chambers 9 formed by the fixed spiral teeth 11b and the swing spiral teeth 12b, the innermost chamber 9a and the pair of innermost chambers 9a are arranged in order from the inside. The place where the second chamber 9b and the pair of outermost chambers 9c are formed is shown. Hereinafter, the suction completion angle refers to the crank angle when the suction of the compression chamber 9 is completed on the winding end side of the spiral tooth.
　図２（ｃ）は、クランク角が連通角の状態を示している。上記図２（ｂ）では、固定渦巻歯１１ｂと揺動渦巻歯１２ｂとが巻き始め側で接触してシール形成点１３０を形成していることで、最内室９ａと一対の第２室９ｂとが形成されている。これに対し、図２（ｃ）では、シール形成点１３０が離間する直前、第２室９ｂが最内室９ａと合流して一室となるところである。以下、連通角とは、第２室９ｂが最内室９ａと合流して一室となるときのクランク角を指す。 Fig. 2(c) shows a state in which the crank angle is the communication angle. In FIG. 2B, the fixed spiral tooth 11b and the oscillating spiral tooth 12b contact each other on the winding start side to form the seal forming point 130, so that the innermost chamber 9a and the pair of second chambers 9b are formed. And are formed. On the other hand, in FIG. 2C, the second chamber 9b merges with the innermost chamber 9a to become one chamber immediately before the seal forming point 130 is separated. Hereinafter, the communication angle refers to the crank angle when the second chamber 9b merges with the innermost chamber 9a to form one chamber.
　図２（ｄ）は、シール形成点１３０が離間し、第２室９ｂが最内室９ａと合わさって一室となった状態、最内室９ａと最外室９ｃとの２室状態を示している。 FIG. 2D shows a state in which the seal forming point 130 is separated and the second chamber 9b is combined with the innermost chamber 9a to form one chamber, and the innermost chamber 9a and the outermost chamber 9c are two chambers. ing.
　図２（ｅ）～図２（ｆ）も、最内室９ａと最外室９ｃの２室状態を示している。 2(e) to 2(f) also show the two-room state of the innermost chamber 9a and the outermost chamber 9c.
　以上のように、クランク角０～２πの揺動スクロール１２の偏心旋回１回転の間に、吸入完了角と連通角とに対するクランク角の大小により、圧縮室９は２室又は３室となる。すなわち、吸入完了角から連通角の間は、最外室９ｃ、第２室９ｂ及び最内室９ａの３室となる。連通角から吸入完了角の間は、最外室９ｃと最内室９ａとの２室となる。そして、吸入完了角において新たな最外室９ｃが形成されて、それまでの最外室９ｃが第２室９ｂとなり、最外室９ｃ、第２室９ｂ及び最内室９ａの３室となる。 As described above, the compression chamber 9 becomes two or three chambers depending on the magnitude of the crank angle with respect to the suction completion angle and the communication angle during one rotation of the eccentric rotation of the orbiting scroll 12 having a crank angle of 0 to 2π. That is, there are three chambers, the outermost chamber 9c, the second chamber 9b, and the innermost chamber 9a, between the suction completion angle and the communication angle. Between the communication angle and the suction completion angle, there are two chambers, the outermost chamber 9c and the innermost chamber 9a. Then, a new outermost chamber 9c is formed at the suction completion angle, and the outermost chamber 9c up to that point becomes the second chamber 9b, and becomes the outermost chamber 9c, the second chamber 9b, and the innermost chamber 9a. ..
　図２（ａ）～図２（ｆ）において、図２（ｂ）で吸入が完了した最外室９ｃは、揺動スクロール１２の偏心旋回により、図２（ｃ）、図２（ｄ）、図２（ｅ）、図２（ｆ）、図２（ａ）を経て、容積が小さくなることで、流体の圧縮を行う。そして、再び図２（ｂ）に到達することで新たに最外室９ｃができるため、これまでの最外室９ｃが第２室９ｂとなる。この第２室９ｂが、図２（ｃ）の連通角において最内室９ａに合流し始める。 2(a) to 2(f), the outermost chamber 9c of which suction has been completed in FIG. 2(b) is eccentrically swung by the orbiting scroll 12 so that the outermost chamber 9c of FIG. 2(c), FIG. 2(e), FIG. 2(f), and FIG. 2(a), the volume is reduced, whereby the fluid is compressed. Then, the outermost chamber 9c is newly formed by reaching FIG. 2B again, so that the outermost chamber 9c thus far becomes the second chamber 9b. The second chamber 9b starts to join the innermost chamber 9a at the communication angle in FIG. 2(c).
　一対の抽気孔１１２は、それぞれ固定渦巻歯１１ｂの内向面／外向面に沿って設けられ、内向面／外向面各々の巻き終わり部１１ｂａ及び巻き終わり部１１ｂｂ（図２（ｂ）参照）から伸開角で約２．５π内側に位置している。 The pair of bleed holes 112 are provided along the inward/outward surfaces of the fixed spiral teeth 11b, respectively, and extend from the winding end portion 11ba and the winding end portion 11bb (see FIG. 2(b)) of each of the inward/outward surfaces. It is located inside about 2.5π at the open angle.
　吸入完了時のクランク角を０とすると、クランク角０で吸入完了した最外室９ｃは揺動スクロール１２の偏心旋回運動に伴って渦巻中心方向に移動する。クランク角が約π／２のとき、つまり吸入完了後１／４回転前後で第２室／最外室間のシール形成点が抽気孔位置を通過すると、最外室９ｃに抽気孔１１２が開口し始める。そして、抽気孔１１２が開口した最外室９ｃが、渦巻中心方向に容積を減少しながら移動し、吸入完了時から揺動スクロール１２が１回転偏心旋回運動した２回目の吸入完了角において、最外室９ｃが第２室９ｂとなる。このように最外室９ｃが第２室９ｂになった後も、次の第２室／最外室間シール形成点の抽気孔位置通過まではこの第２室９ｂに抽気孔１１２が開口している。 When the crank angle at the time of completion of suction is 0, the outermost chamber 9c at the completion of suction at the crank angle of 0 moves toward the center of the spiral with the eccentric orbiting motion of the orbiting scroll 12. When the crank angle is about π/2, that is, when the seal forming point between the second chamber and the outermost chamber passes the bleed hole position about 1/4 rotation after completion of suction, the bleed hole 112 is opened in the outermost chamber 9c. Begin to. Then, the outermost chamber 9c in which the extraction hole 112 is opened moves in the direction toward the center of the spiral while decreasing the volume, and at the second suction completion angle at which the orbiting scroll 12 has made one eccentric orbiting motion from the completion of suction, The outer chamber 9c becomes the second chamber 9b. Even after the outermost chamber 9c becomes the second chamber 9b in this way, the bleeding hole 112 is opened in the second chamber 9b until the bleeding hole position at the next second chamber/outermost chamber seal forming point passes. ing.
　最内室（連通角以前の場合は第２室）／最外室間のシール形成点の抽気孔位置通過が連通角よりも後となる設定では、揺動スクロール１２の偏心旋回運動が進み、連通角での第２室９ｂと最内室９ａの合流以降は、最内室９ａに抽気孔１１２が開口する。シール形成点が抽気孔位置を通過した時点で抽気孔１１２は第２室に開口する。前記２回目の吸入完了角からクランク角が約π／４になると、第２室９ｂへの抽気孔１１２の開口が終了し、２回目の吸入完了角後１／４回転前後の最外室９ｃに抽気孔１１２が開口し始める。 In a setting in which the passage of the extraction hole at the seal forming point between the innermost chamber (the second chamber before the communication angle)/outermost chamber is after the communication angle, the eccentric orbiting motion of the orbiting scroll 12 proceeds, After the merging of the second chamber 9b and the innermost chamber 9a at the communication angle, the extraction hole 112 opens in the innermost chamber 9a. The bleed hole 112 opens to the second chamber when the seal forming point passes through the bleed hole position. When the crank angle becomes about π/4 from the second suction completion angle, the opening of the extraction hole 112 to the second chamber 9b ends, and the outermost chamber 9c about 1/4 rotation after the second suction completion angle. The bleed hole 112 begins to open.
　揺動スクロール１２の偏心旋回により、抽気孔１１２から見れば、近づいてくる最外室９ｃに開口してから、この最外室９ｃが第２室９ｂを経て最内室９ａとなるまで開口し続けた後、次に近づいてくる最外室９ｃに開口し始める、という動作が繰り返される。抽気孔１１２は、揺動スクロール１２の偏心旋回１回転中常に何れかの圧縮室９即ち中間圧圧縮室３７に開口し、圧縮室９内の圧力を後述の背圧室２９１ｂに供給する。図２によると、抽気孔１１２が揺動渦巻歯１２ｂによって塞がれ、厳密には圧縮室９に開口しない時間もあるが、開口しない時間は僅かであって、実質的には常に何れかの圧縮室９に開口している。 Due to the eccentric rotation of the orbiting scroll 12, when viewed from the bleed hole 112, the outermost chamber 9c that is approaching is opened, and then the outermost chamber 9c is opened through the second chamber 9b to the innermost chamber 9a. After that, the operation of opening the outermost chamber 9c approaching next is repeated. The bleeding hole 112 is always open to one of the compression chambers 9, that is, the intermediate pressure compression chamber 37 during one eccentric rotation of the orbiting scroll 12, and supplies the pressure in the compression chamber 9 to the back pressure chamber 291b described later. According to FIG. 2, the bleed hole 112 is blocked by the oscillating spiral teeth 12b, and strictly speaking, there is a time during which it does not open to the compression chamber 9, but the time during which it does not open is small, and it is substantially always It opens to the compression chamber 9.
　スクロール圧縮機においては、渦巻仕様が決まることで組込容積比、すなわち（吸入完了容積）／（連通角到達時の第２室の容積）が決まる。スクロール圧縮機１では、上述したように、吸入完了角で最外室９ｃが形成された後、揺動スクロール１２が１回転偏心旋回運動して再び吸入完了角に到達することで最外室９ｃが第２室９ｂになり、更に揺動スクロール１２が偏心旋回運動して連通角に到達することで、その第２室９ｂが最内室９ａに合流する。つまり、最外室９ｃが形成されてから、その最外室９ｃが連通角において最内室９ａと合流して第１吐出ポート１１１と連通するまでの間、その圧縮室９では運転条件の高低圧に関わらず圧縮が行われる。 In a scroll compressor, the built-in volume ratio, that is, (suction completion volume)/(volume of the second chamber when the communication angle is reached) is determined by determining the spiral specifications. In the scroll compressor 1, as described above, after the outermost chamber 9c is formed at the suction completion angle, the orbiting scroll 12 makes one rotation eccentric orbital motion and reaches the suction completion angle again to reach the suction completion angle 9c. Becomes the second chamber 9b, and the orbiting scroll 12 further eccentrically orbits to reach the communication angle, whereby the second chamber 9b joins the innermost chamber 9a. In other words, after the outermost chamber 9c is formed, until the outermost chamber 9c merges with the innermost chamber 9a at the communication angle and communicates with the first discharge port 111, the compression chamber 9 has high operating conditions. The compression takes place regardless of the low pressure.
　圧縮比或いは圧力比は、ある圧縮室が吸入完了時点からどれだけ圧縮されたかを、容積減少の結果の昇圧に着目して示す指標であって、同じ渦巻仕様であっても冷媒物性及び吸入状態量によって異なってくる。渦巻仕様としては組込容積比で定義する方が合理的である。 The compression ratio or pressure ratio is an index showing how much a certain compression chamber has been compressed from the time when suction is completed, focusing on the pressure increase resulting from the volume reduction. It depends on the amount. It is more rational to define the spiral volume as a built-in volume ratio.
　通常、スクロール圧縮機では、組込容積比は固定値である。このため、吸入圧と吐出圧との圧力差が例えば比較的小さい運転条件では、圧縮機構部で冷媒を圧縮し過ぎる過圧縮が生じる。つまり、上述したように、揺動スクロールが吸入完了角から１回転偏心旋回運動し、更に連通角に到達するまで、圧縮室では圧縮が継続されるので、組込容積比まで圧縮したときに、圧縮室内の圧力が高圧を上回ると、必要以上に昇圧することによる損失、所謂過圧縮損失を生じる。 Normally, in scroll compressors, the built-in volume ratio is a fixed value. Therefore, under operating conditions where the pressure difference between the suction pressure and the discharge pressure is relatively small, for example, overcompression occurs in which the refrigerant is compressed too much by the compression mechanism section. That is, as described above, since the orbiting scroll makes one rotation eccentric orbital movement from the suction completion angle and further continues to be compressed in the compression chamber until the communication angle is reached, when compression is performed up to the built-in volume ratio, When the pressure in the compression chamber exceeds the high pressure, a loss due to excessive pressure increase, so-called overcompression loss occurs.
　組込容積比を持つことによる過圧縮損失を低減することは、スクロール圧縮機の圧縮機構特有の課題である。その１つの手段が、連通角到達以前の圧縮室から高圧側への吐出、つまり高圧バイパスを行う、所謂リリーフ機構であり、本実施の形態１ではリリーフ機構として後述のリリーフポート２９５及びリリーフ弁２６等を設けている。 -Reducing the over-compression loss by having a built-in volume ratio is a problem peculiar to the compression mechanism of the scroll compressor. One of the means is a so-called relief mechanism that discharges from the compression chamber before reaching the communication angle to the high pressure side, that is, performs high pressure bypass. In the first embodiment, a relief port 295 and a relief valve 26, which will be described later, are used as the relief mechanism. Etc. are provided.
　本実施の形態１の低圧バイパスによるアンロードを、密閉容器２１外から圧縮機構部１０へ接続する配管等を用いることなく可能とした構造について、以下に説明する。 A structure that enables unloading by the low-pressure bypass according to the first embodiment without using a pipe or the like connected to the compression mechanism unit 10 from outside the closed container 21 will be described below.
　図３は、本発明の実施の形態１によるスクロール圧縮機のアンロード時の要部断面模式図である。図４は、本発明の実施の形態１によるスクロール圧縮機のアンロード時のアンロード機構の拡大模式図である。図５は、本発明の実施の形態１によるスクロール圧縮機の非アンロード時の要部断面模式図である。図６は、本発明の実施の形態１によるスクロール圧縮機の非アンロード時のアンロード機構の拡大模式図である。 FIG. 3 is a schematic cross-sectional view of essential parts of the scroll compressor according to Embodiment 1 of the present invention when it is unloaded. FIG. 4 is an enlarged schematic view of the unload mechanism during unloading of the scroll compressor according to the first embodiment of the present invention. FIG. 5 is a schematic cross-sectional view of a main part of the scroll compressor according to the first embodiment of the present invention when it is not unloaded. FIG. 6 is an enlarged schematic view of the unload mechanism of the scroll compressor according to the first embodiment of the present invention when it is not unloading.
　固定スクロール１１の揺動スクロール１２とは反対側の端面とセパレータ２９との間には、背圧室２９１ｂが形成されている。背圧室２９１ｂは、セパレータ２９の低圧空間２１２側の面に形成された円環状の凹部で構成されている。背圧室２９１ｂの内周面１１８の溝には環状のシール部材３３が配置されている。また、背圧室２９１ｂの外周面１１９の溝には環状のシール部材３４が配置されている。これにより、固定スクロール１１の固定台板１１ａとセパレータ２９との間には、円筒状の吐出室２９１ａと、環状の背圧室２９１ｂとが区画される。 A back pressure chamber 291b is formed between the separator 29 and the end surface of the fixed scroll 11 opposite to the orbiting scroll 12. The back pressure chamber 291b is formed of an annular recess formed on the surface of the separator 29 on the low pressure space 212 side. An annular seal member 33 is arranged in the groove of the inner peripheral surface 118 of the back pressure chamber 291b. An annular seal member 34 is arranged in the groove of the outer peripheral surface 119 of the back pressure chamber 291b. As a result, a cylindrical discharge chamber 291a and an annular back pressure chamber 291b are defined between the fixed base plate 11a of the fixed scroll 11 and the separator 29.
　吐出室２９１ａは、第１吐出ポート１１１に連通しており、第１吐出ポート１１１から吐出された流体によって高圧となる。背圧室２９１ｂは、固定スクロール１１に形成された抽気孔１１２を介して圧縮途中の圧縮室９即ち中間圧圧縮室３７に連通しており、中間圧となる。 The discharge chamber 291a communicates with the first discharge port 111, and a high pressure is generated by the fluid discharged from the first discharge port 111. The back pressure chamber 291b communicates with the compression chamber 9 in the middle of compression, that is, the intermediate pressure compression chamber 37 through the extraction hole 112 formed in the fixed scroll 11, and has an intermediate pressure.
　セパレータ２９には、過圧縮リリーフを行うリリーフ機構２２０としてリリーフポート２９５、リリーフ弁２６及びリリーフ弁２６のリフト量を制限するリリーフ弁ストッパ２６ｂが設けられている。リリーフポート２９５は、入口側が背圧室２９１ｂに開口し、出口側が高圧空間２１１に開口している。リリーフ弁２６及びリリーフ弁ストッパ２６ｂは、リリーフポート２９５の出口側に設けられている。 The separator 29 is provided with a relief port 295, a relief valve 26, and a relief valve stopper 26b for limiting the lift amount of the relief valve 26 as a relief mechanism 220 for performing overcompression relief. The relief port 295 has an inlet side opening to the back pressure chamber 291b and an outlet side opening to the high pressure space 211. The relief valve 26 and the relief valve stopper 26b are provided on the outlet side of the relief port 295.
　固定スクロールの軸方向位置が固定されているスクロール圧縮機においては、運転中の渦巻歯或いは台板の変形及び熱膨張等により、渦巻歯先が、対向する相手側のスクロールの台板に接触又は干渉することがある。最終的に渦巻歯先或いは相手台板の焼付きに至る可能性があるので、この不都合を避けるため、組立時に、渦巻歯先と対向する相手側のスクロールの台板との間に歯先すきまを設定する必要があった。組立時設定歯先すきまは、流体の漏れ経路となることから、圧縮機としての効率低下の要因となっていた。 In a scroll compressor in which the axial position of the fixed scroll is fixed, the spiral tooth tips may come into contact with the opposite base plate of the scroll on the opposite side due to deformation and thermal expansion of the spiral teeth or the base plate during operation. May interfere. In the end, there is a possibility that seizure of the spiral tooth tip or seizure of the mating base plate may occur eventually. Had to set. The tooth clearance set at the time of assembly is a factor for reducing the efficiency of the compressor because it serves as a fluid leakage path.
　これに対し、本実施の形態１のスクロール圧縮機１は、背圧室２９１ｂに中間圧力を導くと共に、吐出室２９１ａに吐出圧を導くことで、固定スクロール１１に軸方向の力を付加して揺動スクロール１２側に押し付ける構造となっている。所謂、軸方向コンププライアント方式を採用しているので、予め、組立時において歯先すきまを設定する必要がない。これにより、歯先すきまを極小化して漏れ損失を低減できる。 On the other hand, in the scroll compressor 1 according to the first embodiment, the intermediate pressure is introduced into the back pressure chamber 291b and the discharge pressure is introduced into the discharge chamber 291a, thereby applying an axial force to the fixed scroll 11. The structure is such that it is pressed against the orbiting scroll 12. Since the so-called axial compliant system is adopted, it is not necessary to set the tooth tip clearance during assembly in advance. As a result, the tooth tip clearance can be minimized and the leakage loss can be reduced.
　セパレータ２９には更に、圧縮室９から低圧側へ流体をバイパスすることによりスクロール圧縮機１の吐出量を制限するアンロードと、吐出量１００％のフルロードとを切り替えるアンロード機構２３０が組み込まれている。以下、フルロードを非アンロードということがある。 The separator 29 is further equipped with an unload mechanism 230 that switches between unloading which limits the discharge amount of the scroll compressor 1 by bypassing the fluid from the compression chamber 9 to the low pressure side and full load with a discharge amount of 100%. ing. Hereinafter, full load may be referred to as non-unload.
　アンロード機構２３０は、スプール状の制御弁３１と、ばね等の弾性体３２とがセパレータ２９内の径方向に形成されたアンロード孔２９６に配置されている。アンロード孔２９６の径方向内側の端部には、制御弁３１による高圧導入孔２９４ａの閉止を防ぐ凸部２９ａが形成されている。アンロード孔２９６の径方向外側の端部はプラグ３５ｃで閉じられている。 The unload mechanism 230 has a spool-shaped control valve 31 and an elastic body 32 such as a spring arranged in an unload hole 296 formed in the separator 29 in the radial direction. A convex portion 29a that prevents the control valve 31 from closing the high-pressure introducing hole 294a is formed at the radially inner end of the unload hole 296. The radially outer end of the unload hole 296 is closed by a plug 35c.
　アンロード機構２３０は、中間圧圧縮室３７内の流体を、抽気孔１１２と、背圧室２９１ｂと、セパレータ２９に形成されたアンロード経路とを経由して低圧空間２１２にバイパスすることで、アンロードを行う。アンロード経路は、背圧室２９１ｂに一端が開口する背圧室連通路２９３ａと、低圧空間２１２に一端が開口する低圧空間連通路２９３ｂと、アンロード孔２９６内の制御弁小径部外周空間２９３ｃとから構成される。 The unloading mechanism 230 bypasses the fluid in the intermediate pressure compression chamber 37 into the low pressure space 212 via the extraction hole 112, the back pressure chamber 291b, and the unloading path formed in the separator 29, Unload. The unload path includes a back pressure chamber communication passage 293a whose one end opens in the back pressure chamber 291b, a low pressure space communication passage 293b whose one end opens in the low pressure space 212, and a control valve small diameter portion outer peripheral space 293c in the unload hole 296. Composed of and.
　制御弁３１は、アンロード孔２９６内にスライド自在に配置されていて、アンロード孔２９６内をスライドすることで、アンロード孔２９６内での制御弁小径部外周空間２９３ｃの位置を移動させる。つまり、制御弁３１は、背圧室連通路２９３ａが制御弁小径部外周空間２９３ｃに対して開く位置（図４）と、閉じる位置（図６）とに移動してアンロード経路を開閉し、アンロードと非アンロードとを切り替える。 The control valve 31 is slidably arranged in the unload hole 296, and by sliding in the unload hole 296, the position of the control valve small diameter portion outer peripheral space 293c in the unload hole 296 is moved. That is, the control valve 31 moves to a position (FIG. 4) in which the back pressure chamber communication passage 293a opens with respect to the control valve small diameter portion outer peripheral space 293c and a closed position (FIG. 6) to open and close the unloading path, Switch between unloading and non-unloading.
　セパレータ２９には、アンロード孔２９６に開口する、高圧導入孔２９４ａ及び低圧導入孔２９４ｂが形成されている。高圧導入孔２９４ａは、一端が高圧空間２１１に開口し、他端がアンロード孔２９６に開口し、高圧空間２１１の高圧流体を、アンロード孔２９６において制御弁３１の移動方向の一方の端面３１ａ側空間に導入する。低圧導入孔２９４ｂは、一端がアンロード孔２９６に開口し、他端が低圧空間２１２に開口し、低圧空間２１２の低圧流体を、アンロード孔２９６において制御弁３１の移動方向の他方の端面３１ｂ側の低圧導入空間２９７に導入する。 The separator 29 is formed with a high-pressure introduction hole 294a and a low-pressure introduction hole 294b which open to the unload hole 296. One end of the high-pressure introduction hole 294a is opened to the high-pressure space 211 and the other end is opened to the unload hole 296, so that the high-pressure fluid in the high-pressure space 211 flows through the unload hole 296 at one end surface 31a in the moving direction of the control valve 31. Introduce into the side space. The low-pressure introduction hole 294b has one end opened to the unload hole 296 and the other end opened to the low-pressure space 212, so that the low-pressure fluid in the low-pressure space 212 flows through the unload hole 296 at the other end surface 31b in the moving direction of the control valve 31. It is introduced into the low pressure introduction space 297 on the side.
　弾性体３２は、制御弁３１の他方の端面３１ｂ側の低圧導入空間２９７に配置されており、制御弁３１を高圧側（図６の右側）に付勢している。制御弁３１は、運転停止時、弾性体３２の付勢力により高圧側に押圧されて一方の端面３１ａが凸部２９ａに接触した状態となっている。この状態において、制御弁３１は、背圧室連通路２９３ａ、制御弁小径部外周空間２９３ｃ、低圧空間連通路２９３ｂからなるアンロード経路を開放している。 The elastic body 32 is arranged in the low pressure introduction space 297 on the other end surface 31b side of the control valve 31, and urges the control valve 31 to the high pressure side (right side in FIG. 6). When the operation is stopped, the control valve 31 is pressed to the high pressure side by the urging force of the elastic body 32, and one end surface 31a is in contact with the convex portion 29a. In this state, the control valve 31 opens the unloading path including the back pressure chamber communication passage 293a, the control valve small diameter outer peripheral space 293c, and the low pressure space communication passage 293b.
　スクロール圧縮機１の運転条件が、高低圧差が設定値以下であるとき、制御弁３１の一方の端面３１ａに作用する高圧と他方の端面３１ｂに作用する低圧との差圧力よりも、弾性体３２による弾性力が上回る。この場合、制御弁３１は端面３１ａ方向に押圧され、図３及び図４に示すように制御弁３１の一方の端面３１ａが凸部２９ａに接触する位置まで移動して停止し、背圧室連通路２９３ａと制御弁小径部外周空間２９３ｃとが連通する。つまり背圧室連通路２９３ａ、制御弁小径部外周空間２９３ｃ、低圧空間連通路２９３ｂからなるアンロード経路が開放される。その結果、中間圧圧縮室３７内の流体が、抽気孔１１２、背圧室２９１ｂ、背圧室連通路２９３ａ、制御弁小径部外周空間２９３ｃ、低圧空間連通路２９３ｂの順に通過して低圧空間２１２に排出される。このため、中間圧圧縮室３７が抽気孔１１２に連通している間、言い換えれば中間圧圧縮室３７の外周側シール形成点が抽気孔１１２を通過するまでの間は、中間圧圧縮室３７では圧縮が為されず、容量制御、すなわちアンロード状態となる。 When the operating condition of the scroll compressor 1 is such that the high/low pressure difference is equal to or less than the set value, the elastic body 32 is higher than the differential pressure between the high pressure acting on one end face 31a of the control valve 31 and the low pressure acting on the other end face 31b. The elastic force due to exceeds. In this case, the control valve 31 is pressed in the direction of the end surface 31a, and as shown in FIGS. 3 and 4, one end surface 31a of the control valve 31 moves to a position where it comes into contact with the convex portion 29a and then stops. The passage 293a and the control valve small diameter portion outer peripheral space 293c communicate with each other. That is, the unloading path including the back pressure chamber communication passage 293a, the control valve small-diameter portion outer peripheral space 293c, and the low pressure space communication passage 293b is opened. As a result, the fluid in the intermediate pressure compression chamber 37 passes through the bleed hole 112, the back pressure chamber 291b, the back pressure chamber communication passage 293a, the control valve small-diameter portion outer peripheral space 293c, and the low pressure space communication passage 293b in this order, and then the low pressure space 212. Is discharged to. Therefore, while the intermediate pressure compression chamber 37 communicates with the extraction hole 112, in other words, until the outer peripheral side seal forming point of the intermediate pressure compression chamber 37 passes through the extraction hole 112, the intermediate pressure compression chamber 37 The compression is not performed and the capacity is controlled, that is, the unload state is set.
　スクロール圧縮機１の運転条件が、高低圧差が設定値を超える場合には、制御弁３１の一方の端面３１ａに作用する高圧と他方の端面３１ｂに作用する低圧との差圧力が、弾性体３２による弾性力を上回る。この場合、図５及び図６に示すように制御弁３１が端面３１ｂ方向にスライドし、背圧室連通路２９３ａが制御弁３１によって塞がれる。これにより、背圧室連通路２９３ａ、制御弁小径部外周空間２９３ｃ、低圧空間連通路２９３ｂからなるアンロード経路が閉じられ、アンロード状態から非アンロード状態に切り替わる。 When the operating condition of the scroll compressor 1 is such that the difference between the high pressure and the low pressure exceeds the set value, the differential pressure between the high pressure acting on one end face 31a of the control valve 31 and the low pressure acting on the other end face 31b is equal to the elastic body 32. Exceeds the elastic force. In this case, as shown in FIGS. 5 and 6, the control valve 31 slides toward the end surface 31b, and the back pressure chamber communication passage 293a is closed by the control valve 31. As a result, the unloading path including the back pressure chamber communication passage 293a, the control valve small diameter portion outer peripheral space 293c, and the low pressure space communication passage 293b is closed, and the unloading state is switched to the non-unloading state.
　このようにアンロード機構２３０は、スクロール圧縮機１の運転条件に応じて制御弁３１の一方の端面３１ａと他方の端面３１ｂとに作用する圧力が変化することで、制御弁３１が自動的に移動し、アンロードと非アンロードとを自動的に切り替える。アンロードと非アンロードとの切り替え点となる上記設定値は、制御弁３１の両端面に作用する圧力を考慮して弾性体３２のばね定数を選択することで、所望の値に調整することが可能である。 In this way, the unloading mechanism 230 changes the pressure acting on the one end surface 31a and the other end surface 31b of the control valve 31 in accordance with the operating conditions of the scroll compressor 1, so that the control valve 31 automatically operates. Move and automatically switch between unloading and non-unloading. The above set value, which is the switching point between unloading and non-unloading, can be adjusted to a desired value by selecting the spring constant of the elastic body 32 in consideration of the pressure acting on both end surfaces of the control valve 31. Is possible.
　アンロード機構２３０は、制御弁３１の両端面に作用させる高低圧を、密閉容器２１内から導いているので、密閉容器２１内で完結した構造であり、密閉容器２１外から圧縮機構部１０へ接続する配管等が不要である。 Since the unloading mechanism 230 guides high and low pressures acting on both end surfaces of the control valve 31 from inside the closed container 21, it has a structure completed inside the closed container 21, and from the outside of the closed container 21 to the compression mechanism section 10. No need for connecting pipes.
　次に、スクロール圧縮機１の動作を、吐出室２９１ａ及び背圧室２９１ｂの作用、並びにリリーフ機構２２０及びアンロード機構２３０の動作に着目して説明する。 Next, the operation of the scroll compressor 1 will be described focusing on the actions of the discharge chamber 291a and the back pressure chamber 291b, and the actions of the relief mechanism 220 and the unload mechanism 230.
　運転時、固定スクロール１１は、吐出室２９１ａ及び背圧室２９１ｂの圧力を受けて、固定スクロール１１外周に複数配置された径方向ガイド部材２８（図２参照）によって平面位置と姿勢を規制されながら、圧縮室９内の圧力に抗して軸方向に揺動スクロール１２側へ押し付けられる。 During operation, the fixed scroll 11 receives the pressures of the discharge chamber 291a and the back pressure chamber 291b, and its planar position and posture are regulated by a plurality of radial guide members 28 (see FIG. 2) arranged on the outer circumference of the fixed scroll 11. , Is pressed in the axial direction toward the orbiting scroll 12 against the pressure in the compression chamber 9.
　高低圧差が小さい条件での運転時は、上述したようにアンロード機構２３０において制御弁３１が背圧室連通路２９３ａ、制御弁小径部外周空間２９３ｃ、低圧空間連通路２９３ｂからなるアンロード経路を開放する。これにより、中間圧圧縮室３７内の流体が、抽気孔１１２、背圧室２９１ｂ及びアンロード経路等を介して低圧空間２１２に排出され、アンロード状態となる。 During operation under the condition that the high/low pressure difference is small, as described above, in the unload mechanism 230, the control valve 31 has the unload path including the back pressure chamber communication passage 293a, the control valve small diameter outer peripheral space 293c, and the low pressure space communication passage 293b. Open. As a result, the fluid in the intermediate pressure compression chamber 37 is discharged into the low pressure space 212 via the bleed hole 112, the back pressure chamber 291b, the unloading path, etc., and becomes in the unloading state.
　アンロード時において、吸入完了角から１／４回転までの間は、最外室９ｃすなわち中間圧圧縮室３７で必ずしも必要ではない圧縮作用を行うことになる。しかし、吸入完了直後の容積変化に対する昇圧幅が小さい領域なので性能低下は限られたものとなり、実用上は問題ない。 During unloading, from the suction completion angle to 1/4 rotation, the outermost chamber 9c, that is, the intermediate pressure compression chamber 37, performs a compression action that is not necessarily required. However, this is a region in which the pressure increase width with respect to the volume change immediately after the completion of inhalation is small, so the performance deterioration is limited, and there is no practical problem.
　高低圧差が設定値を超える条件での運転時は、上述したようにアンロード機構２３０において制御弁３１が背圧室連通路２９３ａ、制御弁小径部外周空間２９３ｃ、低圧空間連通路２９３ｂからなるアンロード経路を閉じ、非アンロード状態となる。 During operation under the condition that the high/low pressure difference exceeds the set value, the control valve 31 in the unload mechanism 230 includes the back pressure chamber communication passage 293a, the control valve small diameter outer peripheral space 293c, and the low pressure space communication passage 293b as described above. The load path is closed and the unload state is entered.
　また、非アンロードで低圧縮比の運転時に背圧室２９１ｂに連通する中間圧圧縮室３７の圧力が吐出圧を上回ると、リリーフ弁２６がその弾性力に逆らって持ち上げられる。揺動スクロール１２が吸入完了角から１回転偏心旋回運動し、更に連通角に到達するまでの間に、中間圧圧縮室３７である第２室９ｂ内の圧力が吐出圧を上回ると、リリーフ弁２６がその弾性力に逆らって持ち上げられる。これにより、背圧室２９１ｂの流体がリリーフポート２９５から高圧空間２１１内にリリーフされ、過圧縮損失が低減される。 Also, when the pressure in the intermediate pressure compression chamber 37 communicating with the back pressure chamber 291b exceeds the discharge pressure during non-unloading and low compression ratio operation, the relief valve 26 is lifted against its elastic force. If the pressure in the second chamber 9b, which is the intermediate pressure compression chamber 37, exceeds the discharge pressure before the orbiting scroll 12 makes one rotation eccentric orbital movement from the suction completion angle and further reaches the communication angle, the relief valve is released. 26 is lifted against its elastic force. Accordingly, the fluid in the back pressure chamber 291b is relieved from the relief port 295 into the high pressure space 211, and the overcompression loss is reduced.
　以上に説明した過圧縮リリーフとアンロードの何れの場合も、圧縮室９から直接、高圧空間２１１又は低圧空間２１２に流体を排出するのではなく、背圧室２９１ｂを経由して排出するため、背圧室２９１ｂとその前後の流路とがバッファとなる。これにより、圧縮室９内の圧力変動と、過圧縮リリーフ及びアンロード側の脈動とが、ダイレクトに影響し合うことのない安定した過圧縮損失の低減及び容量制御を実現できる。 In both cases of overcompression relief and unloading described above, the fluid is not discharged directly from the compression chamber 9 to the high pressure space 211 or the low pressure space 212, but is discharged via the back pressure chamber 291b. The back pressure chamber 291b and the flow passages before and after it serve as a buffer. As a result, it is possible to realize stable reduction of overcompression loss and capacity control in which pressure fluctuations in the compression chamber 9 and pulsations on the overcompression relief and unload side do not directly influence each other.
　また、アンロード時、抽気孔１１２が開口している圧縮室９の実質的な吸入完了は、抽気孔１１２が開口しなくなったタイミングとなる。このため、アンロード時の圧縮室９の昇圧部分の圧力及びその受圧面積である圧縮室９の平面投影面積は、非アンロード時よりも減少する。したがって、アンロード時は、固定スクロール１１を軸方向上向きに押し上げて揺動スクロール１２から引き離そうとする力が、非アンロード時よりも減少する。このため、固定スクロール１１に作用する軸方向下向きの力が、軸方向上向きの力に比べて過剰とならないように、アンロード時は非アンロード時よりも背圧力を減らす必要がある。 Also, during unloading, the substantial suction completion of the compression chamber 9 in which the extraction hole 112 is opened is the timing at which the extraction hole 112 does not open. Therefore, the pressure of the pressure rising portion of the compression chamber 9 at the time of unloading and the planar projected area of the compression chamber 9 which is the pressure receiving area thereof are smaller than those at the time of unloading. Therefore, at the time of unloading, the force that pushes the fixed scroll 11 upward in the axial direction to separate it from the orbiting scroll 12 is smaller than that at the time of non-unloading. Therefore, it is necessary to reduce the back pressure during unloading than during non-unloading so that the axially downward force acting on the fixed scroll 11 does not become excessive as compared with the axially upward force.
　しかし、何らかの理由により背圧室２９１ｂに中間圧が残った状態でアンロードとなると、固定スクロール１１を揺動スクロール１２に押し付けようとする背圧力が減少しないことになる。この場合、軸方向コンプライアントの押付け力、つまり軸方向下向きの力が過剰となり、摺動損失の増大から歯先の焼付きに至るといった不具合が生じる可能性がある。 However, if the back pressure chamber 291b is unloaded for some reason while the intermediate pressure remains, the back pressure for pressing the fixed scroll 11 against the orbiting scroll 12 will not decrease. In this case, the pressing force of the axial compliant, that is, the downward force in the axial direction becomes excessive, which may cause a problem such as an increase in sliding loss and seizure of the tooth tips.
　本実施の形態１では、アンロードと背圧室２９１ｂの圧力開放とが同じ制御弁３１という要素によって行われるため、背圧室２９１ｂに中間圧が残った状態でアンロードになることがなく、このような不具合が生じることが避けられる。 In the first embodiment, since the unloading and the pressure release of the back pressure chamber 291b are performed by the same element, that is, the control valve 31, the unloading does not occur when the intermediate pressure remains in the back pressure chamber 291b. It is possible to avoid such a problem.
　以上説明したように、本実施の形態１は、セパレータ２９にアンロード孔２９６が形成されており、制御弁３１がアンロード孔２９６内で移動することでアンロード経路を開閉するアンロード機構２３０を備えている。制御弁３１の位置を移動させるために制御弁３１の両端面に作用させる低圧及び高圧を、密閉容器２１内から導く構成とし、アンロードに係る構造が、密閉容器２１内で完結している。このため、アンロードを、密閉容器２１外から圧縮機構部１０へ配管接続することなく行うことができる。したがって、従来のように圧縮機構部１０と密閉容器２１外の配管とを接続したり、その配管に弁類を備えたりする必要が無く、コストの低減を図ることができる。 As described above, in the first embodiment, the unload hole 296 is formed in the separator 29, and the unload mechanism 230 that opens and closes the unload path by moving the control valve 31 in the unload hole 296. Is equipped with. The low pressure and the high pressure applied to both end surfaces of the control valve 31 to move the position of the control valve 31 are guided from inside the closed container 21, and the structure related to unloading is completed inside the closed container 21. Therefore, the unloading can be performed without connecting the outside of the closed container 21 to the compression mechanism unit 10 by piping. Therefore, it is not necessary to connect the compression mechanism unit 10 to the pipe outside the closed container 21 or to provide the pipe with valves as in the conventional case, and the cost can be reduced.
　また、本実施の形態１では、アンロードと非アンロードとの切り替えが運転条件に応じて自動的に切り替えられる。つまり、非アンロードからアンロードへの移行及びアンロードから非アンロードへの復帰が自動で行われる。このため、外部からの切り替え操作のための配管接続によるコスト増大を避けることができ、また、切り替え弁等の操作が不要である。これにより、幅広い容量で効率の良いスクロール圧縮機１を得ることができる。 In addition, in the first embodiment, switching between unloading and non-unloading is automatically switched according to operating conditions. That is, the transition from non-unload to unload and the return from unload to non-unload are automatically performed. Therefore, it is possible to avoid an increase in cost due to the pipe connection for the switching operation from the outside, and the operation of the switching valve or the like is unnecessary. As a result, the scroll compressor 1 having a wide capacity and high efficiency can be obtained.
　本実施の形態１において、制御弁３１は、高低圧差が予め設定した設定値を超えるとき、アンロード経路を閉、高低圧差が設定値以下のとき、アンロード経路を開とする。このように、高低圧差に応じてアンロードと非アンロードとを切り替えることができる。 In the first embodiment, the control valve 31 closes the unload path when the high/low pressure difference exceeds a preset value, and opens the unload path when the high/low pressure difference is less than or equal to the preset value. In this way, unloading and non-unloading can be switched according to the high/low pressure difference.
　本実施の形態１において、アンロード機構２３０は、制御弁３１を高圧側に付勢して、制御弁３１を、アンロード経路を開放する位置に位置させる弾性体３２を備えている。制御弁３１は、運転条件に応じて変化する高低圧差に応じた差圧力が弾性体３２の付勢力を上回ることで、アンロード経路を開放する位置から閉じる位置に移動する。これにより、非アンロードからアンロードへの移行及びアンロードから非アンロードへの復帰を自動で行える。 In the first embodiment, the unload mechanism 230 includes the elastic body 32 that urges the control valve 31 to the high pressure side to position the control valve 31 at the position where the unload path is opened. The control valve 31 moves from the position where the unloading path is opened to the position where the unloading path is closed when the differential pressure corresponding to the high/low pressure difference that changes according to the operating conditions exceeds the biasing force of the elastic body 32. As a result, the transition from non-unload to unload and the return from unload to non-unload can be performed automatically.
　本実施の形態１において、アンロード孔２９６はセパレータ２９に形成されている。アンロード経路は、背圧室２９１ｂに一端が開口する背圧室連通路２９３ａと、低圧空間２１２に一端が開口する低圧空間連通路２９３ｂと、制御弁小径部外周空間２９３ｃとから構成されている。セパレータ２９には、制御弁３１の一方の端面３１ｂが面する空間に低圧空間２１２の低圧を導入する低圧導入孔２９４ｂと、制御弁３１の他方の端面３１ａが面する空間に高圧空間２１１の高圧を導入する高圧導入孔２９４ａとが形成されている。この構造により、制御弁３１の両端面に密閉容器２１内から高低圧を作用させることができる。 In the first embodiment, the unload hole 296 is formed in the separator 29. The unloading path includes a back pressure chamber communication passage 293a having one end opened to the back pressure chamber 291b, a low pressure space communication passage 293b having one end opened to the low pressure space 212, and a control valve small diameter portion outer peripheral space 293c. .. In the separator 29, a low pressure introduction hole 294b for introducing the low pressure of the low pressure space 212 into a space facing one end surface 31b of the control valve 31 and a high pressure space of the high pressure space 211 in a space facing the other end surface 31a of the control valve 31. And a high pressure introducing hole 294a for introducing With this structure, high pressure and low pressure can be applied to both end surfaces of the control valve 31 from inside the closed container 21.
　また、本実施の形態１では、リリーフポート２９５及びアンロード経路がセパレータ２９に形成され、それぞれが背圧室２９１ｂに連通し、背圧室２９１ｂが、固定スクロール１１に設けた抽気孔１１２を介して中間圧圧縮室３７に連通している。リリーフ機構２２０とアンロード機構２３０とで共通の抽気孔１１２が中間圧圧縮室３７に開口する構成により、過圧縮リリーフ及びアンロードの何れにおいても、圧縮室９に開口するポートは抽気孔１１２のみである。したがって、過圧縮リリーフ及びアンロードの各々について、独立のポートが必要であった従来の構成に比べて、圧縮室９に開口するポート数を最少とすることができる。 In addition, in the first embodiment, the relief port 295 and the unloading path are formed in the separator 29, and each communicates with the back pressure chamber 291b, and the back pressure chamber 291b passes through the bleed hole 112 provided in the fixed scroll 11. And communicates with the intermediate pressure compression chamber 37. With the configuration in which the common bleed hole 112 of the relief mechanism 220 and the unload mechanism 230 is opened to the intermediate pressure compression chamber 37, the bleed hole 112 is the only port opened to the compression chamber 9 in both overcompression relief and unloading. Is. Therefore, the number of ports opened to the compression chamber 9 can be minimized as compared with the conventional configuration in which an independent port is required for each of the overcompression relief and the unload.
　本実施の形態１では、吐出室２９１ａ及び背圧室２９１ｂの圧力による固定スクロール１１の揺動スクロール１２側への押圧により、歯先すきまを最小化でき、圧縮効率を高効率化することができる。また、背圧室からの高圧側リリーフによる低圧縮比条件での過圧縮損失低減と併せて、幅広い条件及び容量範囲で高効率のスクロール圧縮機を得ることが可能となる。 In the first embodiment, the pressure in the discharge chamber 291a and the back pressure chamber 291b presses the fixed scroll 11 toward the oscillating scroll 12 to minimize the tooth gap, thereby improving the compression efficiency. .. In addition, it is possible to obtain a highly efficient scroll compressor under a wide range of conditions and capacity ranges, in addition to reducing overcompression loss under low compression ratio conditions due to the high pressure side relief from the back pressure chamber.
　なお、本実施の形態１では、制御弁３１で背圧室連通路２９３ａを塞ぐことで背圧室連通路２９３ａ、制御弁小径部外周空間２９３ｃ、低圧空間連通路２９３ｂからなるアンロード経路を閉じるようにしているが、低圧空間連通路２９３ｂを塞ぐことでアンロード経路を閉じるようにしてもよい。 In the first embodiment, the control valve 31 closes the back pressure chamber communication passage 293a to close the unload path including the back pressure chamber communication passage 293a, the control valve small diameter outer peripheral space 293c, and the low pressure space communication passage 293b. However, the unloading path may be closed by closing the low pressure space communication passage 293b.
実施の形態２．
　上記実施の形態１では、アンロード孔２９６がセパレータ２９に形成されていたが、実施の形態２では、固定スクロール１１にアンロード孔１１７が形成されている。以下、実施の形態２が実施の形態１と異なる点を中心に説明する。 Embodiment 2.
Although the unload hole 296 is formed in the separator 29 in the first embodiment, the unload hole 117 is formed in the fixed scroll 11 in the second embodiment. Hereinafter, the points of difference between the second embodiment and the first embodiment will be mainly described.
　図７は、本発明の実施の形態２によるスクロール圧縮機の縦断面模式図である。図８は、本発明の実施の形態２によるスクロール圧縮機の要部断面模式図である。図８において点線で囲った部分がアンロード機構２３０に相当する。図９は、本発明の実施の形態２によるスクロール圧縮機のアンロード時のアンロード機構の拡大模式図である。図１０は、本発明の実施の形態２によるスクロール圧縮機の非アンロード時のアンロード機構の拡大模式図である。図８～図１０において操作圧導入横孔１２４及び受圧ポケット１１５に示した矢印は油圧の向きを示している。 FIG. 7 is a schematic vertical sectional view of a scroll compressor according to the second embodiment of the present invention. FIG. 8 is a schematic sectional view of essential parts of a scroll compressor according to Embodiment 2 of the present invention. The portion surrounded by the dotted line in FIG. 8 corresponds to the unload mechanism 230. FIG. 9 is an enlarged schematic view of an unload mechanism during unloading of the scroll compressor according to the second embodiment of the present invention. FIG. 10 is an enlarged schematic view of the unload mechanism of the scroll compressor according to the second embodiment of the present invention when it is not unloading. 8 to 10, the arrows shown in the operating pressure introducing lateral hole 124 and the pressure receiving pocket 115 indicate the direction of hydraulic pressure.
　図１１は、図７の固定スクロールを渦巻側から見た図である。図１２は、図７の固定スクロールを反渦巻側から見た図である。図１３は、図７の揺動スクロールを渦巻側から見た図である。図１４は、図７の揺動スクロールを反渦巻側から見た図である。 FIG. 11 is a view of the fixed scroll of FIG. 7 viewed from the spiral side. FIG. 12 is a view of the fixed scroll of FIG. 7 viewed from the side opposite to the spiral. FIG. 13 is a view of the orbiting scroll of FIG. 7 viewed from the spiral side. FIG. 14 is a view of the orbiting scroll of FIG. 7 viewed from the side opposite to the spiral.
　図１５は、本発明の実施の形態２によるスクロール圧縮機のアンロード時の渦巻組み合わせ状態を示す平面形状図である。図１６は、図１５のアンロード機構の拡大形状図である。図１７は、図７のアンロード機構の制御弁の形状図である。図１８は、図７のアンロード機構のばね座３６の形状図である。図１９は、図７のアンロード機構のプラグの形状図である。図２０は、本発明の実施の形態２によるスクロール圧縮機の非アンロード時の渦巻組み合わせ状態を示す平面形状図である。図２１は、図２０のアンロード機構の拡大形状図である。 FIG. 15 is a plan view showing a spiral combined state when the scroll compressor according to the second embodiment of the present invention is unloaded. FIG. 16 is an enlarged shape view of the unload mechanism of FIG. FIG. 17 is a shape view of the control valve of the unload mechanism of FIG. 7. FIG. 18 is a shape view of the spring seat 36 of the unload mechanism of FIG. 7. FIG. 19 is a shape view of the plug of the unload mechanism of FIG. 7. FIG. 20 is a plan view showing a spiral combined state when the scroll compressor according to the second embodiment of the present invention is not unloaded. 21 is an enlarged shape view of the unload mechanism of FIG.
　本実施の形態２のアンロード機構２３０は、スプール状の制御弁３１と、ばね等の弾性体３２と、ばね座３６とが、固定スクロール１１の固定台板１１ａに形成されたアンロード孔１１７に配置されている。アンロード孔１１７は、図１１及び図１２に示すように、固定スクロール１１の固定台板１１ａの外周から渦巻中心を通過せずに固定台板１１ａを貫通して形成されている。アンロード孔１１７の一端側は図１６に示すようにプラグ３５ａで塞がれ、他端側はばね座３６で塞がれている。 In the unload mechanism 230 of the second embodiment, the spool-shaped control valve 31, the elastic body 32 such as a spring, and the spring seat 36 are formed in the fixed base plate 11 a of the fixed scroll 11 and the unload hole 117 is formed. It is located in. As shown in FIGS. 11 and 12, the unload hole 117 is formed from the outer periphery of the fixed base plate 11a of the fixed scroll 11 so as to pass through the fixed base plate 11a without passing through the spiral center. As shown in FIG. 16, one end side of the unload hole 117 is closed by a plug 35a, and the other end side is closed by a spring seat 36.
　アンロード機構２３０は、中間圧圧縮室３７内の流体を、抽気孔１１２と、背圧室２９１ｂと、固定台板１１ａに形成されたアンロード孔１１７に構成されたアンロード経路とを介して低圧空間２１２にバイパスすることで、アンロードを行う。アンロード経路は、背圧室２９１ｂに一端が開口する背圧室連通路１１３と、低圧空間２１２に一端が開口する低圧空間連通路１１４と、背圧室連通路１１３の他端と低圧空間連通路１１４の他端とを連通する制御弁小径部外周空間１２０とから構成される。制御弁小径部外周空間１２０は、アンロード孔１１７の一部である。 The unload mechanism 230 causes the fluid in the intermediate pressure compression chamber 37 to flow through the bleed hole 112, the back pressure chamber 291b, and the unload path configured in the unload hole 117 formed in the fixed base plate 11a. Unloading is performed by bypassing the low-pressure space 212. The unload path includes a back pressure chamber communication passage 113 having one end opened to the back pressure chamber 291b, a low pressure space communication passage 114 having one end opened to the low pressure space 212, and the other end of the back pressure chamber communication passage 113 to the low pressure space communication passage 113. It is composed of a control valve small diameter portion outer peripheral space 120 communicating with the other end of the passage 114. The control valve small-diameter portion outer peripheral space 120 is a part of the unload hole 117.
　制御弁３１は、アンロード孔１１７にスライド自在に配置されて、一方の端面３１ａとばね座３６との間に配置された弾性体３２によってアンロード孔１１７のプラグ３５ａ方向（図１６の左方）に押圧されている。これにより、制御弁３１は、他方の端面３１ｂがプラグ３５ａの先端に当接した状態でアンロード孔１１７内に配置されている。プラグ３５ａは図１６及び図１９に示すように先端部が後方のアンロード孔１１７閉止部よりも小径に形成されており、固定スクロール１１に形成されている後述の操作圧導入孔１１６を塞がないようになっている。なお、図７～図９では、プラグ３５ａの形状等が上記の説明と異なるが、図７～図９は模式図であって、図１９に示した形状も具体的形状の一例に過ぎない。 The control valve 31 is slidably arranged in the unload hole 117, and an elastic body 32 arranged between the one end face 31a and the spring seat 36 causes the control valve 31 to move toward the plug 35a of the unload hole 117 (left side in FIG. 16). ) Is pressed. As a result, the control valve 31 is arranged in the unload hole 117 with the other end surface 31b in contact with the tip of the plug 35a. As shown in FIGS. 16 and 19, the plug 35a has a tip portion formed to have a smaller diameter than the closing portion of the unload hole 117 at the rear, and closes an operation pressure introducing hole 116, which will be described later, formed in the fixed scroll 11. It is supposed to not. 7 to 9, the shape and the like of the plug 35a is different from the above description, but FIGS. 7 to 9 are schematic views, and the shape shown in FIG. 19 is also an example of a specific shape.
　ばね座３６は図１８に示すように、先端部がアンロード孔１１７の径よりも小径に形成され、その小径部分外周とアンロード孔１１７内面の間に弾性体３２が挿入される。ばね座３６の中心部には均圧用の細孔３６ａが貫通している。 As shown in FIG. 18, the spring seat 36 has a tip portion formed to have a diameter smaller than the diameter of the unload hole 117, and the elastic body 32 is inserted between the outer periphery of the small diameter portion and the inner surface of the unload hole 117. A hole 36a for equalizing pressure penetrates through the center of the spring seat 36.
　固定スクロール１１の固定台板１１ａ及び固定渦巻歯１１ｂには、固定渦巻歯１１ｂの立設方向に貫通する操作圧導入孔１１６が形成されている。操作圧導入孔１１６の一端はアンロード孔１１７に、制御弁３１のプラグ３５ａ側の端面３１ｂが面する操作圧導入空間２９８で、開口している。操作圧導入孔１１６の他端は、固定渦巻歯１１ｂの歯先面に形成された円形で凹状の受圧ポケット１１５に開口している。受圧ポケット１１５の径は、後述の操作圧導入縦孔１２５の揺動軌跡を包含できる径に設定されており、受圧ポケット１１５は操作圧導入縦孔１２５に常に連通している。 The fixed base plate 11a and the fixed spiral tooth 11b of the fixed scroll 11 are formed with an operation pressure introducing hole 116 penetrating in the standing direction of the fixed spiral tooth 11b. One end of the operating pressure introducing hole 116 opens to the unloading hole 117 in the operating pressure introducing space 298 facing the end surface 31b of the control valve 31 on the plug 35a side. The other end of the operation pressure introducing hole 116 opens into a circular concave pressure receiving pocket 115 formed on the tooth crest surface of the fixed spiral tooth 11b. The diameter of the pressure receiving pocket 115 is set to a diameter that can include the swing locus of the operation pressure introducing vertical hole 125 described later, and the pressure receiving pocket 115 is always in communication with the operation pressure introducing vertical hole 125.
　揺動スクロール１２の揺動台板１２ａには、図８及び図１４に示すように揺動スクロール１２のボス部１２１内から給油圧を固定スクロール１１の受圧ポケット１１５に導く操作圧導入横孔１２４及び操作圧導入縦孔１２５が形成されている。操作圧導入横孔１２４は、揺動台板１２ａの平面方向横穴であり、操作圧導入縦孔１２５は、操作圧導入横孔１２４から縦に延びて揺動台板１２ａ上面に開口する縦穴である。 As shown in FIGS. 8 and 14, the rocking base plate 12 a of the rocking scroll 12 has an operating pressure introducing lateral hole 124 for guiding the hydraulic pressure from the boss portion 121 of the rocking scroll 12 to the pressure receiving pocket 115 of the fixed scroll 11. Also, an operating pressure introducing vertical hole 125 is formed. The operating pressure introducing lateral hole 124 is a lateral hole in the plane direction of the rocking base plate 12a, and the operating pressure introducing vertical hole 125 is a vertical hole extending vertically from the operating pressure introducing lateral hole 124 and opening on the upper surface of the rocking base plate 12a. is there.
　軸１５の回転により給油ポンプ２７が駆動されて潤滑油２２が給油孔１５２を上昇し、ボス部１２１の上部内側に供給される。ボス部１２１に供給された潤滑油２２は、操作圧導入横孔１２４、操作圧導入縦孔１２５、受圧ポケット１１５、操作圧導入孔１１６を経てアンロード孔１１７に供給される。これにより、制御弁３１の操作圧導入空間２９８側の端面３１ｂに、揺動スクロール１２のボス部１２１内上部から下流側の抵抗と、給油ポンプ２７のポンプ圧とに応じた油圧が作用する。 The rotation of the shaft 15 drives the oil supply pump 27 to move the lubricating oil 22 up through the oil supply hole 152 and be supplied to the inside of the upper portion of the boss 121. The lubricating oil 22 supplied to the boss portion 121 is supplied to the unload hole 117 via the operating pressure introducing lateral hole 124, the operating pressure introducing vertical hole 125, the pressure receiving pocket 115, and the operating pressure introducing hole 116. As a result, the hydraulic pressure according to the resistance from the upper part inside the boss 121 of the orbiting scroll 12 to the downstream side and the pump pressure of the oil supply pump 27 acts on the end surface 31b of the control valve 31 on the operating pressure introducing space 298 side.
　制御弁３１の操作圧導入空間２９８と反対側の端面３１ａには常に低圧が作用している。これは、制御弁３１の端面３１ａが面する空間が、ばね座３６に形成された細孔３６ａによって低圧空間２１２と均圧していることに依る。 A low pressure is constantly acting on the end surface 31a of the control valve 31 opposite to the operation pressure introducing space 298. This is because the space facing the end surface 31a of the control valve 31 is pressure-equalized with the low-pressure space 212 by the pores 36a formed in the spring seat 36.
　スクロール圧縮機１が比較的低速で運転される、つまり、軸１５の回転数が設定回転数以下であるとき、給油ポンプ２７の給油量は少なく、給油圧は低い。したがって、制御弁３１の操作圧導入空間２９８側の端面３１ｂへの作用圧由来の力よりも、操作圧導入空間２９８と反対側の端面３１ａへの作用圧由来の力と弾性体３２の弾性力の合計の方が上回る。この場合、図１５及び図１６に示すように、制御弁３１がプラグ３５ａ側に移動してプラグ３５ａの先端に当接する。これにより、図９に示すように背圧室連通路１１３と、制御弁小径部外周空間１２０と、低圧空間連通路１１４とが連通し、アンロード経路が開放される。 When the scroll compressor 1 is operated at a relatively low speed, that is, when the rotation speed of the shaft 15 is less than or equal to the set rotation speed, the oil supply amount of the oil supply pump 27 is small and the oil supply pressure is low. Therefore, the force derived from the acting pressure to the end surface 31a opposite to the operation pressure introducing space 298 and the elastic force of the elastic body 32 are smaller than the force derived from the acting pressure to the end surface 31b of the control valve 31 on the operating pressure introducing space 298 side. Is more than the total. In this case, as shown in FIGS. 15 and 16, the control valve 31 moves to the plug 35a side and contacts the tip of the plug 35a. As a result, as shown in FIG. 9, the back pressure chamber communication passage 113, the control valve small diameter portion outer peripheral space 120, and the low pressure space communication passage 114 communicate with each other, and the unloading passage is opened.
　その結果、中間圧圧縮室３７内の流体が、抽気孔１１２、背圧室２９１ｂ、背圧室連通路１１３、制御弁小径部外周空間１２０、低圧空間連通路１１４の順に通過して低圧空間２１２に排出される。このため、中間圧圧縮室３７が抽気孔１１２に連通している間、言い換えれば中間圧圧縮室３７の外周側シール形成点が抽気孔１１２を通過するまでの間は、中間圧圧縮室３７では圧縮が為されず、容量制御、すなわちアンロード状態となる。 As a result, the fluid in the intermediate pressure compression chamber 37 passes through the extraction hole 112, the back pressure chamber 291b, the back pressure chamber communication passage 113, the control valve small-diameter portion outer peripheral space 120, and the low pressure space communication passage 114 in this order, and the low pressure space 212. Is discharged to. Therefore, while the intermediate pressure compression chamber 37 communicates with the extraction hole 112, in other words, until the outer peripheral side seal forming point of the intermediate pressure compression chamber 37 passes through the extraction hole 112, the intermediate pressure compression chamber 37 The compression is not performed and the capacity is controlled, that is, the unload state is set.
　軸１５の回転数が設定回転数を超えると、給油ポンプ２７の給油量が増大し、給油圧が上昇する。これにより、制御弁３１の操作圧導入空間２９８側の端面３１ｂへの作用圧由来の力が、操作圧導入空間２９８と反対側の端面３１ａへの作用圧由来の力と弾性体３２の弾性力の合計を上回る。このとき、図１０、図２０及び図２１に示すように、制御弁３１がプラグ３５ａから離れて弾性体３２を圧縮する方向に移動し、図１０に示すように低圧空間連通路１１４が制御弁３１によって塞がれる。これにより、背圧室連通路１１３、制御弁小径部外周空間120及び低圧空間連通路１１４からなるアンロード経路が閉じられ、アンロード状態から非アンロード状態に切り替わる。 When the rotation speed of the shaft 15 exceeds the set rotation speed, the oil supply amount of the oil supply pump 27 increases and the oil supply pressure increases. Accordingly, the force derived from the acting pressure on the end surface 31b of the control valve 31 on the operating pressure introducing space 298 side is the force derived from the acting pressure on the end surface 31a on the side opposite to the operating pressure introducing space 298 and the elastic force of the elastic body 32. Exceeds the total of. At this time, as shown in FIGS. 10, 20, and 21, the control valve 31 moves away from the plug 35a in the direction of compressing the elastic body 32, and as shown in FIG. Blocked by 31. As a result, the unloading path formed by the back pressure chamber communication passage 113, the control valve small diameter portion outer peripheral space 120 and the low pressure space communication passage 114 is closed, and the unloading state is switched to the unloading state.
　このようにアンロード機構２３０は、スクロール圧縮機１の運転回転数に応じて制御弁３１の両端面に作用する圧力が変化することで、制御弁３１が自動的に移動し、アンロードと非アンロードとを自動的に切り替える。アンロードと非アンロードとの切り替え点となる上記設定回転数は、制御弁３１の両端面に作用する圧力を考慮して弾性体３２のばね定数を選択することにより、所望の値に調整することが可能である。 As described above, in the unload mechanism 230, the pressure acting on both end surfaces of the control valve 31 changes according to the operating speed of the scroll compressor 1, so that the control valve 31 automatically moves and the unloading and non-loading operations are performed. Automatically switch between unload and. The set rotational speed, which is a switching point between unloading and non-unloading, is adjusted to a desired value by selecting the spring constant of the elastic body 32 in consideration of the pressure acting on both end surfaces of the control valve 31. It is possible.
　アンロード機構２３０は、制御弁３１の一方の端面３１ａ及び他方の端面３１ｂに作用させる低圧及び操作圧である油圧を、密閉容器２１内から導いている。つまり、アンロード機構２３０は、密閉容器２１内で完結した構造であり、密閉容器２１外から圧縮機構部１０へ接続する配管等が不要である。 The unload mechanism 230 guides, from the inside of the closed container 21, the hydraulic pressure that is the low pressure and the operating pressure applied to the one end surface 31 a and the other end surface 31 b of the control valve 31. In other words, the unloading mechanism 230 has a structure that is completed inside the closed container 21, and does not require piping or the like that connects the outside of the closed container 21 to the compression mechanism unit 10.
　以上説明したように、本実施の形態２によれば、実施の形態１と同様に、軸方向押付による歯先すきまの漏れ損失低減、高圧側リリーフによる低圧縮比条件での過圧縮損失低減の効果を得られる。また、本実施の形態２によれば実施の形態１と同様に、密閉容器内で完結したアンロード機構による容量制御の、圧縮室に開口するポート数最少での構成、圧縮室内の圧力変動とリリーフ側及びアンロード側の脈動とが影響し合わないことによる安定的動作、を実現できる。また、実施の形態２によれば実施の形態１と同様に、アンロードと背圧室の圧力開放とが制御弁という単一要素の動作によって行われるため信頼性が高い、広運転範囲、高効率のスクロール圧縮機を、低コストで得ることができる。 As described above, according to the second embodiment, similarly to the first embodiment, the reduction of the leakage loss of the tooth tip clearance due to the axial pressing and the reduction of the overcompression loss under the low compression ratio condition by the high pressure side relief can be achieved. You can get the effect. Further, according to the second embodiment, similarly to the first embodiment, the capacity control by the unloading mechanism completed in the closed container, the configuration with the minimum number of ports opening to the compression chamber, the pressure fluctuation in the compression chamber, and the like. A stable operation can be realized because the pulsations on the relief side and the unload side do not affect each other. Further, according to the second embodiment, as in the first embodiment, the unloading and the pressure release of the back pressure chamber are performed by the operation of the single element of the control valve, which is highly reliable, has a wide operating range, and has a high operating range. An efficient scroll compressor can be obtained at low cost.
　また、本実施の形態２では、回転数に依存した油圧をアンロード機構の操作圧として利用することで実施の形態１に比べて、容量制御のより広範囲での利用が可能となる。空調用途の部分負荷条件では、負荷率が下がる程、より低圧縮比、より低差圧となる傾向がある。負荷率低下に運転回転数を減じることだけで対応しようとすると、低速運転に起因する漏れ損失の相対的増大を招くため、アンロード運転により非アンロード運転時よりも最低回転数を高く保つことが有効である。 Further, in the second embodiment, by using the hydraulic pressure depending on the rotation speed as the operating pressure of the unload mechanism, the capacity control can be used in a wider range as compared with the first embodiment. Under partial load conditions for air conditioning applications, the lower the load factor, the lower the compression ratio and the lower the differential pressure. If you try to deal with the reduction of the load factor only by reducing the operating speed, the relative increase of the leakage loss due to the low speed operation will occur.Therefore, keep the minimum speed higher by unloading the operation than when not unloading. Is effective.
　高低圧は冷凍サイクルの高温熱源と低温熱源の温度差に依存するので、上述の部分負荷条件のように温度差小と空調負荷減が相関を持っている場合は、実施の形態１の高低圧差依存でアンロード運転に移行するような機構で有効である。これに対して、例えば１台の室外機と多数の室内機で構成されるシステムでは、高低圧差に依らずアンロードした方が良い場合がある。高外気温時に室内機１台のみの冷房運転を行なうような場合、室内外の気温差に依存する高低圧差は大きくて、室内機の運転台数減により空調負荷が室外機容量に比して小さくなるので、アンロードするのが望ましい。 Since the high/low pressure depends on the temperature difference between the high temperature heat source and the low temperature heat source of the refrigeration cycle, when the small temperature difference and the air conditioning load decrease are correlated as in the partial load condition described above, the high/low pressure difference of the first embodiment is used. This is effective for a mechanism that shifts to unload operation depending on the dependency. On the other hand, for example, in a system including one outdoor unit and many indoor units, it may be better to unload regardless of the high/low pressure difference. When performing cooling operation of only one indoor unit when the outdoor temperature is high, the high/low pressure difference depending on the indoor/outdoor temperature difference is large, and the air conditioning load is smaller than the outdoor unit capacity due to the decrease in the number of operating indoor units. Therefore, it is desirable to unload.
　アンロードせずに運転回転数減のみで、室内機稼働台数極少に対応した室外機容量制御を行なうと、圧縮機は低速運転となり前述のように漏れ損失増大による性能低下を招く。また、差圧は温度差に起因するので圧縮機構の各部材に作用する差圧由来の荷重（例えば軸受負荷）が小さくなるわけではないので、低速高差圧運転による軸受焼き付き等を避けるために限界を超えた低回転数運転は出来ない。つまり、差圧依存で起動するアンロード機構が有効ではない運転条件が存在する。 ⑦ If the outdoor unit capacity control that corresponds to the minimum number of operating indoor units is performed by only reducing the operating speed without unloading, the compressor will operate at low speed, resulting in a decrease in performance due to increased leakage loss as described above. Further, since the differential pressure is caused by the temperature difference, the load (for example, bearing load) derived from the differential pressure that acts on each member of the compression mechanism does not become small. Therefore, in order to avoid the seizure of the bearing due to the low speed high differential pressure operation, etc. Low speed operation beyond the limit cannot be performed. That is, there are operating conditions in which the unloading mechanism that starts depending on the differential pressure is not effective.
　実施の形態２の回転数依存でのアンロード運転移行によれば、低差圧ではないがシステムの容量に比して必要な冷凍能力が小さい、という場合に対応するときにも著しい低回転数運転を回避することが可能となるという効果がある。 According to the rotation speed-dependent unloading operation shift according to the second embodiment, a significantly low rotation speed is achieved even when the case where the required refrigerating capacity is smaller than the capacity of the system is not low differential pressure. There is an effect that it becomes possible to avoid driving.
　本実施の形態２のスクロール圧縮機１は、軸１５の下端部に給油ポンプ２７を備える。給油ポンプ２７は、軸１５の回転により、密閉容器２１の下部に溜められた潤滑油２２を、軸１５に貫通して設けられた給油孔１５２を介して圧縮機構部１０に供給する。制御弁３１の操作圧導入空間２９８側の端面３１ｂには、給油ポンプ２７から供給される潤滑油２２の油圧が作用する。また、制御弁３１の操作圧導入空間２９８と反対側の端面３１ａには低圧空間の低圧が作用する。この構成により、運転条件に応じて、制御弁３１の両端面に作用する圧力差が変化し、制御弁３１の位置が移動してアンロード経路の開閉を行うことができる。 The scroll compressor 1 according to the second embodiment includes an oil supply pump 27 at the lower end of the shaft 15. By the rotation of the shaft 15, the oil supply pump 27 supplies the lubricating oil 22 stored in the lower portion of the closed container 21 to the compression mechanism unit 10 through the oil supply hole 152 provided through the shaft 15. The oil pressure of the lubricating oil 22 supplied from the oil supply pump 27 acts on the end surface 31b of the control valve 31 on the operating pressure introducing space 298 side. Further, the low pressure of the low pressure space acts on the end surface 31a of the control valve 31 on the side opposite to the operation pressure introducing space 298. With this configuration, the pressure difference acting on both end surfaces of the control valve 31 changes according to the operating condition, the position of the control valve 31 moves, and the unloading path can be opened and closed.
　本実施の形態２において、制御弁３１は、軸１５の回転数が予め設定した設定回転数を超えるとき、アンロード経路を閉、回転数が設定回転数以下のとき、アンロード経路を開とする。このように、軸１５の回転数に応じてアンロードと非アンロードとを切り替えることができる。 In the second embodiment, the control valve 31 closes the unloading path when the rotation speed of the shaft 15 exceeds a preset setting rotation speed, and opens the unloading path when the rotation speed is less than or equal to the setting rotation speed. To do. In this way, unloading and non-unloading can be switched according to the rotation speed of the shaft 15.
　本実施の形態２において、アンロード孔１１７は固定スクロール１１に形成されている。アンロード経路は、背圧室２９１ｂに一端が開口する背圧室連通路１１３と、低圧空間２１２に一端が開口する低圧空間連通路１１４と、制御弁小径部外周空間１２０とから構成されている。アンロード孔１１７内のばね座３６には、制御弁３１の反操作圧導入空間側である端面３１ａ側に低圧空間２１２の低圧を導入する細孔３６ａが形成されている。また、固定スクロール１１には、制御弁３１の端面３１ｂ側の操作圧導入空間２９８に給油ポンプ２７からの油圧を供給する操作圧導入経路である、受圧ポケット１１５及び操作圧導入孔１１６が形成されている。この構造により、制御弁３１の両端面に密閉容器２１内から低圧及び操作圧である油圧を作用させることができる。 In the second embodiment, the unload hole 117 is formed in the fixed scroll 11. The unloading path is composed of a back pressure chamber communication passage 113 having one end opening to the back pressure chamber 291b, a low pressure space communication passage 114 having one end opening to the low pressure space 212, and a control valve small diameter outer peripheral space 120. .. In the spring seat 36 in the unload hole 117, a pore 36a for introducing the low pressure of the low pressure space 212 is formed on the end surface 31a side of the control valve 31, which is the counter operation pressure introducing space side. Further, the fixed scroll 11 is formed with a pressure receiving pocket 115 and an operation pressure introducing hole 116 which are operation pressure introducing paths for supplying hydraulic pressure from the oil supply pump 27 to the operation pressure introducing space 298 on the end surface 31b side of the control valve 31. ing. With this structure, a low pressure and an operating pressure can be applied to both end faces of the control valve 31 from the inside of the closed container 21.
　なお、本実施の形態２では、制御弁３１で低圧空間連通路１１４を塞ぐことで背圧室連通路１１３、制御弁小径部外周空間１２０、低圧空間連通路１１４からなるアンロード経路を閉じるようにしているが、背圧室連通路１１３を塞ぐことでアンロード経路を閉じるようにしてもよい。 In the second embodiment, the low pressure space communication passage 114 is closed by the control valve 31 to close the unloading passage including the back pressure chamber communication passage 113, the control valve small diameter outer peripheral space 120, and the low pressure space communication passage 114. However, the unloading path may be closed by closing the back pressure chamber communication passage 113.
　１　スクロール圧縮機、９　圧縮室、９ａ　最内室、９ｂ　第２室、９ｃ　最外室、１０　圧縮機構部、１１　固定スクロール、１１ａ　固定台板、１１ｂ　固定渦巻歯、１１ｂａ　巻き終わり部、１１ｂｂ　巻き終わり部、１２　揺動スクロール、１２ａ　揺動台板、１２ｂ　揺動渦巻歯、１３　姿勢規制手段、１４　フレーム、１４ａ　主軸受、１５　軸、１５ａ　偏心部、１６　第１バランサ、１７　第２バランサ、１８　モータ、１８ａ　ステータ、１８ｂ　ロータ、１９　サブフレーム、１９ａ　副軸受、２１　密閉容器、２２　潤滑油、２３　吸入管、２４　吐出管、２５　吐出弁、２５ｂ　吐出弁ストッパ、２６　リリーフ弁、２６ｂ　リリーフ弁ストッパ、２７　給油ポンプ、２８　径方向ガイド部材、２９　セパレータ、２９ａ　凸部、３１　制御弁、３１ａ　端面、３１ｂ　端面、３２　弾性体、３３　シール部材、３４　シール部材、３５ａ　プラグ、３５ｂ　プラグ、３５ｃ　プラグ、３６　ばね座、３６ａ　細孔、３７　中間圧圧縮室、１１１　第１吐出ポート、１１２　抽気孔、１１３　背圧室連通路、１１４　低圧空間連通路、１１５　受圧ポケット、１１６　操作圧導入孔、１１７　アンロード孔、１１８　背圧室内周面、１１９　背圧室外周面、１２０　制御弁小径部外周空間、１２１　ボス部、１２４　操作圧導入横孔、１２５　操作圧導入縦孔、１３０　シール形成点、１５２　給油孔、２１１　高圧空間、２１２　低圧空間、２２０　リリーフ機構、２３０　アンロード機構、２９１ａ　吐出室、２９１ｂ　背圧室、２９２　第２吐出ポート、２９３ａ　背圧室連通路、２９３ｂ　低圧空間連通路、２９３ｃ　制御弁小径部外周空間、２９４ａ　高圧導入孔、２９４ｂ　低圧導入孔、２９５　リリーフポート、２９６　アンロード孔、２９７　低圧導入空間、２９８　操作圧導入空間。 1 scroll compressor, 9 compression chamber, 9a innermost chamber, 9b second chamber, 9c outermost chamber, 10 compression mechanism part, 11 fixed scroll, 11a fixed base plate, 11b fixed spiral tooth, 11ba winding end part, 11bb winding End part, 12 oscillating scroll, 12a oscillating bed plate, 12b oscillating spiral tooth, 13 attitude regulating means, 14 frame, 14a main bearing, 15 shaft, 15a eccentric part, 16 1st balancer, 17 2nd balancer, 18 Motor, 18a stator, 18b rotor, 19 subframe, 19a auxiliary bearing, 21 sealed container, 22 lubricating oil, 23 suction pipe, 24 discharge pipe, 25 discharge valve, 25b discharge valve stopper, 26 relief valve, 26b relief valve stopper, 27 oil pump, 28 radial guide member, 29 separator, 29a convex portion, 31 control valve, 31a end face, 31b end face, 32 elastic body, 33 seal member, 34 seal member, 35a plug, 35b plug, 35c plug, 36 spring Seat, 36a pore, 37 intermediate pressure compression chamber, 111 first discharge port, 112 bleed hole, 113 back pressure chamber communication passage, 114 low pressure space communication passage, 115 pressure receiving pocket, 116 operating pressure introduction hole, 117 unloading hole, 118 back pressure chamber peripheral surface, 119 back pressure chamber outer peripheral surface, 120 control valve small diameter outer peripheral space, 121 boss portion, 124 operating pressure introducing lateral hole, 125 operating pressure introducing vertical hole, 130 seal forming point, 152 oil supply hole, 211 High pressure space, 212 low pressure space, 220 relief mechanism, 230 unload mechanism, 291a discharge chamber, 291b back pressure chamber, 292 second discharge port, 293a back pressure chamber communication passage, 293b low pressure space communication passage, 293c control valve small diameter outer circumference Space, 294a high pressure introduction hole, 294b low pressure introduction hole, 295 relief port, 296 unload hole, 297 low pressure introduction space, 298 operating pressure introduction space.

Claims (9)

  1. 　密閉容器と、
    　前記密閉容器内を高圧空間と低圧空間とに区画するセパレータと、
    　固定スクロール及び揺動スクロールを有し、前記固定スクロール及び前記揺動スクロールを噛み合わせて形成された圧縮室に、前記低圧空間から流体を吸入して圧縮し、前記高圧空間に吐出する圧縮機構部と、
    　前記圧縮室内から前記低圧空間へ前記流体をバイパスすることにより、吐出量を制限するアンロードを行うアンロード機構とを備え、
    　前記固定スクロールの前記揺動スクロールとは反対側の端面と前記セパレータとの間には、前記固定スクロールに形成された抽気孔を介して、圧縮途中の前記圧縮室に連通する背圧室が形成され、前記セパレータ又は前記固定スクロールには、前記背圧室と前記低圧空間とを連通するアンロード経路の一部を構成するアンロード孔が形成されており、
    　前記アンロード機構は、
    　前記アンロード孔内での位置が移動することで前記アンロード経路を開閉する制御弁を備え、
    　運転中、前記制御弁の移動方向の一方の端面に前記低圧空間の低圧が作用すると共に、他方の端面に前記密閉容器内から導かれて前記低圧空間よりも高い圧力が作用し、
    　運転条件に応じて、前記制御弁の両端面とに作用する圧力差が変化することで前記制御弁が移動して前記アンロード経路を開閉するスクロール圧縮機。     A closed container,
    A separator that divides the closed container into a high-pressure space and a low-pressure space,
    A compression mechanism unit having a fixed scroll and an orbiting scroll, which sucks and compresses fluid from the low pressure space into a compression chamber formed by meshing the fixed scroll and the orbiting scroll and discharges the fluid into the high pressure space. When,
    By-passing the fluid from the compression chamber to the low-pressure space, an unloading mechanism that performs unloading to limit the discharge amount,
    A back pressure chamber communicating with the compression chamber in the middle of compression is formed between the separator and the end surface of the fixed scroll on the opposite side to the orbiting scroll, and through the extraction hole formed in the fixed scroll. The separator or the fixed scroll has an unload hole forming a part of an unload path communicating the back pressure chamber and the low pressure space,
    The unload mechanism is
    A control valve that opens and closes the unloading path by moving a position in the unloading hole;
    During operation, a low pressure of the low pressure space acts on one end face in the moving direction of the control valve, and a pressure higher than the low pressure space acts on the other end face from the inside of the closed container,
    A scroll compressor that moves the control valve to open and close the unloading path by changing a pressure difference acting on both end surfaces of the control valve according to operating conditions.
  2. 　前記制御弁は、高低圧差が予め設定した設定値を超えるとき、前記アンロード経路を閉、前記圧力差が前記設定値以下のとき、前記アンロード経路を開とする請求項１記載のスクロール圧縮機。 The scroll compression according to claim 1, wherein the control valve closes the unload path when the high-low pressure difference exceeds a preset value, and opens the unload path when the pressure difference is equal to or less than the preset value. Machine.
  3. 　前記アンロード機構は、前記制御弁を高圧側に付勢して、前記制御弁を前記アンロード経路を開放する位置に位置させる弾性体を備え、
    　前記圧力差に応じた差圧力が前記弾性体の付勢力を上回ることで前記制御弁が前記アンロード経路を開く位置から閉じる位置に移動する請求項１記載のスクロール圧縮機。     The unload mechanism includes an elastic body that biases the control valve to a high pressure side to position the control valve at a position where the unload path is opened,
    The scroll compressor according to claim 1, wherein the control valve moves from a position where the unloading path is opened to a position where the unloading path is closed when a differential pressure corresponding to the pressure difference exceeds an urging force of the elastic body.
  4. 　前記アンロード孔は前記セパレータに形成されており、
    　前記アンロード経路は、前記背圧室に一端が開口する背圧室連通路と、前記低圧空間に一端が開口する低圧空間連通路と、前記背圧室連通路の他端と前記低圧空間連通路の他端とを連通する制御弁小径部外周空間とから構成され、
    　前記セパレータには、前記制御弁の前記一方の端面が面する空間に前記低圧空間の低圧を導入する低圧導入孔と、前記制御弁の前記他方の端面が面する空間に前記高圧空間の高圧を導入する高圧導入孔とが形成されている請求項１～請求項３の何れか一項に記載のスクロール圧縮機。     The unload hole is formed in the separator,
    The unload path includes a back pressure chamber communication passage having one end opened to the back pressure chamber, a low pressure space communication passage having one end opened to the low pressure space, and the other end of the back pressure chamber communication passage and the low pressure space communication passage. It is composed of a control valve small diameter part outer peripheral space communicating with the other end of the passage,
    In the separator, a low pressure introduction hole for introducing the low pressure of the low pressure space into a space facing the one end face of the control valve, and a high pressure of the high pressure space in a space facing the other end face of the control valve. The scroll compressor according to any one of claims 1 to 3, wherein a high-pressure introduction hole to be introduced is formed.
  5. 　前記圧縮機構部を駆動する軸と、
    　前記軸の下端部に取り付けられ、前記軸の回転により、前記密閉容器の下部に溜められた潤滑油を、前記軸に貫通して設けられた給油孔を介して前記圧縮機構部に供給する給油ポンプとを備え、
    　前記制御弁の前記他方の端面には、前記給油ポンプから供給される前記潤滑油の給油圧が作用する請求項１～請求項３の何れか一項に記載のスクロール圧縮機。     A shaft for driving the compression mechanism section,
    Lubricating oil that is attached to the lower end of the shaft and that is stored in the lower part of the closed container by rotation of the shaft is supplied to the compression mechanism section through an oiling hole that penetrates the shaft. Equipped with a pump,
    The scroll compressor according to any one of claims 1 to 3, wherein a supply oil pressure of the lubricating oil supplied from the oil supply pump acts on the other end surface of the control valve.
  6. 　前記軸の回転数が予め設定した設定回転数を超えるとき、前記アンロード経路を閉、前記回転数が前記設定回転数以下のとき、前記アンロード経路を開とする請求項５記載のスクロール圧縮機。 The scroll compression according to claim 5, wherein when the rotation speed of the shaft exceeds a preset rotation speed, the unload path is closed, and when the rotation speed is equal to or lower than the preset rotation speed, the unload path is opened. Machine.
  7. 　前記アンロード孔は前記固定スクロールに形成されており、
    　前記アンロード経路は、前記背圧室に一端が開口する背圧室連通路と、前記低圧空間に一端が開口する低圧空間連通路と、前記背圧室連通路の他端と前記低圧空間連通路の他端とを連通する制御弁小径部外周空間とから構成され、
    　前記固定スクロールには、前記制御弁の前記一方の端面が面する空間に前記低圧空間の低圧を導入する低圧導入孔と、前記制御弁の前記他方の端面が面する空間に前記給油ポンプからの前記給油圧を供給する操作圧導入孔とが形成されている請求項５又は請求項６記載のスクロール圧縮機。     The unload hole is formed in the fixed scroll,
    The unload path includes a back pressure chamber communication passage having one end opened to the back pressure chamber, a low pressure space communication passage having one end opened to the low pressure space, and the other end of the back pressure chamber communication passage and the low pressure space communication passage. It is composed of a control valve small diameter part outer peripheral space communicating with the other end of the passage,
    In the fixed scroll, a low pressure introduction hole for introducing the low pressure of the low pressure space into a space facing the one end surface of the control valve, and a space from the oil pump to the space facing the other end surface of the control valve. The scroll compressor according to claim 5 or 6, wherein an operation pressure introducing hole for supplying the hydraulic pressure is formed.
  8. 　前記セパレータには、入口側が前記背圧室に開口し、出口側が前記高圧空間に開口するポートであって、前記圧縮室内において過圧縮となった流体を前記高圧空間へリリーフするリリーフポートが形成されており、前記リリーフポートの出口側に前記リリーフポートを開閉するリリーフ弁を有する請求項１～請求項７の何れか一項に記載のスクロール圧縮機。 The separator has a port having an inlet side opening to the back pressure chamber and an outlet side opening to the high pressure space, and a relief port for relieving an overcompressed fluid in the compression chamber to the high pressure space is formed. The scroll compressor according to any one of claims 1 to 7, further comprising a relief valve that opens and closes the relief port on an outlet side of the relief port.
  9. 　前記固定スクロールの前記揺動スクロールとは反対側の端面と前記セパレータとの間には、前記固定スクロールに形成された第１吐出ポートが開口する吐出室が形成されており、前記セパレータには、入口側が前記吐出室に開口し、出口側が前記高圧空間に開口するポートであって、前記圧縮室内で圧縮された流体を前記高圧空間へ吐出する第２吐出ポートが形成され、前記第２吐出ポートの出口側に前記第２吐出ポートを開閉する吐出弁を有する請求項８記載のスクロール圧縮機。 A discharge chamber in which the first discharge port formed in the fixed scroll is opened is formed between the separator and the end surface of the fixed scroll on the side opposite to the oscillating scroll, and the separator is formed. A second discharge port is formed, which is a port having an inlet side opening to the discharge chamber and an outlet side opening to the high pressure space, for discharging a fluid compressed in the compression chamber to the high pressure space, and the second discharge port. 9. The scroll compressor according to claim 8, further comprising a discharge valve that opens and closes the second discharge port on the outlet side of the scroll compressor.
PCT/JP2018/048052 2018-12-27 2018-12-27 Scroll compressor WO2020136786A1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113606136A (en) * 2021-08-27 2021-11-05 珠海格力电器股份有限公司 Compressor and air conditioner with same

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JPH0763173A (en) * 1993-08-30 1995-03-07 Mitsubishi Heavy Ind Ltd Scroll type hydraulic machine
JPH09177689A (en) * 1995-12-27 1997-07-11 Daikin Ind Ltd Hermetic compressor
JP2002506164A (en) * 1998-03-05 2002-02-26 キャリア・コーポレーション Scroll compressor with combined pressure ratio / pressure difference relief valve
JP2018035748A (en) * 2016-08-31 2018-03-08 ダイキン工業株式会社 Scroll compressor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0763173A (en) * 1993-08-30 1995-03-07 Mitsubishi Heavy Ind Ltd Scroll type hydraulic machine
JPH09177689A (en) * 1995-12-27 1997-07-11 Daikin Ind Ltd Hermetic compressor
JP2002506164A (en) * 1998-03-05 2002-02-26 キャリア・コーポレーション Scroll compressor with combined pressure ratio / pressure difference relief valve
JP2018035748A (en) * 2016-08-31 2018-03-08 ダイキン工業株式会社 Scroll compressor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113606136A (en) * 2021-08-27 2021-11-05 珠海格力电器股份有限公司 Compressor and air conditioner with same
CN113606136B (en) * 2021-08-27 2022-11-15 珠海格力电器股份有限公司 Compressor and air conditioner with same

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