WO2020136786A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

Info

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
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
chamber
control valve
unload
space
Prior art date
Application number
PCT/JP2018/048052
Other languages
English (en)
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.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2020562036A priority Critical patent/JP7012881B2/ja
Priority to PCT/JP2018/048052 priority patent/WO2020136786A1/fr
Publication of WO2020136786A1 publication Critical patent/WO2020136786A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents

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.

Landscapes

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

Abstract

Ce compresseur à spirale est pourvu d'un mécanisme de déchargement pour effectuer une opération de déchargement dans laquelle la vitesse de décharge est limitée par l'alimentation d'un fluide à travers une dérivation d'une chambre de compression à un espace basse pression. Formé dans un séparateur ou une spirale fixe se trouve un passage de décharge qui relie l'espace basse pression et une chambre de contre-pression qui est reliée à la chambre de compression au cours d'un processus de compression. Le mécanisme de déchargement est pourvu d'une soupape de commande qui ferme et ouvre le passage de déchargement. Pendant le fonctionnement, une basse pression à partir de l'espace basse pression est exercée sur l'une des faces d'extrémité de la soupape de commande dans la direction de déplacement de celle-ci, tandis qu'une pression supérieure à celle dans l'espace basse pression, et dérivée de l'intérieur d'un récipient étanche, agit sur l'autre face d'extrémité de la soupape de commande. Par un changement de la différence entre les pressions agissant sur les deux faces d'extrémité de la soupape de commande en fonction des conditions de fonctionnement, la soupape de commande est déplacée de manière à amener le passage de déchargement à être ouvert ou fermé.
PCT/JP2018/048052 2018-12-27 2018-12-27 Compresseur à spirale WO2020136786A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2020562036A JP7012881B2 (ja) 2018-12-27 2018-12-27 スクロール圧縮機
PCT/JP2018/048052 WO2020136786A1 (fr) 2018-12-27 2018-12-27 Compresseur à spirale

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/048052 WO2020136786A1 (fr) 2018-12-27 2018-12-27 Compresseur à spirale

Publications (1)

Publication Number Publication Date
WO2020136786A1 true WO2020136786A1 (fr) 2020-07-02

Family

ID=71126164

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/048052 WO2020136786A1 (fr) 2018-12-27 2018-12-27 Compresseur à spirale

Country Status (2)

Country Link
JP (1) JP7012881B2 (fr)
WO (1) WO2020136786A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113606136A (zh) * 2021-08-27 2021-11-05 珠海格力电器股份有限公司 压缩机以及具有其的空调器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0763173A (ja) * 1993-08-30 1995-03-07 Mitsubishi Heavy Ind Ltd スクロ−ル型流体機械
JPH09177689A (ja) * 1995-12-27 1997-07-11 Daikin Ind Ltd 密閉形圧縮機
JP2002506164A (ja) * 1998-03-05 2002-02-26 キャリア・コーポレーション 圧力比／圧力差複合リリーフ弁を有するスクロールコンプレッサ
JP2018035748A (ja) * 2016-08-31 2018-03-08 ダイキン工業株式会社 スクロール圧縮機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0763173A (ja) * 1993-08-30 1995-03-07 Mitsubishi Heavy Ind Ltd スクロ−ル型流体機械
JPH09177689A (ja) * 1995-12-27 1997-07-11 Daikin Ind Ltd 密閉形圧縮機
JP2002506164A (ja) * 1998-03-05 2002-02-26 キャリア・コーポレーション 圧力比／圧力差複合リリーフ弁を有するスクロールコンプレッサ
JP2018035748A (ja) * 2016-08-31 2018-03-08 ダイキン工業株式会社 スクロール圧縮機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113606136A (zh) * 2021-08-27 2021-11-05 珠海格力电器股份有限公司 压缩机以及具有其的空调器
CN113606136B (zh) * 2021-08-27 2022-11-15 珠海格力电器股份有限公司 压缩机以及具有其的空调器

Also Published As

Publication number Publication date
JPWO2020136786A1 (ja) 2021-09-09
JP7012881B2 (ja) 2022-01-28

Similar Documents

Publication Publication Date Title
US10495086B2 (en) Compressor valve system and assembly
TW591175B (en) Scroll compressor
JP4680616B2 (ja) スクロール圧縮機の容量可変装置
AU766033B2 (en) Scroll type compressor
JP5396235B2 (ja) スクロール圧縮機
KR20180093693A (ko) 스크롤 압축기
US10982674B2 (en) Scroll compressor with back pressure chamber and back pressure passages
US7611342B2 (en) Multistage compression type rotary compressor
JP4930022B2 (ja) 流体機械
WO2020136786A1 (fr) Compresseur à spirale
JP6385708B2 (ja) スクリュー圧縮機
KR101909606B1 (ko) 스크롤 압축기
JP2008133810A (ja) 圧縮機
JP2013019293A (ja) スクロール圧縮機
JPH09217690A (ja) スクロール気体圧縮機
JP2017172504A (ja) スクロール圧縮機
JP6692195B2 (ja) スクロール圧縮機
JP6913842B2 (ja) スクロール圧縮機
JP2016020651A (ja) スクリュー圧縮機
CN113007093B (zh) 涡旋压缩机
JP2006009640A (ja) スクロール圧縮機
JP2014190319A (ja) スクロール圧縮機
JP2012225226A (ja) スクロール圧縮機
JP2001041183A (ja) スクロール気体圧縮機
JP2013139714A (ja) スクロール圧縮機

Legal Events

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

Ref document number: 18944773

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2020562036

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18944773

Country of ref document: EP

Kind code of ref document: A1