WO2019244273A1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
WO2019244273A1
WO2019244273A1 PCT/JP2018/023450 JP2018023450W WO2019244273A1 WO 2019244273 A1 WO2019244273 A1 WO 2019244273A1 JP 2018023450 W JP2018023450 W JP 2018023450W WO 2019244273 A1 WO2019244273 A1 WO 2019244273A1
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WO
WIPO (PCT)
Prior art keywords
hole
rotary compressor
cylinder
flow path
injection
Prior art date
Application number
PCT/JP2018/023450
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English (en)
Japanese (ja)
Inventor
亮 濱田
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2018/023450 priority Critical patent/WO2019244273A1/fr
Priority to CN201880094444.2A priority patent/CN112262259B/zh
Priority to JP2020525146A priority patent/JP6961084B2/ja
Publication of WO2019244273A1 publication Critical patent/WO2019244273A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation

Definitions

  • the present invention relates to a rotary compressor that compresses and discharges a fluid, mainly a refrigerant.
  • a conventional rotary compressor has a configuration in which a compression mechanism and an electric motor that drives the compression mechanism via a rotating shaft are arranged in a closed container.
  • the compression mechanism mainly includes a cylindrical cylinder, a rolling piston rotatably fitted to the eccentric portion of the rotating shaft, and a vane slidably disposed in a vane groove provided in the cylinder. .
  • a through hole is formed in the center of the cylinder in the axial direction, and the through hole is closed by end plates disposed on both end surfaces in the axial direction of the cylinder, so that a cylinder chamber is formed in the cylinder.
  • a compression chamber partitioned by vanes is formed, and the rotating shaft rotates and the rolling piston rotates eccentrically in the cylinder chamber, so that the volume of the compression chamber is reduced and the refrigerant is compressed. Has become.
  • the injection method includes a method in which an injection flow path is provided in a cylinder and an end plate, and a method in which an injection flow path is provided only in an end plate (for example, see Patent Document 1).
  • the injection channel formed in the end plate is formed by drilling a hole or the like from the outer peripheral surface of the end plate. For this reason, the hole is opened on the outer peripheral surface of the end plate, and in order to prevent the injection flow path from communicating with the space outside the end plate, it is necessary to close the opening with a closing member such as a bolt. . Therefore, a closing member for closing the opening is required separately, which causes a problem of increasing the number of parts.
  • the present invention has been made in order to solve such a problem, and an object of the present invention is to provide a rotary compressor capable of forming an injection flow path without using a closing component.
  • a rotary compressor is a rotary compressor including a compression mechanism that compresses a refrigerant by rotation of a rotation shaft, wherein the compression mechanism includes a cylinder having a through hole that penetrates in an axial direction, and a rotation shaft. Formed by the rolling piston driven by the piston and housed in the through hole of the cylinder, two end plates arranged on both end surfaces in the axial direction of the cylinder, and the through hole of the cylinder closed by the two end plates. It has a vane projecting into the cylinder chamber, partitioning the cylinder chamber by coming into contact with the rolling piston to form a compression chamber in the cylinder chamber, and an injection flow path that guides the injection refrigerant to the compression chamber. A first hole formed in the cylinder and a second hole formed in one of the two end plates are formed so as to communicate with each other. In which only the end face of the cylinder side is formed by the open pores.
  • the injection flow path is formed such that the first hole formed in the cylinder and the second hole formed in one of the two end plates communicate with each other.
  • a hole was formed only in the end face of the end plate on the cylinder side.
  • FIG. 1 is a schematic sectional view of a rotary compressor according to Embodiment 1 of the present invention.
  • FIG. 2 is an enlarged view of an injection flow path near a compression mechanism of the rotary compressor according to Embodiment 1 of the present invention.
  • BRIEF DESCRIPTION OF THE DRAWINGS It is the figure which shows the main bearing of the rotary compressor which concerns on Embodiment 1 of this invention, Comprising: It is the figure which put together (a) schematic longitudinal section and (b) schematic bottom view.
  • FIG. 4 is a diagram showing a modification of the injection flow path of the rotary compressor according to Embodiment 1 of the present invention.
  • FIG. 7 is a schematic bottom view of a main bearing of a rotary compressor according to Embodiment 2 of the present invention.
  • FIG. 7 is a diagram showing a main bearing of a rotary compressor according to Embodiment 3 of the present invention, and is a diagram collectively showing (a) a schematic longitudinal sectional view and (b) a schematic bottom view.
  • FIG. 7 is an enlarged view of the periphery including a second hole in FIG. 6. It is a figure which shows the main bearing of the rotary compressor which concerns on Embodiment 4 of this invention, and which put together (a) schematic longitudinal cross-sectional view and (b) schematic bottom view.
  • FIG. 15 is a schematic longitudinal sectional view of a modification of the main bearing of the rotary compressor according to Embodiment 5 of the present invention.
  • FIG. 1 is a schematic sectional view of a rotary compressor according to Embodiment 1 of the present invention.
  • the rotary compressor according to the present invention is a hermetic electric compressor in which a compression mechanism 2 and an electric motor 3 for driving the compression mechanism 2 via a rotary shaft 6 are arranged in a closed container 1. Having.
  • the compression mechanism 2 is arranged at an upper part in the closed container 1, and the electric motor unit 3 is arranged at a lower part in the closed container 1.
  • the rotary compressor according to the first embodiment will be described taking a twin rotary type rotary compressor in which the compression mechanism 2 has two cylinders as an example, but the present invention is not limited to this, and one or three or more cylinders are used. It may be.
  • the rotary compressor compresses the refrigerant by rotating the rotating shaft 6 by the electric motor unit 3 and driving the compression mechanism unit 2. After the refrigerant is sucked through the suction muffler 5 and compressed by the compression mechanism 2, the refrigerant becomes a high-temperature and high-pressure gas and is discharged into the closed casing 1.
  • the refrigerant gas discharged into the closed container 1 passes through the gap of the electric motor unit 3 and is discharged from the discharge pipe 1a into the refrigerant circuit.
  • Lubricating oil is stored in the lower part of the closed container 1, and lubrication of the compression mechanism part 2 is maintained by supplying oil to each part by an oil supply mechanism (not shown) provided at the lower end part of the rotating shaft 6.
  • the motor unit 3 includes a stator 3a and a rotor 3b.
  • the rotating shaft 6 is fixed to the rotor 3b, and the rotating shaft 6 rotates by the rotation of the rotor 3b, so that rotational power is transmitted to the compression mechanism 2.
  • the compression mechanism section 2 includes a first compression mechanism section 20A that is a compression section, a second compression mechanism section 20B that is a compression section, a main bearing 30 disposed on an upper end surface of the first compression mechanism section 20A,
  • the auxiliary bearing 40 includes an auxiliary bearing 40 disposed on the lower end surface of the compression mechanism 20 ⁇ / b> B and an intermediate plate 50.
  • the main bearing 30 is composed of a hollow cylindrical bearing portion 31 that rotatably supports the rotary shaft 6 and a flat annular end plate 32 that closes an upper end surface of the cylinder 21 described below.
  • the auxiliary bearing 40 includes a hollow cylindrical bearing portion 41 that rotatably supports the rotating shaft 6 and a flat plate-shaped end plate 42 that closes a lower end surface of the cylinder 21 described below.
  • Each of the end plate 32 and the end plate 42 has a discharge port (not shown) provided with a discharge valve that opens when a pressure in a compression chamber, which will be described later, becomes equal to or higher than a predetermined pressure.
  • first compression mechanism 20A and the second compression mechanism 20B of the compression mechanism 2 will be described. Since the first compression mechanism 20A and the second compression mechanism 20B have basically the same configuration, the first compression mechanism 20A will be described below as a representative.
  • the first compression mechanism section 20A includes a cylindrical cylinder 21 having a through-hole penetrating in the axial direction (vertical direction in FIG. 1), a rolling piston 22 driven by the rotating shaft 6, a vane 23, and the like. .
  • the main bearing 30 and the intermediate plate 50 are disposed on both end surfaces in the axial direction of the cylinder 21, and the through-hole is closed by the end plate 32 and the intermediate plate 50 of the main bearing 30, so that the cylinder 21 is inserted into the cylinder 21.
  • a cylinder chamber is formed.
  • the end plate 32 and the intermediate plate 50 of the main bearing 30 function as an end plate that closes the through hole.
  • the end surface of the cylinder 21 on the side of the main bearing 30 is referred to as a bearing-side end surface 21a
  • the end surface of the cylinder 21 on the side of the intermediate plate 50 is referred to as an intermediate-plate-side end surface 21b.
  • the rolling piston 22 is housed in the through hole of the cylinder 21 in a state of being rotatably fitted to the eccentric shaft portion 6 a of the rotating shaft 6.
  • the vane 23 is slidably disposed in a vane groove (not shown) provided in the cylinder 21 in the radial direction.
  • the vane 23 projects into the cylinder chamber, and the tip end of the vane 23 contacts the rolling piston 22 to partition the cylinder chamber into a suction chamber 24 (see FIG. 3B described later) and a compression chamber 25.
  • the first compression mechanism unit 20A configured as described above eccentrically rotates in the cylinder chamber while the rolling piston 22 is in sliding contact with the vane 23, so that the volume of the compression chamber 25 is reduced and the refrigerant is compressed. I have.
  • the compressed high-temperature and high-pressure refrigerant gas is discharged from the discharge port (not shown) provided in the end plate 32 of the main bearing 30 into the closed vessel 1 against a discharge valve (not shown).
  • the refrigerant gas discharged into the closed container 1 passes through the discharge pipe 1a and is discharged to a refrigerant circuit outside the compressor.
  • R410 refrigerant is used as an operating refrigerant, but the type of refrigerant is not limited to this.
  • the injection channel can be configured without using a closing member.
  • the injection channel will be described.
  • the configuration of the injection flow path in the first compression mechanism 20A and the second compression mechanism 20B is the same. Therefore, in this specification, the first compression mechanism 20A will be described as a representative.
  • FIG. 2 is an enlarged view of the injection flow path near the compression mechanism of the rotary compressor according to Embodiment 1 of the present invention.
  • FIG. 3 is a diagram showing a main bearing of the rotary compressor according to Embodiment 1 of the present invention, and is a diagram collectively showing (a) a schematic longitudinal sectional view and (b) a schematic bottom view.
  • FIG. 3B shows the inner peripheral surface of the cylinder 21 (hereinafter, referred to as the cylinder inner peripheral surface) 21 c, the discharge port 321, the vane 23, and the rolling piston 22. The positions are shown by dotted lines.
  • the first compression mechanism unit 20 ⁇ / b> A includes the injection passage 10 that guides the injection refrigerant, which is a liquid refrigerant or a two-phase refrigerant, to the compression chamber 25.
  • the injection refrigerant which is a liquid refrigerant or a two-phase refrigerant
  • a first hole 211 formed in the cylinder 21 and a second hole 60 formed in the end plate 32 of the main bearing 30 communicate with each other.
  • the first hole 211 has a passage inlet opening on the outer peripheral surface of the cylinder 21 and a passage outlet opening on the bearing-side end surface 21a.
  • the first hole 211 includes a lateral hole 211a extending in the surface direction from the outer peripheral surface of the cylinder 21 and a vertical hole 211b extending in the axial direction from the flow path outlet of the lateral hole 211a and opening to the bearing side end surface 21a.
  • the vertical hole 211b of the first hole 211 extends in the axial direction and is formed perpendicular to the end face 32a, but the vertical hole 211b may be non-vertical.
  • the second hole 60 is formed by a lateral groove formed along the end face 32a on the cylinder 21 side in the end plate 32 of the main bearing 30.
  • the second hole 60 is formed to extend in the radial direction as shown in FIG. 3 (b), and the radially inner end 60a is located inside the cylinder inner peripheral surface 21c, and the radially outer end 60b is the second end 60b. It is located at a position facing the flow path outlet of the one hole 211.
  • the second hole 60 is formed by a hole opened only in the end face 32a.
  • the second hole 60 is formed as a closed hole that does not open except at the end face 32a. Thereby, the injection channel 10 is configured without using the closing member.
  • the respective surface shapes of the radially inner end portion 60a and the radially outer end portion 60b of the second hole 60 are formed in a curved surface in order to reduce flow path bending pressure loss, and in the first embodiment, the curvature radius R5 is used. Is formed.
  • the injection pipe 4 is connected to the outer peripheral end of the first hole 211 in the injection channel 10 configured as described above. Then, the injection refrigerant that has flowed into the injection flow path 10 from the injection pipe 4 is injected into the compression chamber 25 through the first hole 211 and the second hole 60.
  • the pressure Pinj of the injection refrigerant is an intermediate pressure between the suction pressure Ps and the discharge pressure Pd.
  • Ps 0.5 MPaG
  • Pd 4.0 MPaG
  • Pinj 1.5 MPaG.
  • the hole diameter D1 of the vertical hole 211b of the first hole 211 is 5 mm.
  • the distance L1 from the cylinder center O to the center of the vertical hole 211b of the first hole 211 is 35 mm.
  • the circumferential width W1 of the second hole 60 is 5 mm.
  • the height H1 in the axial direction of the second hole 60 is 5 mm.
  • the cylinder inner diameter D2 is 50 mm. It should be noted that the dimensions of each location shown here are merely examples, and they may be set as appropriate. This is the same in the embodiment described later.
  • the second hole 60 communicating the first hole 211 formed in the cylinder 21 and the compression chamber 25 is formed along the end face 32 a of the main bearing 30. It is composed of a lateral groove.
  • the second hole 60 is constituted by a hole opened only at the end face 32 a of the main bearing 30. For this reason, a closing member is not required in the injection flow path 10, and the injection flow path 10 can be configured with a simpler configuration than the conventional configuration in which a closing member is required.
  • the closing member is not required, it is not necessary to secure a space for disposing the closing member, so that the degree of freedom of arrangement of the injection flow path 10 can be improved.
  • the injection refrigerant Since the pressure of the injection refrigerant is lower than the discharge pressure, the injection refrigerant has an effect of cooling sliding components such as the vane 23 and the rolling piston 22 included in the compression mechanism 2. By cooling the sliding parts, there is an effect that the clearance between the parts is sufficiently maintained and seizure between the parts is prevented. Therefore, a highly reliable rotary compressor can be configured by locally cooling the sliding components included in the compression mechanism 2 using the injection refrigerant.
  • a specific description will be given.
  • FIG. 3B shows a state in which the rolling piston 22 is located at a position of 270 ° in the rotation direction of the rotating shaft 6 (the direction of the arrow 220 in FIG. 3B) when the vane phase is 0 °. .
  • the position where the phase is 270 ° is a position designed to minimize the gap between the rolling piston 22 and the cylinder inner peripheral surface 21c when the rotating shaft 6 rotates. Therefore, when the rolling piston 22 is at the position of 270 °, the rolling piston 22 thermally expands due to friction. Therefore, it is preferable to cool the rolling piston 22 at this position with the injection refrigerant.
  • the second holes 60 are arranged at a position of 270 ° in phase, so to say, are arranged in a phase in which the gap between the rolling piston 22 and the cylinder inner peripheral surface 21c is minimized. Therefore, the rolling piston 22 can be effectively cooled by the injection refrigerant ejected from the second hole 60.
  • FIG. 4 is a diagram showing a modification of the injection flow path of the rotary compressor according to Embodiment 1 of the present invention. 1 to 3, the second hole 60 is formed in the end plate 32 of the main bearing 30, but in this modification, the second hole 60 is formed in the intermediate plate 50. Then, with the formation of the second hole 60 in the intermediate plate 50, the vertical hole 211b of the first hole 211 is opened not in the bearing side end surface 21a but in the intermediate plate side end surface 21b. As described above, even when the second hole 60 is provided in the intermediate plate 50, the same effect as when the second hole 60 is formed in the end plate 32 of the main bearing 30 can be obtained.
  • the formation position of the second hole 60 may be the end plate 32 of the main bearing 30 and the end plate 42 of the sub bearing 40, or may be the intermediate plate 50. The points are the same.
  • the second hole 60 has a linear shape extending in the radial direction.
  • the second hole 60 may be formed by a hole opened only in the end face 32 a of the end plate 32 on the cylinder 21 side.
  • the shape is not limited to the shape of the first embodiment.
  • an embodiment in which the second hole has another shape will be described.
  • the second embodiment is different from the first embodiment in the shape of the second hole, and the other configuration is the same as the first embodiment.
  • a description will be given focusing on differences between the second embodiment and the first embodiment.
  • FIG. 5 is a schematic bottom view of a main bearing of a rotary compressor according to Embodiment 2 of the present invention.
  • the second hole 61 of the second embodiment has a curved shape when a part of the second hole 60 of the first embodiment shown in FIG. 3 is viewed in the axial direction.
  • 5 mm from the radially inner end of the second hole 61 has a linear shape
  • the radially outer portion of the second hole 61 has a curved shape with a radius of curvature R20.
  • the reason why the radially inner end portion of the second hole 61 is formed in a straight line is to take into account mass production in manufacturing, and may be entirely curved.
  • the curved shape has the radius of curvature R20, but the radius of the curved shape may change, for example, like an involute curve.
  • the second hole 61 By forming the second hole 61 into a curved shape when viewed in the axial direction, directivity can be given in the injection direction of the injection refrigerant from the second hole 61 to the compression chamber 25.
  • the injection direction is formed so as to point in the rotation direction of the rotation shaft 6 (the direction of the arrow 220).
  • the radially inner end 61a of the second hole 61 is disposed at a position advanced by a phase ⁇ in the rotation direction of the rotating shaft 6 from the radially outer end 61b.
  • the second hole 61 By forming the second hole 61 so that the injection direction is directed to the rotation direction of the rotary shaft 6 (the direction of the arrow 220), the following effects can be obtained.
  • a flow of the compressed refrigerant in the direction of rotation of the rotating shaft 6, in other words, a flow of the refrigerant toward the discharge port 321 is formed. Therefore, the injection refrigerant in the second hole 61 is drawn into the compression chamber 25 by the flow of the refrigerant in the compression chamber 25 by directing the second hole 61 in the rotation direction of the rotating shaft 6, and the injection is effectively performed.
  • the flow rate can be increased. That is, an injection mechanism with a large injection flow rate can be configured with a simple structure.
  • the vane 23 may be directed.
  • the vane 23 can be sufficiently cooled by the injection refrigerant, and a highly reliable rotary compressor can be configured.
  • the specific curved shape of the second hole 61 in the case of directing the vane 23 is such that the radially inner end portion 61a of the second hole 61 is closer to the vane 23 when viewed in the axial direction than the radially outer end portion 61b.
  • Embodiment 3 is a form in which the reverse flow of the refrigerant from the compression chamber 25 to the injection flow path and the leakage of the refrigerant from the low pressure side to the high pressure side in the cylinder chamber are suppressed.
  • the shape of the second hole is This is different from the first embodiment.
  • the configuration other than the shape of the second hole is the same as that of the first embodiment.
  • FIG. 6 is a diagram showing a main bearing of a rotary compressor according to Embodiment 3 of the present invention, and is a diagram collectively showing (a) a schematic longitudinal sectional view and (b) a schematic bottom view.
  • FIG. 7 is an enlarged view of the periphery including the second hole of FIG.
  • the second hole 62 of the third embodiment is formed as a hole opened only in the end face 32a of the end plate 32 on the cylinder 21 side, which is the same as in the first embodiment.
  • a characteristic configuration of the second hole 62 according to the third embodiment will be described.
  • the second hole 62 has a configuration provided with a throttle portion 62 a having a narrowed flow path section in the middle of the flow path of the second hole 62.
  • the upstream side of the throttle 62a is formed by a lateral groove 62b formed in the end face 32a of the main bearing 30, and the downstream side is formed by a vertical hole 62c extending in the axial direction from the end face 32a of the main bearing 30.
  • the throttle portion 62a is formed by a groove formed in the end face 32a of the main bearing 30 so as to extend in the radial direction. Then, as shown in FIG.
  • the radially outer end 62aa of the throttle portion 62a has the same radial position as the cylinder inner peripheral surface 21c, and the throttle portion 62a and the vertical hole 62c are positioned closer to the cylinder inner peripheral surface 21c. It is located inside and communicates with the compression chamber 25.
  • a radially outer end 62ba of the lateral groove 62b is located at a position facing the flow path outlet of the first hole 211.
  • the width W1 and the height H1 in the circumferential direction of the lateral groove 62b are each 5 mm.
  • the height H2 of the vertical hole 62c is 7 mm, and the height of the vertical hole 62c is higher than the height of the horizontal groove 62b.
  • the diameter D3 of the vertical hole 62c is 6 mm.
  • the center of the vertical hole 62c is located inside the cylinder inner peripheral surface 21c, and the radial distance L2 between the cylinder inner peripheral surface 21c and the center of the vertical hole 62c is 5 mm.
  • the circumferential width W2 of the narrowed portion 62a is 3 mm, which is set to be smaller than the diameter D3 of the vertical hole 62c and smaller than the circumferential width W1 of the horizontal groove 62b.
  • the pressure of the injection refrigerant may be lower than the internal pressure of the compression chamber 25 depending on the operating conditions and the phase in which the throttle portion 62a is arranged.
  • the internal pressure of the compression chamber 25 > the pressure of the injection refrigerant.
  • the discharge pressure is 4.1 MPaG
  • the suction pressure is 0.5 MPaG
  • the pressure of the injection refrigerant is 1.3 MPaG.
  • FIG. 6B when the arrangement phase of the restricting portion 62a is 0 ° in the vane phase, the phase is 270 ° in the rotation direction of the rotary shaft 6 (the direction of the arrow 220 in FIG. 6B).
  • the same effect as in the first embodiment can be obtained, and the throttle portion 62a is provided in the second hole 62 so that the second hole 62 is throttled in the middle of the flow path.
  • the effect is obtained. That is, the backflow of the refrigerant from the compression chamber 25 to the injection flow path 10 can be suppressed.
  • the height H2 of the vertical hole 62c is higher than the height H1 of the horizontal groove 62b, the injection refrigerant that has flowed back into the vertical hole 62c can be caught in the depth of the vertical hole 62c, and the backflow into the horizontal groove 62b can be suppressed.
  • Embodiment 4 is an embodiment in which directivity is provided in the injection direction of the injection refrigerant from the injection flow path to the compression chamber 25.
  • Embodiment 4 is specifically different from Embodiment 1 in the shape of the second hole, and other configurations are the same as those in Embodiment 1.
  • a description will be given focusing on differences between the fourth embodiment and the first embodiment.
  • FIG. 8 is a diagram showing a main bearing of a rotary compressor according to Embodiment 4 of the present invention, and is a diagram collectively showing (a) a schematic longitudinal sectional view and (b) a schematic bottom view.
  • the second hole 63 of the fourth embodiment is formed as a hole opened only at the end face 32a of the main bearing 30, and this point is the same as that of the first embodiment.
  • a characteristic configuration of the second hole 63 according to the fourth embodiment will be described.
  • the second hole 63 is composed of a radial groove 63a formed in the end face 32a of the main bearing 30 and extending in the radial direction, and an inclined hole 63b formed in communication with the lateral groove 63a and non-perpendicular to the end face 32a. .
  • a radially outer end 63aa of the lateral groove 63a faces the flow path outlet of the first hole 211, and the lateral groove 63a communicates with the first hole 211.
  • the channel outlet 63ba of the inclined hole 63b is located inside the cylinder inner peripheral surface 21c and communicates with the compression chamber 25.
  • the inclined hole 63b is formed such that the injection direction of the injection refrigerant injected into the compression chamber 25 from the inclined hole 63b is directed to the rotation direction of the rotary shaft 6 (the direction of the arrow 220). Specifically, as shown in FIG. 8 (b), the flow path outlet 63ba of the inclined hole 63b is more rotated than the flow path inlet 63bb communicating with the lateral groove 63a of the inclined hole 63b in the direction of rotation of the rotary shaft 6 (arrow). 220 direction), and is disposed at a position advanced by a phase ⁇ .
  • the inclined hole 63b is inclined, for example, by 30 degrees here with respect to the perpendicular of the end face 32a. With the configuration described above, the injection refrigerant in the inclined hole 63b is drawn into the compression chamber 25 as in the second embodiment, and the injection flow rate can be effectively increased.
  • the same effects as those of the first embodiment can be obtained, and the following effects can be obtained. That is, since the second hole 63 is formed such that the injection direction of the injection refrigerant from the second hole 63 to the compression chamber 25 is directed to the rotation direction of the rotary shaft 6, the injection flow rate can be effectively increased. That is, an injection mechanism with a large injection flow rate can be configured with a simple structure. In addition, since it is the inclined hole 63b on the flow path exit side of the second hole 63 that determines the injection direction, the flow path exit 63ba of the inclined hole 63b has advanced in the rotation direction of the rotary shaft 6 more than the flow path entrance 63bb. If it is formed at the position, it can be configured to direct the rotation direction of the rotating shaft 6.
  • the vane 23 may be directed.
  • the vane 23 can be sufficiently cooled by the injection refrigerant, and a highly reliable rotary compressor can be configured.
  • the passage outlet 63ba of the inclined hole 63b may be closer to the vane 23 when viewed in the axial direction than the passage inlet 63bb.
  • the illustrated second hole 63 also corresponds thereto.
  • Embodiment 5 FIG.
  • the fifth embodiment similarly to the fourth embodiment, directivity is provided in the injection direction of the injection refrigerant from the injection flow path to the compression chamber 25.
  • the fifth embodiment is different from the first and fourth embodiments in the shape of the second hole, and the other configuration is the same as that of the first embodiment.
  • a description will be given focusing on differences between the fifth embodiment and the first embodiment.
  • FIG. 9 is a diagram showing a main bearing of a rotary compressor according to Embodiment 5 of the present invention, and is a diagram collectively showing (a) a schematic longitudinal sectional view and (b) a schematic bottom view.
  • the second hole 64 of the fifth embodiment is formed as a hole opened only in the end face 32a of the end plate 32 on the cylinder 21 side, and this point is the same as in the first embodiment.
  • a characteristic configuration of the second hole 64 of the fifth embodiment will be described.
  • the second hole 64 is composed of a radially extending lateral groove 64a formed in the end face 32a of the main bearing 30, a first inclined hole 64b, and a second inclined hole 64c.
  • the second hole 64 of the fifth embodiment corresponds to a configuration in which the inclined hole 63b of the second hole 63 of the fourth embodiment is replaced with two inclined holes.
  • a radially outer end 64aa of the lateral groove 64a faces the flow path outlet of the first hole 211, and the lateral groove 63a communicates with the first hole 211.
  • the first inclined hole 64b is formed so as to communicate with a radially inner end of the lateral groove 64a, and is inclined with respect to the end face 32a.
  • the second inclined hole 64c is formed to communicate with a radially inner end of the first inclined hole 64b, and is inclined with respect to the first inclined hole 64b.
  • the passage outlet 64ca of the second inclined hole 64c is located inside the cylinder inner peripheral surface 21c and communicates with the compression chamber 25.
  • the second inclined hole 64c is formed such that the direction of injection of the refrigerant injected from the second inclined hole 64c into the compression chamber 25 is in the direction of rotation of the rotary shaft 6 (the direction of the arrow 220). Specifically, as shown in FIG. 9B, the flow path outlet 64ca of the second inclined hole 64c is disposed at a position advanced by the phase ⁇ in the rotation direction of the rotating shaft 6 from the flow path inlet 64cb. .
  • the second inclined hole 64c is inclined here by, for example, 30 ° with respect to a perpendicular to the end face 32a.
  • the hole diameter of each of the first inclined hole 64b and the second inclined hole 64c is 3 mm.
  • the intersection angle ⁇ between the first inclined hole 64b and the second inclined hole 64c is 120 °.
  • the intersection angle ⁇ is desirably 90 ° or more in order to suppress the bending pressure loss of the refrigerant.
  • the inclined hole 63b (see FIG. 8) is continuous with the lateral groove 63a on the side of the end face 32a, so to say, the groove is formed on the end face 32a.
  • the first inclined hole 64b and the second inclined hole 64c do not communicate with each other on the end face 32a side, and the intersection of the first inclined hole 64b and the second inclined hole 64c is closer to the end face 32a.
  • the fifth embodiment has a configuration in which the first inclined hole 64b, the second inclined hole 64c, and the end surface 32a form a triangle.
  • the upper limit value of the intersection angle ⁇ may be smaller than the value specified by the following equation (1).
  • r1 radius of the first inclined hole 64b
  • r2 radius of the second inclined hole 64c
  • L3 distance from the opening on the end face 32a side of the first inclined hole 64b to the intersection
  • L4 from the opening on the end face 32a side of the second inclined hole 64c Distance to intersection
  • Equation (1) is calculated as follows.
  • equation (1) is calculated.
  • the same effects as those of the first embodiment can be obtained, and the following effects can be obtained. That is, since the second hole 64 is formed so that the injection direction of the injection refrigerant from the second hole 64 to the compression chamber 25 is directed to the rotation direction of the rotating shaft 6, the injection flow rate can be effectively increased. That is, an injection mechanism with a large injection flow rate can be configured with a simple structure.
  • the direction of the injection is determined by the second inclined hole 64c on the flow path outlet side of the second hole 64. Therefore, if the flow path outlet 64ca of the second inclined hole 64c is formed at a position advanced in the rotation direction of the rotary shaft 6 beyond the flow path inlet 64cb, the configuration can be such that the rotation direction of the rotary shaft 6 is directed.
  • the vane 23 may be directed as a destination of the injection refrigerant by the second hole 64.
  • the vane 23 can be sufficiently cooled by the injection refrigerant, and a highly reliable rotary compressor can be configured.
  • the flow path outlet 64ca of the second inclined hole 64c may be closer to the vane 23 when viewed in the axial direction than the flow path inlet 64cb.
  • the following effects can be obtained by providing the second hole 64 with two inclined holes and a structure in which the flow direction is changed in the second hole 64. That is, leakage of the refrigerant from the compression chamber 25 to the suction chamber 24 when the rolling piston 22 passes through the flow path outlet 64ca can be prevented, and the compressor efficiency can be improved.
  • FIG. 9 illustrates an example in which the second hole 64 is configured by the lateral groove 64a, the first inclined hole 64b, and the second inclined hole 64c, but may be configured as illustrated in FIG.
  • the configuration in which the lateral groove 64a is provided as shown in FIG. 9 makes it easier to freely determine the intersection angle ⁇ between the first inclined hole 64b and the second inclined hole 64c as compared with the configuration of FIG. Can be increased.
  • FIG. 10 is a schematic longitudinal sectional view of a modification of the main bearing of the rotary compressor according to Embodiment 5 of the present invention.
  • the second hole 64 is constituted by a first inclined hole 64b and a second inclined hole 64c.
  • the configuration may be such that the lateral groove 64a is eliminated and the flow path inlet of the first inclined hole 64b communicates with the first hole 211.
  • the intersection angle ⁇ is desirably set to 90 ° or more in order to suppress the bending pressure loss of the refrigerant.
  • the present invention is not limited to the above embodiments as they are, and the characteristic configurations of the embodiments may be appropriately combined.
  • the second embodiment and the third embodiment may be combined to provide a configuration in which a throttle section is provided in the middle of the flow path of the second hole 61 of the second embodiment shown in FIG.
  • the third embodiment and the fourth embodiment may be combined to provide a configuration in which a throttle portion is provided in the middle of the flow path of the second hole 63 shown in FIG.

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

Abstract

La présente invention concerne un compresseur rotatif dont le mécanisme de compression comporte un cylindre avec un trou débouchant axial, un piston rotatif qui est entraîné par un arbre rotatif et qui est contenu dans le trou débouchant du cylindre, deux plaques d'extrémité disposées sur les surfaces d'extrémité axiale opposées du cylindre, une ailette qui fait saillie dans une chambre de cylindre formée en fermant le trou débouchant du cylindre au moyen des deux plaques d'extrémité, et qui est en contact avec le piston rotatif pour diviser la chambre de cylindre, ce qui permet de former une chambre de compression à l'intérieur de la chambre de cylindre, et un passage d'écoulement d'injection qui conduit un fluide frigorigène d'injection vers la chambre de compression. Le passage d'écoulement d'injection est formé en reliant un premier trou qui est formé dans le cylindre, et un second trou qui est formé dans l'une des deux plaques d'extrémité. Le second trou est uniquement ouvert en direction de la surface d'extrémité côté cylindre de la plaque d'extrémité.
PCT/JP2018/023450 2018-06-20 2018-06-20 Compresseur rotatif WO2019244273A1 (fr)

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CN201880094444.2A CN112262259B (zh) 2018-06-20 2018-06-20 旋转式压缩机
JP2020525146A JP6961084B2 (ja) 2018-06-20 2018-06-20 ロータリ圧縮機

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022269752A1 (fr) * 2021-06-22 2022-12-29 三菱電機株式会社 Compresseur rotatif et dispositif à cycle de réfrigération

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5252110U (fr) * 1975-10-13 1977-04-14
JPS55137378A (en) * 1979-04-12 1980-10-27 Toshiba Corp Sealed type compressor
JPS6156439B2 (fr) * 1982-03-02 1986-12-02 Daikin Kogyo Co Ltd
US20150118091A1 (en) * 2013-10-29 2015-04-30 Emerson Climate Technologies, Inc. Rotary compressor with vapor injection system

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2768004B2 (ja) * 1990-11-21 1998-06-25 松下電器産業株式会社 ロータリ式多段気体圧縮機
JP3998752B2 (ja) * 1997-04-07 2007-10-31 三菱電機株式会社 密閉型回転圧縮機
JP4924092B2 (ja) * 2007-02-26 2012-04-25 パナソニック株式会社 冷凍サイクル装置
CN201486856U (zh) * 2009-06-30 2010-05-26 珠海格力电器股份有限公司 一种带增焓装置的回转压缩机
CN101608621B (zh) * 2009-07-28 2012-01-25 珠海格力电器股份有限公司 一种回转压缩机及使用该压缩机的空调系统
JP2017203451A (ja) * 2016-05-10 2017-11-16 ダイキン工業株式会社 回転式圧縮機
CN106089711B (zh) * 2016-07-20 2019-04-05 广东美芝制冷设备有限公司 多缸旋转压缩机及具有其的制冷循环装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5252110U (fr) * 1975-10-13 1977-04-14
JPS55137378A (en) * 1979-04-12 1980-10-27 Toshiba Corp Sealed type compressor
JPS6156439B2 (fr) * 1982-03-02 1986-12-02 Daikin Kogyo Co Ltd
US20150118091A1 (en) * 2013-10-29 2015-04-30 Emerson Climate Technologies, Inc. Rotary compressor with vapor injection system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022269752A1 (fr) * 2021-06-22 2022-12-29 三菱電機株式会社 Compresseur rotatif et dispositif à cycle de réfrigération

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CN112262259A (zh) 2021-01-22
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JP6961084B2 (ja) 2021-11-05

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