WO2023182457A1 - Compresseur à vis et congélateur - Google Patents

Compresseur à vis et congélateur Download PDF

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Publication number
WO2023182457A1
WO2023182457A1 PCT/JP2023/011627 JP2023011627W WO2023182457A1 WO 2023182457 A1 WO2023182457 A1 WO 2023182457A1 JP 2023011627 W JP2023011627 W JP 2023011627W WO 2023182457 A1 WO2023182457 A1 WO 2023182457A1
Authority
WO
WIPO (PCT)
Prior art keywords
compression chamber
rotor
screw
screw compressor
refrigerant
Prior art date
Application number
PCT/JP2023/011627
Other languages
English (en)
Japanese (ja)
Inventor
純幸 植村
貴司 井上
Original Assignee
ダイキン工業株式会社
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 ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Publication of WO2023182457A1 publication Critical patent/WO2023182457A1/fr

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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
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston 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

Definitions

  • the present disclosure relates to a screw compressor and a refrigeration device.
  • Patent Document 1 discloses a screw compressor that includes a screw rotor and a gate rotor.
  • the screw rotor is inserted into the cylinder, and a compression chamber is formed by meshing the gate of the gate rotor with the screw groove of the screw rotor.
  • the pressure difference generated between the space near the suction side end in the compression chamber and the space outside the compression chamber adjacent to the suction side end creates a gap between the suction side end and the inner surface of the cylinder.
  • refrigerant may flow through the gaps. For example, if intermediate-pressure refrigerant in a space outside the compression chamber adjacent to the suction side end leaks into the suction side of the compression chamber, the suction pressure will increase and compression efficiency will decrease.
  • An object of the present disclosure is to suppress the flow of refrigerant at the suction side end of the compression chamber of a screw compressor.
  • a first aspect of the present disclosure includes: a casing (11) having a cylinder part (16) therein; an electric motor (13) disposed within the casing (11); a drive shaft (19) connected to the electric motor (13) and driven to rotate; a screw rotor (40) disposed within the cylinder portion (16) and connected to the drive shaft (19); a gate rotor (50) having a gate (53) that meshes with the screw groove (41) of the screw rotor (40); A screw compressor in which a compression chamber is formed by the screw rotor (40) and the gate (53) inside the cylinder part (16),
  • the suction side end (42) of the screw rotor (40) is formed in a cylindrical shape so that the outer peripheral surface (42a) follows the inner peripheral surface of the cylinder part (16), A first surface (F) opposite to the outer circumferential surface (42a) of the suction side end (42) or the first axial end surface (42b) of the suction side end (42) is configured to allow fluid to flow therethrough.
  • the space near the suction side end (42) of the compression chamber (25) has a low pressure due to the suction refrigerant. Therefore, if the space adjacent to the compression chamber (25) via the suction side end (42) has an intermediate pressure, the refrigerant will flow between the first surface (F) and the suction side due to the pressure difference (differential pressure) of the refrigerant. It attempts to flow into the compression chamber (25) through the gap with the end (42).
  • the seal portion (80) provided on the first surface (F) can suppress the refrigerant from flowing through the gap between the first surface (F) and the suction side end (42). . As a result, it is possible to sufficiently ensure the pressure difference between high and low levels within the compression chamber (25), and it is possible to suppress a decrease in the capacity of the screw compressor.
  • a second aspect of the present disclosure provides, in the first aspect, a bearing part (21) fixed within the cylinder part (16) and supporting the drive shaft (19);
  • the bearing part (21) is arranged adjacent to the suction side end part (42),
  • the seal portion (80) is provided on the bearing portion (21).
  • the first surface (F) facing the suction side end (42) is located on the bearing portion (21).
  • the seal portion (80) formed on the first surface (F) of the bearing portion (21) can suppress the refrigerant from flowing between the suction side end portion (42) and the bearing portion (21). In this way, the bearing portion (21) has a bearing function and a sealing function.
  • a third aspect of the present disclosure provides, in the second aspect, The seal portion (80) is provided on the first surface (F) of the bearing portion (21) opposite to the axial end surface of the suction side end portion (42).
  • the seal portion (80) can be provided on the end surface of the bearing portion (21).
  • a fourth aspect of the present disclosure is, in the second or third aspect,
  • the bearing portion (21) has a flange portion (21c) disposed between the inner surface of the cylinder portion (16) and the outer peripheral surface (42a) of the suction side end portion (42),
  • the seal portion (80) is provided on the collar portion (21c).
  • the seal portion (80) is provided on the inner circumferential surface of the brim (21c), with the inner circumferential surface of the brim (21c) serving as the first surface (F). In this way, the seal portion (80) can also be provided in the bearing portion (21) having the flange portion (21c).
  • a fifth aspect of the present disclosure provides, in any one of the first to fourth aspects,
  • the gate rotor (50) has a first gate rotor (50a) and a second gate rotor (50b),
  • the compression chamber (25) is a first compression chamber (23) formed by the first gate rotor (50a) and the screw rotor (40) and compressing fluid at suction pressure introduced into the casing (11) to an intermediate pressure;
  • a second compression chamber (24) is formed by the second gate rotor (50b) and the screw rotor (40) and compresses the fluid at the intermediate pressure to the discharge pressure.
  • the screw compressor is configured as a two-stage compression type. While the intermediate pressure refrigerant discharged from the first compression chamber (23) moves to the suction port of the second compression chamber (24), there is a gap between the first surface (F) and the suction side end (42). It is possible to prevent the air from passing through the air and being sucked into the first compression chamber (23) again.
  • a sixth aspect of the present disclosure provides, in any one of the first to fifth aspects,
  • the seal portion (80) is composed of a labyrinth seal.
  • a seventh aspect of the present disclosure provides, in any one of the first to fifth aspects,
  • the seal portion (80) is configured with a surface texture.
  • An eighth aspect of the present disclosure is the screw compressor according to any one of the first to seventh aspects.
  • FIG. 1 is a schematic piping system diagram of a refrigeration system according to an embodiment.
  • FIG. 2 is a vertical cross-sectional view showing a main part of the schematic configuration of the screw compressor according to the embodiment.
  • FIG. 3 is a cross-sectional view taken along the line III--III in FIG. 2.
  • FIG. 4 is a perspective view showing the state of engagement between the screw rotor and the gate rotor.
  • FIG. 5 is a schematic plan view showing the suction process, compression process, and discharge process of the screw compressor.
  • FIG. 6 is a perspective view showing the flow of low-stage compression refrigerant.
  • FIG. 7 is a perspective view showing the flow of high-stage compression refrigerant.
  • FIG. 8 is a side sectional view illustrating the flow of refrigerant in the compression mechanism.
  • FIG. 9 is an enlarged side cross section illustrating the flow of refrigerant around the first end of the compression mechanism.
  • FIG. 10 is a side sectional view and an enlarged view of a part of the compression mechanism for explaining the seal portion of this embodiment.
  • FIG. 11 corresponds to an enlarged view of FIG. 10 of a screw compressor according to modification 2.
  • FIG. 12 is a diagram corresponding to an enlarged view of FIG. 10 of a screw compressor according to modification 3.
  • FIG. 13 is a diagram corresponding to FIG. 10 of a screw compressor according to modification 4.
  • FIG. 14 is a piping system diagram of a refrigerant circuit to which a screw compressor according to modification 5 is connected.
  • Air conditioner As shown in FIG. 1, the screw compressor (10) of this embodiment is provided in an air conditioner (1) that air-conditions indoor space.
  • the air conditioner (1) is an example of the refrigeration device (1) of the present disclosure.
  • the air conditioner (1) has a refrigerant circuit (2) filled with refrigerant.
  • the refrigerant circuit (2) has a screw compressor (10), a condenser (3), an expansion valve (4), and an evaporator (5).
  • the refrigerant circuit (2) performs a vapor compression type refrigeration cycle.
  • the arrows in FIG. 1 indicate the direction in which the refrigerant flows.
  • heat is radiated from the refrigerant compressed by the screw compressor (10) in the condenser (3).
  • the heat radiated refrigerant is depressurized by the expansion valve (4), evaporated by the evaporator (5), and then sucked into the screw compressor (10).
  • Screw Compressor The screw compressor (10) compresses refrigerant.
  • the screw compressor (10) sucks in low-pressure gas refrigerant and compresses the sucked gas refrigerant.
  • the screw compressor (10) discharges compressed high-pressure gas refrigerant.
  • the screw compressor (10) of this embodiment is configured to compress refrigerant in two stages.
  • the screw compressor (10) includes a casing (11), an electric motor (13), a drive shaft (19), and a compression mechanism (30).
  • “upper”, “lower”, “right”, and “left” refer to directions when the side of the screw compressor (10) shown in FIG. 2 is viewed from the front.
  • the casing (11) is formed into a horizontally long cylindrical shape.
  • a suction port and a discharge port (not shown) are formed in the casing (11).
  • a low pressure space (S1) and a high pressure space (S2) are formed inside the casing (11).
  • the low-pressure space (S1) is a space through which low-pressure gas refrigerant is sucked into the compression mechanism (30) through the suction port.
  • the high pressure space (S2) is a space into which the high pressure gas refrigerant discharged from the compression mechanism (30) flows.
  • the refrigerant in the high pressure space (S2) flows out of the screw compressor (10) from the discharge port.
  • a cylinder portion (16) is formed within the casing (11).
  • the cylinder portion (16) is formed into a horizontally elongated substantially cylindrical shape.
  • a screw rotor (40), which will be described later, is disposed within the cylinder portion (16).
  • the electric motor (13) is housed within the casing (11).
  • the electric motor (13) is arranged at one end inside the casing (11).
  • the electric motor (13) has a stator (14) and a rotor (15).
  • the stator (14) is fixed to the inner wall of the casing (11).
  • the rotor (15) is arranged inside the stator (14).
  • a drive shaft (19) is fixed inside the rotor (15).
  • the rotation speed of the electric motor (13) can be changed.
  • the electric motor (13) is an inverter-driven electric motor.
  • the drive shaft (19) is arranged inside the casing (11).
  • the drive shaft (19) extends along the longitudinal direction of the casing (11).
  • the drive shaft (19) extends substantially horizontally.
  • the drive shaft (19) is inserted into the cylinder portion (16) along the cylinder axis direction.
  • the drive shaft (19) is arranged so that its axial center coincides with the cylindrical axis center of the cylinder portion (16).
  • the drive shaft (19) is driven by an electric motor (13).
  • the rotation speed of the drive shaft (19) changes as the rotation speed of the electric motor (13) changes. In other words, the rotation speed of the drive shaft (19) can be changed.
  • the drive shaft (19) connects the electric motor (13) and the compression mechanism (30).
  • the drive shaft (19) is rotatably supported by a first bearing part (21) and a second bearing part (22) that are fixed within the cylinder part (16).
  • the first bearing portion (21) is arranged at an intermediate portion of the drive shaft (19).
  • the second bearing portion (22) is arranged at the discharge side end of the drive shaft (19) (the end opposite to the electric motor (13)).
  • the first bearing part (21) is composed of a first bearing (21a) and a first bearing holder (21b).
  • the second bearing portion (22) includes a second bearing (22a) and a second bearing holder (22b).
  • the drive shaft (19) is supported by each bearing holder (21b, 22b) via each bearing (21a, 22a).
  • the first bearing (21a) and the second bearing (22a) may be collectively referred to simply as bearings (21a, 22a).
  • the first bearing holder (21b) and the second bearing holder (22b) may be collectively referred to simply as bearing holders (21b, 22b).
  • the bearing holder (21b, 22b) is formed into a substantially cylindrical shape that surrounds the entire circumference of the bearing (21a, 22a).
  • the outer peripheral surface of the bearing holder is fixed to the inner peripheral surface of the cylinder portion (16).
  • the first bearing holder (21b) and the second bearing holder (22b) are arranged to sandwich the screw rotor (40).
  • Each of the bearing parts (21) has a cylindrical peripheral wall (21c, 22c).
  • the peripheral wall (21c, 22c) is provided at the outer peripheral edge of the axial end surface of the bearing holder (21b, 22b).
  • the peripheral walls (21c, 22c) are formed along the inner circumferential surface of the cylinder portion (16). Specifically, the peripheral wall (21c, 22c) is arranged between the inner peripheral surface of the cylinder portion (16) and the outer peripheral surface of the end portion (42, 43) of the screw rotor (40). The outer peripheral surface of the peripheral wall (21c, 22c) is fixed to the inner peripheral surface of the cylinder part (16).
  • the inner peripheral surface of the peripheral wall (21c, 22c) is close to the outer peripheral surface of the end portion (42, 43) of the screw rotor (40).
  • the peripheral walls (21c, 22c) of the first bearing part (21) are referred to as first peripheral walls (21c), and the peripheral walls (21c, 22c) of the second bearing part (22) are referred to as second peripheral walls (22c).
  • the first peripheral wall (21c) is an example of the collar (21c) of the present disclosure.
  • the compression mechanism (30) has one cylinder part (16), one screw rotor (40), two gate rotors (50), and two slide valves (65).
  • the cylinder section (16) accommodates the screw rotor (40).
  • a first slit (16a) and a second slit (16b) are formed in the cylinder portion (16).
  • the first slit (16a) and the second slit (16b) are elongated openings extending in the cylinder axis direction.
  • the first slit (16a) and the second slit (16b) are arranged adjacent to each other in the circumferential direction.
  • a gate rotor (50) passes through each of the first slit (16a) and the second slit (16b). Details of the first slit (16a) and the second slit (16b) will be described later.
  • the cylinder portion (16) is provided with a valve accommodating portion (66) in which the slide valve (65) is accommodated.
  • Two valve housing portions (66) are provided in the circumferential direction of the cylinder portion (16). Each valve housing portion (66) is formed to bulge radially outward from the cylinder portion (16).
  • the outer peripheral wall of the valve accommodating part (66) is a partition wall (66a) that partitions the low pressure space (S1) and the high pressure space (S2), and a partition wall (66a) that extends from the widthwise center position of the partition wall (66a) toward the high pressure space (S2) side. It has a guide wall (66b) extending in the axial direction.
  • Screw rotor The screw rotor (40) is arranged inside the cylinder part (16).
  • the screw rotor (40) is a metal member formed into a generally cylindrical shape.
  • the screw rotor (40) is fixed to the drive shaft (19).
  • the screw rotor (40) rotates as the drive shaft (19) rotates.
  • the outer circumferential surface of the screw rotor (40) is close to the inner circumferential surface of the cylinder portion (16).
  • first end (42) Of both ends of the screw rotor (40) in the cylinder axis direction, one end is called a first end (42), and the other end is called a second end (43). Both the first end (42) and the second end (43) are formed into a cylindrical shape.
  • the first end (42) is an end on the suction side of the compression chamber (25), which will be described later.
  • the first end (42) is the suction side end (42) of the present disclosure.
  • the second end (43) is the discharge side end of the compression chamber (25).
  • the first end (42) is arranged adjacent to the first bearing part (21).
  • the second end (43) is arranged adjacent to the second bearing part (22).
  • the outer circumferential surface of the first end (42) will be referred to as a first outer circumferential surface (42a), and the end surface of the first end (42) will be referred to as a first end surface (42b).
  • the outer circumferential surface of the second end (43) is referred to as a second outer circumferential surface (43a), and the end surface of the second end (43) is referred to as a second end surface (43b).
  • the first outer circumferential surface (42a) and the second outer circumferential surface (43a) are along the inner circumferential surface of the cylinder portion (16). Specifically, the first outer circumferential surface (42a) is close to the inner surface of the first circumferential wall (21c) of the first bearing section (21), and the second outer circumferential surface (43a) is close to the inner surface of the first circumferential wall (21c) of the second bearing section (22). 2 Close to the inner surface of the peripheral wall (22c).
  • the first end surface (42b) and the second end surface (43b) are formed as flat surfaces perpendicular to the cylinder axis direction.
  • the first end surface (42b) faces the end surface of the first bearing holder (21b).
  • the second end surface (43b) faces the end surface of the second bearing holder (22b). Specifically, the first end surface (42b) is close to the end surface of the first bearing holder (21b), and the second end surface (43b) is close to the end surface of the second bearing holder (22b).
  • a plurality of screw grooves (41) extending spirally are formed on the outer peripheral surface of the screw rotor (40).
  • the screw groove (41) extends from the first end (42) to the second end (43) in the axial direction of the screw rotor (40).
  • the gate rotor (50) includes a first gate rotor (50a) and a second gate rotor (50b). Each gate rotor (50) has a plurality of gates (53) arranged radially. The gate (53) is inserted through the slits (16a, 16b) of the cylinder portion (16) and engages with the screw groove (41).
  • Each gate rotor (50) is supported by a gate rotor shaft (58).
  • the gate rotor shaft (58) extends in a direction perpendicular to the axial direction of the drive shaft (19).
  • the gate rotor shaft (58) is housed in a bearing housing (55) defined within the casing (11).
  • the gate rotor shaft (58) is rotatably supported via a ball bearing (56) provided within the bearing housing (55).
  • the gate rotor (50) and the gate rotor shaft (58) are arranged in the gate rotor chamber (18).
  • the gate rotor chamber (18) is defined within the casing (11) and adjacent to the cylinder portion (16).
  • the gate rotor chamber (18) includes a first gate rotor chamber (18a) and a second gate rotor chamber (18b).
  • a first gate rotor (50a) is arranged in the first gate rotor chamber (18a).
  • a second gate rotor (50b) is arranged in the second gate rotor chamber (18b).
  • the first gate rotor chamber (18a) is configured to supply refrigerant to a first compression chamber (23), which will be described later.
  • the second gate rotor chamber (18b) is configured to supply refrigerant flowing out from the first compression chamber (23) to a second compression chamber (24), which will be described later.
  • the slide valve (65) is housed in the valve housing section (66).
  • the slide valve (65) is configured to be slidable in the axial direction of the cylinder portion (16) by a drive mechanism (71) to be described later.
  • the slide valve (65) faces the outer peripheral surface of the screw rotor (40) while being inserted into the valve accommodating portion (66).
  • the drive mechanism (71) includes a cylinder portion (16), a piston (73), a piston rod (74), an arm (75), a connecting rod (76), and a spring (77).
  • the cylinder portion (16) is formed on the right side wall surface of the fixed plate (29).
  • the piston (73) is loaded into the cylinder section (16).
  • the piston rod (74) has one end fixed to the center of the piston (73) and extends to the left.
  • the arm (75) is connected to the other end of the piston rod (74).
  • the connecting rod (76) connects the arm (75) and the slide valve (65).
  • the spring (77) is provided on the connecting rod (76) so as to bias the arm (75) to the right.
  • the drive mechanism (71) controls the movement of the piston (73) by adjusting the gas pressure acting on the left and right end surfaces of the piston (73), and adjusts the position of the slide valve (65).
  • the slide valve (65) is a valve that can adjust the position of the screw rotor (40) in the axial direction.
  • This slide valve (65) can be used as an unloading mechanism that changes the operating capacity by returning the refrigerant that is being compressed in the compression chamber (25) to the suction side.
  • the slide valve (65) can be used as a compression ratio adjustment mechanism that adjusts the compression ratio (internal volume ratio) by adjusting the timing of discharging refrigerant from the compression chamber (25).
  • a fixed discharge port (not shown) is formed in the cylinder portion (16), which always communicates with the compression chamber (25) regardless of the position of the slide valve (65). This fixed port is provided to prevent the compression chamber (25) from being in a sealed state so as to avoid liquid compression when the screw compressor (10) is started up or under low load.
  • the compression chamber (25) includes a first compression chamber (23), which is the lower stage side of two-stage compression, and a second compression chamber (24), which is the higher stage side.
  • the first compression chamber (23) and the second compression chamber (24) are formed by a screw rotor (40) and a gate rotor (50) inside the cylinder part (16).
  • the first compression chamber (23) compresses the refrigerant at the suction pressure introduced into the casing (11) to an intermediate pressure higher than the suction pressure.
  • the second compression chamber (24) compresses the intermediate pressure refrigerant to a discharge pressure (high pressure) higher than the intermediate pressure.
  • the low pressure space (S1) communicates with the first compression chamber (23) via the first gate rotor chamber (18a).
  • Low pressure space (S1), first gate rotor chamber (18a), first compression chamber (23), second gate rotor chamber (18b) which is intermediate pressure space, second compression chamber (24), and high pressure space (S2 ) are connected in order from the side with lower refrigerant pressure to the side with higher refrigerant pressure.
  • the first slit (16a) communicates the low pressure space (S1) and the first gate rotor chamber (18a) with the first compression chamber (23).
  • the second slit (16b) communicates the second gate rotor chamber (18b), which is an intermediate pressure space, with the second compression chamber (24).
  • the first slit (16a) constitutes a first suction port that introduces the low-pressure refrigerant in the low-pressure space (S1) into the first compression chamber (23).
  • the second slit (16b) constitutes a second suction port that introduces the refrigerant in the intermediate pressure space into the second compression chamber (24).
  • the compression stroke shown in FIG. 5 is performed.
  • the shaded compression chamber (25) is completely closed. That is, the screw groove (41) corresponding to this compression chamber (25) is partitioned off from the suction side space by the gate (53).
  • the gate (53) approaches the end of the screw groove (41) as the screw rotor (40) rotates, the volume of the compression chamber (25) gradually decreases. As a result, the refrigerant in the compression chamber (25) is compressed.
  • the discharge stroke shown in FIG. 5 is performed.
  • the shaded compression chamber (25) (strictly speaking, the discharge chamber) communicates with the fixed discharge port via the discharge side end.
  • the gate (53) approaches the end of the screw groove (41)
  • the compressed refrigerant is pushed out from the compression chamber (25) through the fixed discharge port and into the discharge side space. It goes down.
  • the low-pressure refrigerant in the first gate rotor chamber (18a) is sucked into the first compression chamber (23) through the first slit (16a).
  • the intermediate pressure refrigerant compressed in the first compression chamber (23) flows out of the first compression chamber (23) and flows into the second gate rotor chamber (18b), which is an intermediate pressure space.
  • the intermediate pressure refrigerant in the second gate rotor chamber (18b) is sucked into the second compression chamber (24) through the second slit (16b).
  • the high-pressure refrigerant compressed in the second compression chamber (24) flows out of the second compression chamber (24) and flows into the high-pressure space (S2), which is the second space.
  • the oil in the refrigerant that has flowed into the high-pressure space (S2) is separated by an oil separator (not shown) and flows out of the casing (11) through the discharge port (10b).
  • the screw rotor The suction side end is required to have a suction cutless structure that seals the inner peripheral surface of the cylinder part and the outer peripheral surface of the screw rotor (corresponding to the first end (42) in this example).
  • the refrigerant sucked into such a screw compressor is sent to a low pressure space (S1), a first gate rotor chamber (18a), a first compression chamber (23), and a second intermediate pressure space. It flows in the order of the gate rotor chamber (18b), the second compression chamber (24), and the high pressure space (S2).
  • the intermediate pressure discharged refrigerant compressed in the first compression chamber (23) flows into the screw rotor (40) before flowing into the second gate rotor chamber (18b). It passes outside the first end (42), which is the suction side end. Since the inside of the first end (42) is at a low pressure due to the refrigerant sucked into the first compression chamber (23), a pressure difference occurs between the outside and inside of the first end (42). Therefore, the intermediate pressure refrigerant outside the first end (42) may flow through the gap between the first end (42) and the cylinder part (16) and flow into the first compression chamber (23) (Fig. 9 dashed line). When the intermediate pressure refrigerant flows into the suction side of the first compression chamber (23), the pressure difference between the suction pressure and the discharge pressure of the refrigerant becomes small in the first compression chamber (23), resulting in a decrease in compression efficiency.
  • the outer circumferential surface (42a) at the first end (42) that is the suction side end or the axial direction at the suction side end (42) A seal portion (80) for suppressing the flow of refrigerant is provided on the first surface (F) facing the first end surface (42b).
  • the seal portion (80) will be specifically explained below.
  • the seal portion (80) of this embodiment is provided in the first bearing portion (21). Specifically, the seal portion (80) is provided on the inner peripheral surface (F) of the first peripheral wall (21c).
  • the inner peripheral surface (F) of the first peripheral wall (21c) is an example of the first surface (F) facing the first end (42) of the present disclosure.
  • the seal portion (80) of this embodiment is a labyrinth seal.
  • the first circumferential wall (21c) has a plurality of grooves (81) formed along the entire circumference of its inner circumferential surface (F), which are lined up at regular intervals in the axial direction. be done.
  • the plurality of grooves (81) form an expansion chamber.
  • the intermediate pressure refrigerant flows into the gap (flow path) between the first end (42) and the first bearing holder (21b) and flows toward the first compression chamber (23). ) and expands (depressurizes), then flows into the flow path.
  • This refrigerant flows into the next groove (81) and is expanded (depressurized), and then flows into the flow path.
  • the intermediate pressure refrigerant repeatedly flows into the flow path from the expansion chamber multiple times.
  • the refrigerant flows from the expansion chamber to the flow path, its ease of flow is suddenly inhibited, resulting in flow resistance and pressure loss.
  • the occurrence of pressure loss can suppress the intermediate refrigerant from flowing into the first compression chamber (23).
  • the first end (42) (suction side end) of the screw rotor (40) has a first outer circumferential surface (42a) that is the inner circumferential surface of the cylinder portion (16). It is formed into a cylindrical shape along the A seal portion (80) for suppressing the flow of refrigerant is provided on the first surface (F) facing the first end portion (42).
  • the intermediate pressure refrigerant discharged from the first compression chamber (23) flows through the space outside the first end (42) when moving to the inlet of the second compression chamber (24).
  • the space inside the first end (42) is the first compression chamber (23) and forms a space into which low-pressure refrigerant is sucked, so a pressure difference is generated across the first end (42).
  • the seal portion (80) is provided on the first surface (F) that the first end (42) faces, so that the intermediate pressure refrigerant can flow between the first end (42) and the first surface. (F) can be suppressed from being distributed between. As a result, a sufficient level differential pressure within the compression chamber can be ensured, and a decrease in the capacity of the screw compressor can be suppressed.
  • the screw compressor (10) of this embodiment includes a first bearing part (21) fixed within the cylinder part (16) and supporting the drive shaft (19).
  • the first bearing portion (21) is arranged adjacent to the first end portion (42), and the seal portion (80) is provided on the first bearing portion (21).
  • the first surface (F) of the first end (42) is located on the first bearing holder (21b), and the seal portion (80) is provided on the first bearing holder (21b).
  • the first bearing portion (21) has a bearing function for the drive shaft (19) and a sealing function for suppressing the flow of refrigerant.
  • the seal part (80) can be provided before installing the first bearing holder (21b) into the cylinder part (16), it is easier to install the seal part (80) than if the seal part (80) is provided inside the cylinder part (16).
  • the seal portion (80) can be easily formed.
  • the first bearing portion (21) has a first peripheral wall (21c) disposed between the inner surface of the cylinder portion (16) and the outer peripheral surface of the first end portion (42). ) (flange portion), and the seal portion (80) is provided on the first peripheral wall (21c).
  • the seal portion (80) can be provided on the inner peripheral surface of the first peripheral wall (21c). Moreover, the inner peripheral surface of the first peripheral wall (21c) and the first end surface (42b) can increase the contact area between the first bearing holder (21b) and the first end (42). By increasing this area, the flow path through which the refrigerant flows, which is the gap between the first bearing holder (21b) and the first end (42), can be lengthened. The effect of suppressing the flow of refrigerant can be increased.
  • the compression chamber (25) includes a first compression chamber (23) that compresses the suction pressure fluid introduced into the casing (11) to an intermediate pressure, and a first compression chamber (23) that compresses the fluid at the suction pressure introduced into the casing (11) to an intermediate pressure. and a second compression chamber (24) for compressing the fluid to the discharge pressure.
  • a part of the intermediate pressure fluid discharged from the first compression chamber (23) passes through the suction side end (42) again during the process of moving to the second compression chamber (24). Inhalation into the first compression chamber (23) can be suppressed.
  • the seal portion (80) is configured with a labyrinth seal. Thereby, the seal portion (80) can be configured relatively easily.
  • the above embodiment may have the following configuration. Below, configurations different from those of the above embodiment will be explained.
  • the seal portion (80) in this example has a surface texture (surface texturing).
  • the surface texture is formed on the inner peripheral surface of the first peripheral wall (21c).
  • Rayleigh steps that generate positive pressure and reverse Rayleigh steps that generate negative pressure are formed as appropriate.
  • the Rayleigh step can suppress friction between the inner peripheral surface of the first peripheral wall (21c) and the outer peripheral surface of the first end (42).
  • the reverse Rayleigh step the refrigerant flowing into the gap between the inner peripheral surface of the first peripheral wall (21c) and the outer peripheral surface of the first end (42) can be sucked back.
  • a reverse Rayleigh step may be adopted so that the intermediate pressure refrigerant does not flow into the first compression chamber (23).
  • the seal portion (80) of this example is formed on the surface facing the first end surface (42b) of the first bearing holder (21b).
  • the surface facing the first end surface (42b) is an example of the first surface (F) of the present disclosure.
  • a plurality of concave grooves (81) are formed on the first end surface (42b) concentrically around the cylindrical axis of the first bearing holder (21b). are formed at intervals of .
  • the seal portion (80) of this example is formed on the inner peripheral surface of the first peripheral wall (21c) and the first end surface (42b) of the first bearing holder (21b).
  • the seal portions (80) are provided on both surfaces facing the first end (42) in this manner, the refrigerant is prevented from flowing into the gap between the first end (42) and the bearing holder (21b, 22b). It can definitely be suppressed.
  • the first bearing part (21) of this example does not have the first bearing holder (21b).
  • the first bearing (21a) is embedded inside the cylinder part (16), and a cylinder end face (26) facing the first end face (42b) is formed inside the cylinder part (16).
  • the first surface (F) of the present disclosure is the inner peripheral surface of the cylinder part (16) facing the first outer peripheral surface (42a), and the cylinder end surface (26) facing the first end surface (42b).
  • the seal portion (80) is provided on the inner circumferential surface of the cylinder portion (16) facing the first outer circumferential surface (42a).
  • the seal portion (80) may be provided on the cylinder end surface (26) opposite to the end surface of the first end (42). Further, the seal portion (80) is attached to both the inner peripheral surface of the cylinder portion (16) facing the first outer peripheral surface (42a) and the cylinder end surface (26) facing the end surface of the first end portion (42). may be provided.
  • the refrigerant circuit (2) of this example includes an economizer circuit (90).
  • the economizer circuit (90) of this example supplies intermediate pressure refrigerant to the compression chamber (25).
  • the arrows in FIG. 14 indicate the direction in which the refrigerant flows.
  • a gas-liquid separation space (S3) in which the refrigerant is separated into gas and liquid is formed within the casing (11) of this example.
  • the gas-liquid separation space (S3) is adjacent to the suction side of the compression chamber (25).
  • the high pressure space (S2) within the casing (11) is adjacent to the discharge side of the compression chamber (25).
  • a refrigerant suction port is provided on the suction side of the compression chamber (25).
  • the screw compressor (10) of this example is configured in a single stage.
  • the inflow side of the condenser (3) communicates with the high pressure space of the screw compressor (10).
  • the outflow side of the condenser (3) communicates with the gas-liquid separation space (S3) of the screw compressor (10).
  • a first expansion valve (4a) is provided between the condenser (3) and the gas-liquid separation space (S3).
  • the inflow side of the evaporator (5) communicates with the gas-liquid separation space (S3) of the screw compressor (10).
  • the outflow side of the evaporator (5) communicates with the suction side of the compression chamber (25) of the screw compressor (10).
  • a second expansion valve (4b) is provided between the gas-liquid separation space (S3) and the evaporator (5).
  • the economizer circuit (90) communicates the gas-liquid separation space (S3) and the compression chamber (25). In the economizer circuit (90), the gas phase intermediate pressure refrigerant in the gas-liquid separation space (S3) flows into the intermediate pressure space in the compression chamber (25).
  • a flow rate control valve (91) is connected to the economizer circuit (90). The flow control valve (91) adjusts the flow rate of refrigerant flowing into the economizer circuit (90).
  • the compression chamber (25) is adjacent to the gas-liquid separation space (S3) on its suction side. Therefore, the seal part (80) allows the intermediate pressure refrigerant in the gas-liquid separation space (S3) to flow through the gap between the first end (42) of the screw rotor (40) and the cylinder part (16) into the compression chamber. (25).
  • the seal portion (80) may also be provided on the second bearing holder (22b).
  • the seal portion (80) may also be provided on the inner peripheral surface of the second peripheral wall (22c).
  • the first bearing holder (21b) does not need to have the first peripheral wall (21c).
  • the first surface (F) of the present disclosure includes the inner peripheral surface of the cylinder part (16) facing the first outer peripheral surface (42a) and the end surface of the bearing holder (21b, 22b) facing the first end surface (42b). It is.
  • the seal portion (80) is attached to the inner peripheral surface of the cylinder portion (16) facing the first outer peripheral surface (42a), the end surface of the bearing holder (21b, 22b) facing the first end surface (42b), or both. provided.
  • the seal portion (80) only needs to be able to suppress the flow between the inside (compression chamber) of the first end (42) and the space outside the first end (42); It may be configured to suppress the distribution of either one.
  • the labyrinth of the seal portion (80) may be an axial labyrinth, a radial labyrinth, an aligned labyrinth, or the like.
  • the refrigeration device (1) may be applied to a water heater, a chiller unit, or a cooling device that cools the air inside the refrigerator.
  • the present disclosure is useful for screw compressors and refrigeration equipment.
  • Air conditioner (refrigeration equipment) 10 Screw compressor 11 Casing 13 Electric motor 16 Cylinder section 19 Drive shaft 21 First bearing section (bearing section) 21c 1st peripheral wall (brim part) 23 Compression chamber 24 First compression chamber 25 Second compression chamber 40 Screw rotor 41 Screw groove 42 First end (suction side end) 50 Gate rotor 53 Gate 80 Seal part F 1st surface (inner peripheral surface)

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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 fournit un compresseur à vis dans lequel une chambre de compression (25) est formée à l'intérieur d'une partie cylindre (16) par un rotor à vis (40) et une grille (53), une partie d'extrémité côté admission (42) du rotor à vis (40) étant formée en une forme cylindrique de sorte qu'une surface périphérique externe (42a) de ladite partie d'extrémité se conforme à la surface périphérique interne de la partie cylindre (16), et une partie d'étanchéité (80) qui réduit au minimum l'écoulement d'un fluide est disposée dans une première surface (F) en direction de laquelle la surface périphérique externe (42a) de la partie d'extrémité côté admission (42) ou une première surface d'extrémité dans la direction axiale (42b) de la partie d'extrémité côté admission (42) fait face.
PCT/JP2023/011627 2022-03-23 2023-03-23 Compresseur à vis et congélateur WO2023182457A1 (fr)

Applications Claiming Priority (2)

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JP2022-047041 2022-03-23
JP2022047041 2022-03-23

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WO2023182457A1 true WO2023182457A1 (fr) 2023-09-28

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Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003286986A (ja) * 2002-03-27 2003-10-10 Mitsubishi Electric Corp シングルスクリュー圧縮機
JP2009275567A (ja) * 2008-05-14 2009-11-26 Mitsubishi Electric Corp スクリュー圧縮機
JP2010249046A (ja) * 2009-04-16 2010-11-04 Mitsubishi Electric Corp スクリュー圧縮機
JP2010249047A (ja) * 2009-04-16 2010-11-04 Mitsubishi Electric Corp スクリュー圧縮機
JP2010249045A (ja) * 2009-04-16 2010-11-04 Mitsubishi Electric Corp スクリュー圧縮機
JP2013536916A (ja) * 2010-08-30 2013-09-26 オスコンプ システムズ インク 液体注入による冷却を行う圧縮機
WO2018051867A1 (fr) * 2016-09-14 2018-03-22 イーグル工業株式会社 Joint mécanique
US20200300244A1 (en) * 2019-03-22 2020-09-24 Vilter Manufacturing Llc Seal assembly for high pressure single screw compressor
JP2021162021A (ja) * 2020-03-31 2021-10-11 ダイキン工業株式会社 スクリュー圧縮機及び冷凍装置

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003286986A (ja) * 2002-03-27 2003-10-10 Mitsubishi Electric Corp シングルスクリュー圧縮機
JP2009275567A (ja) * 2008-05-14 2009-11-26 Mitsubishi Electric Corp スクリュー圧縮機
JP2010249046A (ja) * 2009-04-16 2010-11-04 Mitsubishi Electric Corp スクリュー圧縮機
JP2010249047A (ja) * 2009-04-16 2010-11-04 Mitsubishi Electric Corp スクリュー圧縮機
JP2010249045A (ja) * 2009-04-16 2010-11-04 Mitsubishi Electric Corp スクリュー圧縮機
JP2013536916A (ja) * 2010-08-30 2013-09-26 オスコンプ システムズ インク 液体注入による冷却を行う圧縮機
WO2018051867A1 (fr) * 2016-09-14 2018-03-22 イーグル工業株式会社 Joint mécanique
US20200300244A1 (en) * 2019-03-22 2020-09-24 Vilter Manufacturing Llc Seal assembly for high pressure single screw compressor
JP2021162021A (ja) * 2020-03-31 2021-10-11 ダイキン工業株式会社 スクリュー圧縮機及び冷凍装置

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