WO2011077724A1 - シングルスクリュー圧縮機 - Google Patents
シングルスクリュー圧縮機 Download PDFInfo
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- WO2011077724A1 WO2011077724A1 PCT/JP2010/007447 JP2010007447W WO2011077724A1 WO 2011077724 A1 WO2011077724 A1 WO 2011077724A1 JP 2010007447 W JP2010007447 W JP 2010007447W WO 2011077724 A1 WO2011077724 A1 WO 2011077724A1
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- discharge
- load
- slide valve
- screw
- screw rotor
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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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
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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
- F04C18/48—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
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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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
- F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
Definitions
- the present invention relates to a single screw compressor, and particularly relates to a slide valve structure of a variable VI mechanism (volume ratio adjusting mechanism) that adjusts a ratio (volume ratio: VI) between a suction volume and a discharge volume.
- a variable VI mechanism volume ratio adjusting mechanism
- a single screw compressor (see FIG. 9) having a compression mechanism for compressing a refrigerant by a rotary motion of a screw rotor is known.
- This single screw compressor (hereinafter referred to as a screw compressor) (100) is formed through the opening of the cylinder wall (131) into the screw rotor (140) rotating in the cylinder wall (131) of the casing (130).
- the compression chamber (123) is formed by meshing the gate rotor (150).
- the screw rotor (140) has one end (the left end in the figure) on the suction side and the other end (the right end in the figure) on the discharge side.
- variable VI mechanism volume ratio adjusting mechanism
- VI volume ratio between the suction volume and the discharge volume
- a slide valve (104) that moves in a moving manner (for example, see Patent Document 1).
- the slide valve (104) is slid in the axial direction of the screw rotor (140) to change the discharge volume by changing the position at which high-pressure gas starts to be discharged (compression is completed). The ratio is changed.
- the screw compressor (100) is configured to change the rotational speed of an electric motor (not shown) by performing inverter control, thereby controlling the operating capacity.
- the operating capacity (refrigerant discharge amount per unit time) is controlled according to the load on the usage side of the refrigerant circuit.
- the slide valve (104) of the variable VI mechanism (103) is controlled so as to have a volume ratio (compression ratio) at which optimum compression efficiency is obtained with respect to the operating capacity controlled according to the load.
- the position of the slide valve (104) in the axial direction of the screw rotor (140) changes according to the operating capacity that changes depending on whether the operating state is the rated load (100% load) state or the partial load state. (See FIGS. 10A and 10B).
- the discharge side end face (104a) of the slide valve (104) is located along the top of the mountain between the screw lands (142) (screw spirals of the screw rotor (140) facing each other so that the pressure loss of the discharge fluid is reduced. It is preferable to form in a shape corresponding to the surface.
- the screw land (142) is not uniform in angle and width from the suction side to the discharge side. Therefore, conventionally, as shown in FIG. 10A, in order to effectively reduce the pressure loss of the discharged fluid at the rated load at which the operating capacity is maximum, the discharge side end face (104a) of the slide valve (104). Was formed in a shape corresponding to the inclination of the screw land (142) facing each other at the rated load.
- the discharge-side end face (104a) of the slide valve (104) has a shape corresponding to the inclination of the screw land (142) facing at the rated load, since the inclination is steep, as shown in FIG.
- the discharge-side end face (104a) straddles the gently sloping screw land (142) at the time of partial load. Therefore, the compression chambers adjacent to each other across the screw land (142) communicate with each other at the time of partial load, so that the desired compression ratio cannot be obtained and the efficiency may be reduced.
- the present invention has been made in view of the above points, and an object of the present invention is to reduce the pressure loss of discharged fluid in a rated load operation state and a partial load operation state in a single screw compressor having a variable volume ratio. And to prevent a decrease in efficiency.
- the first invention comprises a screw rotor (40) having a spiral groove (41) formed on the outer peripheral surface with one end on the fluid suction side and the other end on the discharge side, and rotatably accommodates the screw rotor (40).
- the drive mechanism (26) for driving the screw rotor (40) in a variable speed according to the load and the screw in the slide groove (33) formed in the cylinder wall (31)
- Single screw compression provided with a slide valve (4) that faces the outer peripheral surface of the rotor (40) and is movable in the axial direction and moves in the axial direction according to the rotational speed to adjust the discharge start position
- the discharge-side end face (4a) of the slide valve (4) is an extension of the land (42) of the screw rotor (40) facing the slide position in the partial load operating state smaller than the rated load. It is formed to extend in a direction corresponding to the direction.
- the slide valve (4) moves to the discharge side in the axial direction to delay the discharge start position as the load increases. That is, the discharge-side end face (4a) of the slide valve (4) is opposed to the wide and steep inclination portion of the land (42) of the screw rotor (40) at the rated load, but is smaller than the rated load. At the time of partial load, the land (42) of the screw rotor (40) is opposed to a portion having a narrow width and a gentle inclination angle.
- the discharge side end face (4a) of the slide valve (4) does not straddle the land (42) of the opposing screw rotor (40), and adjacent compression chambers (spiral grooves (41 )) Not communicating with each other.
- the land (42) of the screw rotor (40) that faces the discharge-side end face (4a) of the slide valve (4) during partial load has a gentler inclination angle than the land (42) that faces when the load is rated If the discharge-side end face (4a) of the slide valve (4) is made to correspond to the slope of the land (42) that faces when the load is partial, the discharge-side end face (4a) of the slide valve (4) faces the land ( 42) is not straddled, and adjacent compression chambers (spiral grooves (41)) do not communicate with each other. That is, the compression chambers adjacent to each other across the land (42) of the screw rotor (40) do not communicate with each other not only at the partial load but also at the rated load.
- the discharge-side end face (4a) of the slide valve (4) has a screw rotor (40) opposed in a sliding position in an operating state with a load factor of 50% to 75%. It is formed to extend in a direction corresponding to the extending direction of the land (42).
- the discharge-side end face (4a) of the slide valve (4) has a screw rotor (40) opposed at a slide position in an operating state with a load factor of 50% to 75%. It is formed to extend in a direction corresponding to the suction side end of the land (42).
- the discharge-side end face (4a) of the slide valve (4) is formed by the screw rotor (40) facing the slide position in an operating state with a load factor of 50% or more and 75% or less. It is formed in a curved surface shape corresponding to the suction side end of the land (42).
- the period coefficient of performance is known as the coefficient of performance (COP) of the refrigeration apparatus.
- This period coefficient of performance is a concept of obtaining the annual COP by weighting the COP at each load, since there are a period with a large load, a period with a small load, an intermediate period, etc. throughout the year.
- COP at the time of partial load should be emphasized when obtaining the period coefficient of performance, and in particular, COP in an operating state with a load rate of 50% or more and 75% or less with a high cumulative appearance frequency in the year is emphasized. It is considered preferable.
- the slide valve (4) extends in a direction corresponding to the land (42) of the opposing screw rotor (40) in an operating state with a load factor of 50% to 75%.
- the discharge side end face (4a) of the slide valve (4) is formed.
- the slide valve (4 ) are formed in a curved shape corresponding to the suction side end of the land (42) of the screw rotor (40) facing each other.
- the discharge-side end face (4a) of the slide valve (4) is formed by the narrowest narrow part (42a) of the land (42) of the screw rotor (40). It is formed so as to extend in a direction corresponding to the extending direction.
- the narrow portion (42a) of the land (42) of the screw rotor (40) whose width and angle are not uniform is narrower than the other portions and has a gentle inclination angle. Therefore, if the discharge side end face (4a) of the slide valve (4) is configured to extend in a direction corresponding to the extending direction of the narrow portion (42a) of the land (42) of the screw rotor (40), the slide valve (4 ) Discharge side end face (4a) does not straddle the land (42) even if it faces any part of the land (42) of the screw rotor (40), and the adjacent compression chamber (spiral groove (41)) They do not communicate with each other.
- the present invention it is possible to prevent communication between the compression chambers adjacent to each other with the land (42) of the screw rotor (40) sandwiched between the rated load operation state and the partial load operation state. Therefore, it is possible to prevent the pressure loss and efficiency reduction of the discharged fluid at the time of partial load and rated load.
- the second to fourth inventions it is possible to reliably prevent the pressure loss and the efficiency reduction of the discharged fluid particularly in the operation state in which the load factor having a high cumulative appearance frequency in the year is 50% or more and 75% or less. Therefore, it is possible to improve the period performance coefficient and significantly reduce the period power consumption.
- the fifth aspect of the invention it is possible to prevent the pressure loss and the efficiency reduction of the discharged fluid in all the movable ranges of the slide valve (4). Therefore, it is possible to prevent the pressure loss and efficiency reduction of the discharged fluid at the time of partial load and rated load.
- FIG. 1 is a longitudinal sectional view showing a configuration of a main part of a screw compressor according to Embodiment 1 of the present invention in a high VI operation state corresponding to a rated load.
- FIG. 2 is a longitudinal sectional view showing a configuration of a main part of the screw compressor of FIG. 1 in a low VI operation state corresponding to a partial load.
- 3 is a cross-sectional view taken along line III-III in FIG.
- FIG. 4 is a perspective view showing an essential part of the screw compressor.
- FIG. 5 is a perspective view showing a screw rotor of the screw compressor.
- FIG. 6 is a development view showing the operating state of the slide valve, where FIG. 6 (A) is an operating state at a rated load, FIG.
- FIG. 6 (B) is an operating state at a load factor of 75%
- FIG. 6 (C) is a load factor
- FIG. 6D shows an operating state with a load factor of 25%
- FIG. 7 is a plan view showing the operation of the compression mechanism of the screw compressor
- FIG. 7 (A) shows the suction stroke
- FIG. 7 (B) shows the compression stroke
- FIG. 7 (C) shows the discharge stroke.
- FIG. 8 is a development view showing the relationship between the slide valve and the screw rotor according to the second embodiment.
- FIG. 9 is a longitudinal sectional view of a conventional screw compressor.
- FIG. 10 is a development view showing an operating state of a slide valve of a conventional screw compressor.
- FIG. 10A shows an operating state at a rated load and FIG.
- FIG. 10B shows an operating state at a partial load.
- FIG. 11 is a longitudinal sectional view showing the configuration of the main part of the screw compressor according to Embodiment 3 of the present invention in a high VI operation state corresponding to the rated load.
- FIG. 12 is a longitudinal sectional view showing a configuration of a main part of the screw compressor of FIG. 11 in a low VI operation state corresponding to a partial load.
- 13 is a cross-sectional view taken along line XIII-XIII in FIG.
- FIG. 14 is a perspective view showing an essential part of the screw compressor.
- FIG. 15 is a perspective view showing a screw rotor of a screw compressor.
- FIG. 16 is a development view showing the operating state of the slide valve.
- FIG. 16A is the rated load operating state
- FIG. 16A is the rated load operating state
- FIG. 16B is the 75% load operating state
- FIG. 16C is the 50% load
- FIG. 16D shows an operating state of 25% load
- FIG. 17 is a plan view showing the operation of the compression mechanism of the screw compressor
- FIG. 17 (A) shows the suction stroke
- FIG. 17 (B) shows the compression stroke
- FIG. 17 (C) shows the discharge stroke.
- FIG. 18 is a longitudinal sectional view of a conventional screw compressor.
- FIG. 19A is a development view showing the shape of the discharge port of a conventional screw compressor
- FIG. 19B is a development view showing a modification thereof.
- Embodiment 1 of the Invention The single screw compressor (1) of the first embodiment (hereinafter simply referred to as a screw compressor) is provided in a refrigerant circuit that performs a refrigeration cycle and compresses the refrigerant.
- the screw compressor (1) includes a compression mechanism (20) and a variable VI mechanism (volume ratio adjustment mechanism) that adjusts the ratio (volume ratio: VI) between the suction volume and the discharge volume in the compression mechanism (20). And 3).
- the compression mechanism (20) includes a cylinder wall (31) formed in a casing (30) of the screw compressor (1), and a cylinder wall (31).
- One screw rotor (40) rotatably arranged on the two and two gate rotors (50) meshing with the screw rotor (40).
- the communication part (32) includes a slide groove (33) extending along the axial direction of the cylinder wall (31), and a slide valve (4) described later can be moved in the axial direction in the slide groove (33). It is attached to.
- the slide groove (33) and the slide valve (4) constitute the variable VI mechanism (3).
- the discharge port (25) includes a valve side discharge port (27) formed in the slide valve (4) and a cylinder side discharge port (28) formed in the cylinder wall (31). It is.
- the drive shaft (21) extending from the electric motor (not shown) is inserted through the screw rotor (40).
- the screw rotor (40) and the drive shaft (21) are connected by a key (22), and the screw rotor (40) is driven by a drive mechanism (26) including the electric motor and the drive shaft (21). ing.
- the drive shaft (21) is arranged coaxially with the screw rotor (40).
- the tip of the drive shaft (21) is freely rotatable by a bearing holder (60) located on the discharge side of the compression mechanism (20) (the right side when the axial direction of the drive shaft (21) in FIG. 1 is the left-right direction). It is supported by.
- the bearing holder (60) supports the drive shaft (21) via a ball bearing (61).
- the screw rotor (40) is rotatably fitted to the cylinder wall (31), and its outer peripheral surface is in sliding contact with the inner peripheral surface of the cylinder wall (31) via an oil film.
- the motor is configured so that the rotation speed can be adjusted by inverter control.
- the screw compressor (1) can change the operating capacity by adjusting the rotational speed of the electric motor.
- the operating capacity (refrigerant discharge amount per unit time) of the screw compressor (1) is controlled according to the load on the usage side of the refrigerant circuit.
- the slide valve (4) of the variable VI mechanism (3) is controlled so as to obtain a volume ratio (compression ratio) at which an optimum compression efficiency is obtained with respect to the operation capacity controlled according to the load.
- the slide valve ( 4) The position changes in the axial direction of the screw rotor (40).
- the slide valve (4) has a small load when compared with the rated load operation state (state of FIG. 1) and the partial load operation state (state of FIG. 2).
- the position changes to the left side (suction side) so that the area of the cylinder side discharge port (28) becomes larger in the operating state.
- the screw rotor (40) shown in FIGS. 4 and 5 is a metal member formed in a substantially cylindrical shape. On the outer peripheral surface of the screw rotor (40), a spiral groove extending in a spiral shape from one end of the screw rotor (40) (end on the suction side of the fluid (refrigerant)) to the other end (end on the discharge side) 41) are formed (six in the first embodiment).
- Each screw groove (41) of the screw rotor (40) has a left end (end portion on the suction side) in FIG. 5 as a start end and a right end in the drawing ends (end on the fluid discharge side). Further, the screw rotor (40) has a tapered left end in the figure. In the screw rotor (40) shown in FIG. 5, the start end of the spiral groove (41) is opened at the left end face formed in a tapered surface, while the end of the spiral groove (41) is not opened at the right end face. .
- Each gate rotor (50) is a resin member. Each gate rotor (50) is radially provided with a plurality of (11 in the first embodiment) gates (51) formed in a rectangular plate shape. Each gate rotor (50) is arranged outside the cylinder wall (31) so as to be axially symmetric with respect to the rotational axis of the screw rotor (40). That is, in the screw compressor (1) of the first embodiment, the two gate rotors (50) are arranged at equiangular intervals (180 ° intervals in the first embodiment) around the rotation center axis of the screw rotor (40). Has been. The axis of each gate rotor (50) is orthogonal to the axis of the screw rotor (40). Each gate rotor (50) is arranged so that the gate (51) penetrates a part (not shown) of the cylinder wall (31) and meshes with the spiral groove (41) of the screw rotor (40).
- the gate rotor (50) is attached to a metal rotor support member (55) (see FIG. 4).
- the rotor support member (55) includes a base portion (56), an arm portion (57), and a shaft portion (58).
- the base (56) is formed in a slightly thick disk shape.
- the same number of arms (57) as the gates (51) of the gate rotor (50) are provided and extend radially outward from the outer peripheral surface of the base (56).
- the shaft portion (58) is formed in a rod shape and is erected on the base portion (56).
- the central axis of the shaft portion (58) coincides with the central axis of the base portion (56).
- the gate rotor (50) is attached to a surface of the base portion (56) and the arm portion (57) opposite to the shaft portion (58). Each arm part (57) is in contact with the back surface of the gate (51).
- the rotor support member (55) to which the gate rotor (50) is attached is accommodated in a gate rotor chamber (90) defined in the casing (30) adjacent to the cylinder wall (31) (see FIG. 3).
- the rotor support member (55) disposed on the right side of the screw rotor (40) in FIG. 3 is installed in such a posture that the gate rotor (50) is on the lower end side.
- the rotor support member (55) disposed on the left side of the screw rotor (40) in the figure is installed in such a posture that the gate rotor (50) is on the upper end side.
- each rotor support member (55) is rotatably supported by a bearing housing (91) in the gate rotor chamber (90) via ball bearings (92, 93).
- Each gate rotor chamber (90) communicates with the suction chamber (S1).
- the compression chamber (23) includes a first compression chamber (23a) located above the horizontal center line in FIG. 3 and a second compression chamber (23b) located below the center line. (See FIG. 5).
- the spiral groove (41) of the screw rotor (40) is opened to the suction chamber (S1) at the suction side end, and this open part is the suction port (24) of the compression mechanism (20).
- variable VI mechanism (3) includes a slide groove (33) of the communicating portion (32) of the cylinder wall (31) and a slide accommodated so as to be slidably fitted in the slide groove (33).
- valve (4) includes a hydraulic cylinder (5) fixed to the discharge side of the bearing holder (60) and positioned in the discharge chamber (S2) (see FIGS. 1 and 2).
- the slide valve (4) is provided in both the first and second compression chambers (23a, 23b). As described above, the slide valve (4) and the cylinder wall (31) are provided on the valve side discharge port (27) and the cylinder side discharge port (28) constituting the discharge port (25) of the compression mechanism (20). ) Are formed, and the compression chamber (23) and the discharge chamber (S2) communicate with each other through the discharge port (25). Further, the inner surface of the slide valve (4) constitutes a part of the inner peripheral surface of the cylinder wall (31) and is slidable in the axial direction of the cylinder wall (31). One end of the slide valve (4) faces the discharge chamber (S2), and the other end faces the suction chamber (S1).
- the hydraulic cylinder (5) includes a cylinder tube (6), a piston (7) loaded in the cylinder tube (6), and an arm (9) connected to the piston rod (8) of the piston (7). ), A connecting rod (10a) for connecting the arm (9) and the slide valve (4), and the arm (9) in the right direction in FIG. 1 (direction in which the arm (9) is separated from the casing (30)). And a spring (10b) for biasing. Further, on both sides of the piston (7) in the cylinder tube (6), a first cylinder chamber (11) (left side of the piston (7) in FIG. 1) and a second cylinder chamber (12) (piston (in FIG. The right side of 7) is formed.
- the hydraulic cylinder (5) is configured to adjust the position of the slide valve (4) by adjusting the pressure in the left and right cylinder chambers (11, 12) of the piston (7).
- FIG. 1 shows a state in which the slide valve (4) is slid to the right. In this state, the discharge port (25) is opened substantially near the end of the spiral groove (41).
- This state is a state corresponding to the rated load operation state (high VI operation state). In the screw compressor (1), this state is the state with the latest discharge timing, and the compression ratio is the largest.
- FIG. 2 shows a state in which the slide valve (4) is slid to the left.
- the discharge port (25) is opened near the middle of the spiral groove (41).
- This state is a state corresponding to the partial load operation state (low VI operation state).
- the discharge timing is earlier than in the high VI operation state (see FIG. 1), and the compression ratio is smaller than in the high VI operation state.
- the optimum VI value is selected so that the screw compressor (1) has the highest efficiency according to the operating state of the refrigerant circuit, and the position of the slide valve (4) is adjusted. It has become.
- the rotational speed of the electric motor is controlled by inverter control according to the operating state (use side load) by a control mechanism (not shown), and capacity control is performed.
- the slide valve (4) is provided with a detent (not shown) so that the inner peripheral surface is in sliding contact with the outer peripheral surface of the valve guide (15) regardless of the position during operation.
- the inner peripheral surface of the slide valve (4) is held in a state of being located on the same cylinder as the inner peripheral surface of the cylinder wall (31) of the casing (30). Therefore, in the first embodiment, the slide valve (4) does not rotate, and the inner peripheral surface of the slide valve (4) and the outer peripheral surface of the screw rotor (40) do not interfere with each other.
- the cylinder side discharge port (28) constituting the discharge port (25) has a main discharge port (28a) and sub discharge ports (28b, 28c) as shown in FIGS. 6 (A) to 6 (D). 28d).
- the main discharge port (28a) is a port whose opening shape is determined in accordance with the position of the slide valve (4) in the rated load operation state, and is shown in FIGS. 6 (A) to 6 (D). As described above, the port is opened without being closed by the slide valve (4) in both the rated load operation state and the partial load operation state, and the fluid is discharged.
- the auxiliary discharge ports (28b, 28c, 28d) are ports whose opening shape is determined according to the position of the slide valve (4) in the partial load operation state. While being closed by 4), it is a port that is opened from the slide valve (4) in a partially loaded state and discharges fluid.
- a plurality of ports are provided as the auxiliary discharge ports (28b, 28c, 28d) so as to correspond to a plurality of partial load operation states.
- the sub-discharge ports (28b, 28c, 28d) are composed of three ports corresponding to operating conditions of a load factor of 75%, a load factor of 50%, and a load factor of 25%.
- the main discharge port (28a) and the sub discharge ports (28b, 28c, 28d) are formed at positions separated from each other.
- FIGS. 6 (B) to 6 (D) are views showing the positional relationship between the slide valve (4) and the cylinder-side discharge port (28) in a state where the screw rotor (40) is deployed.
- the sub discharge port (28b) (referred to as the first sub discharge port (28b)) corresponding to the operation state with a load factor of 75% is operated at the rated load operation state as shown in FIG. 6 (A) by the slide valve (4).
- FIGS. 6 (B) to 6 (D) it is formed at a position where it is opened in an operating state where the load factor is 75%, the load factor is 50%, and the load factor is 25%.
- the sub discharge port (28c) (referred to as the second sub discharge port (28c)) corresponding to the operation state with a load factor of 50% is shown in FIGS. 6 (A) and 6 (B) by the slide valve (4). 6C is closed at the rated load and an operating state with a load factor of 75%, while being opened at an operating state with a load factor of 50% and a load factor of 25% as shown in FIGS. Is formed.
- the sub discharge port (28d) (referred to as the third sub discharge port (28d)) corresponding to the operating state with a load factor of 25% is changed to the state shown in FIGS. As shown in FIG. 6 (D), the load is closed at the rated load, the load factor of 75% and the load factor of 50%, and is opened at the load factor of 25%. .
- the discharge-side end face (4a) of the slide valve (4) is located between the screw land (42) and the spiral groove (41) of the screw rotor (40) that the slide valve (4) faces in the partial load operation state.
- the surface along the top of the mountain is extended in a direction corresponding to the extending direction.
- the discharge side end face (4a) of the slide valve (4) has a load factor of 50% or more and 75% or less as shown in FIGS. 6 (B) and 6 (C).
- the inclination of the screw land (42) that is opposed in the operating state (this inclination is determined by changing the two points P and Q at the corners of the discharge side end face (4a) in FIGS.
- Each of the sub discharge ports (28b, 28c, 28d) has a corresponding portion (line segment P′Q) of the screw land (42) which is a reference for the inclination of the discharge side end surface (4a) of the slide valve (4). It is formed with a narrower width than the part corresponding to '). Further, the plurality of sub discharge ports (28b, 28c, 28d) are formed so that the width becomes narrower from the discharge side toward the suction side. As shown in FIGS. 6 (A) to 6 (D), the screw land (42) of the slide valve (4) facing the discharge side end face (4a) in the movable range of the slide valve (4) is arranged. The width of each sub-discharge port (28b, 28c, 28d) is set in accordance with the narrowing of the width from the discharge side toward the suction side.
- the discharge-side end face (4a) of the slide valve (4) is inclined to the suction-side end of the screw land (42) that opposes the operating state with a load factor of 50% to 75% as described above.
- the reason why it is formed so as to correspond is as follows.
- a period performance coefficient is known as a coefficient of performance (COP) of a refrigeration apparatus.
- This period coefficient of performance is a concept of obtaining the annual COP by weighting the COP at each load, since there are a period with a large load, a period with a small load, an intermediate period, etc. throughout the year.
- the period coefficient of performance includes, for example, IPLV (Integrated Part Load Value) defined by the American Refrigeration and Air Conditioning Industry Association. This IPLV has a COP of A at a rated load (load factor of 100%) and a load factor of 75%.
- IPLV 0.01A + 0.42B + 0.45C + 0.12D It is stipulated that it is required. This means that if all the refrigerators that are subject to IPLV are averaged, 45% of the annual operation time is 50% load factor operation and 42% of the annual operation time is 75% load factor operation. A rate 25% operation and a load factor 100% operation mean that they are considered to be 12% and 1% of the annual operating hours, respectively.
- COP at the time of partial load should be emphasized when obtaining the period coefficient of performance, and in particular, COP in an operating state with a load rate of 50% or more and 75% or less with a high cumulative appearance frequency in the year is emphasized. It is considered preferable.
- the discharge-side end face (4a) of the slide valve (4) faces the discharge-side end face (4a) of the slide valve (4) in an operating state with a load factor of 50% to 75%.
- the shape corresponds to the suction side end of the screw rotor (40).
- the compression chamber adjacent to the screw land (42) straddling the screw land (42) facing the discharge side end face (4a) of the slide valve (4). (23) It is possible to reliably prevent communication between each other, reduce discharge resistance, and prevent pressure loss and efficiency reduction of discharged refrigerant.
- the COP in the operating state with a load factor of 50% or more and 75% or less is improved so that the period coefficient of performance can be increased.
- the compression chamber (23) with dots is in communication with the suction chamber (S1). Further, the spiral groove (41) in which the compression chamber (23) is formed meshes with the gate (51) of the gate rotor (50) located on the lower side of the figure.
- the gate (51) relatively moves toward the terminal end of the spiral groove (41), and the volume of the compression chamber (23) increases accordingly. As a result, the low-pressure gas refrigerant in the suction chamber (S1) is sucked into the compression chamber (23) through the suction port (24).
- the compression chamber (23) to which dots are attached is completely closed. That is, the spiral groove (41) in which the compression chamber (23) is formed meshes with the gate (51) of the gate rotor (50) located on the upper side of the drawing, and the suction chamber (51) is formed by the gate (51). It is partitioned from S1).
- the gate (51) moves toward the end of the spiral groove (41) as the screw rotor (40) rotates, the volume of the compression chamber (23) gradually decreases. As a result, the gas refrigerant in the compression chamber (23) is compressed.
- variable VI mechanism (3) volume ratio adjustment mechanism
- FIG. 1 shows a state in which the slide valve (4) slides to the right.
- the discharge port (25) opens near the end of the spiral groove (41), and the refrigeration unit is operated at the rated load.
- this state is the state with the latest discharge timing, and the compression ratio is the largest.
- FIG. 2 shows a state in which the slide valve (4) slides to the left.
- the discharge port (25) opens near the middle of the spiral groove (41), and the refrigeration apparatus is operated at a partial load. It is in the low VI operation state corresponding to.
- the discharge timing is earlier than in the high VI operation state (see FIG. 1), and the compression ratio is smaller than in the high VI operation state.
- the second sub-discharge port (28c) and the third sub-discharge port (28d) are connected to the slide valve (4
- the main discharge port (28a) and the first sub discharge port (28b) are opened from the slide valve (4).
- the refrigerant compressed in the compression chamber (23) flows out to the discharge chamber (S2) through the main discharge port (28a) and the first sub discharge port (28b).
- the third sub discharge port (28d) is closed by the slide valve (4), and the main discharge port ( 28a), the first sub discharge port (28b) and the second sub discharge port (28c) are opened from the slide valve (4).
- the refrigerant compressed in the compression chamber (23) flows out into the discharge chamber (S2) through the main discharge port (28a), the first sub discharge port (28b), and the second sub discharge port (28c). .
- the main discharge port (28a), the first sub discharge port (28b), and the second sub discharge port ( 28c) and the third auxiliary discharge port (28d) are all open from the slide valve (4).
- the refrigerant compressed in the compression chamber (23) passes through the main discharge port (28a), the first sub discharge port (28b), the second sub discharge port (28c), and the third sub discharge port (28d).
- the discharge chamber (S2) To the discharge chamber (S2).
- the refrigerant is discharged not only from the main discharge port (28a) but also from the corresponding sub discharge ports (28b, 28c, 28d) in all the operation states of the plurality of partial loads. The Therefore, the discharge resistance is reduced and the pressure loss is reduced.
- the screw land (42) opposed to the discharge side end face (4a) of the slide valve (4) in the movable range of the slide valve (4) becomes wider from the suction side to the discharge side and has a sharp inclination angle. It has become. That is, the screw land (42) is wider at the portion facing the discharge valve end face (4a) of the slide valve (4) at the time of partial load and has a steeper slope than the portion at the rated load. . Therefore, if the discharge-side end surface (4a) of the slide valve (4) is formed so as to correspond to the inclination of the suction-side end of the screw land (42) facing at the rated load (see the phantom line in FIG. 6A). In addition, when the inclination becomes steep and the partial load operation state is reached, the adjacent compression chambers (23) may communicate with each other as indicated by the phantom line in FIG. If adjacent compression chambers (23) communicate with each other, the desired compression ratio cannot be obtained.
- the discharge-side end face (4a) of the slide valve (4) is opposed to an operation state with a load factor of 50% or more and 75% or less with a high cumulative appearance frequency during a partial load.
- the screw land (42) is inclined according to the inclination of the suction side end (inclination of the line segment P'Q ').
- the discharge-side end face (4a) of the slide valve (4) does not straddle the opposing screw land (42) at the slide position in the operating state with a load factor of 50% to 75%.
- the discharge side end face (4a) of the slide valve (4) has a discharge side end face (4a) at the slide position in an operating state at a load factor (predetermined load factor of 100% or less) larger than the predetermined load factor. Does not straddle the opposing screw land (42).
- the adjacent spiral grooves (41) compression chambers (23)) between the partial load (load factor of 50% or more and 75% or less) and the rated load (load factor of 100%). Does not communicate.
- the shape of the discharge side end face (4a) of the slide valve (4) is made to correspond to the inclination of the screw land (42) facing at the time of partial load, so that both at the time of partial load and at the rated load, Since the discharge-side end face (4a) of the slide valve (4) does not straddle the opposing screw land (42), communication between adjacent compression chambers (23, 23) across the screw land (42) is prevented. be able to. Therefore, it is possible to prevent the pressure loss and efficiency reduction of the discharged fluid at the time of partial load and rated load.
- the discharge side end face (4a) of the slide valve (4) is opposed to the suction side end of the screw land (42) facing the slide position in the operating state with a load factor of 50% to 75%. It is formed so as to extend in a direction corresponding to.
- Embodiment 2 of the Invention changes the shape of the discharge side end surface (4a) of a slide valve (4) in the screw compressor (1) according to Embodiment 1.
- the shape of the discharge side end face (4a) of the slide valve (4) extends in a direction corresponding to the narrowest narrow part (42a) of the screw land (42). It is formed as follows. More specifically, the discharge-side end face (4a) of the slide valve (4) is inclined at the narrow part (42a) of the screw land (42) (this inclination is the corner of the discharge-side end face (4a) in FIG. 8). Are points corresponding to a line segment R ′S ′ connecting the points R ′ and S ′ projected in the axial direction on the suction side end of the narrow portion (42a) of the screw land (42). ).
- the narrow part (42a) of the screw land (42) whose width and angle are not uniform is narrower than the other parts and has a gentle inclination angle. Therefore, if the discharge side end face (4a) of the slide valve (4) extends in a direction corresponding to the narrow part (42a) of the screw land (42), the discharge side end face (4a) of the slide valve (4) Even if it faces any part of the screw land (42), it does not straddle the screw land (42).
- the pressure loss of the discharged fluid can be prevented in all the movable ranges of the slide valve (4), and the compression chambers (23) adjacent to each other with the screw land (42) interposed therebetween can be prevented.
- the communication can be suppressed and the efficiency can be prevented from decreasing. That is, it is possible to prevent the pressure loss and efficiency reduction of the discharged fluid at the partial load and the rated load, which are the objects of the present invention.
- Embodiments 1 and 2 >> About the said Embodiment 1 and 2, it is good also as the following structures.
- the discharge-side end surface (4a) of the slide valve (4) extends in a direction corresponding to the extending direction of the opposing screw land (42) in the operation state with a load factor of 50% to 75%.
- the discharge-side end face (4a) may be formed to extend in a direction corresponding to the extending direction of the opposing screw land (42) in an operation state with a load factor other than this.
- the discharge-side end face (4a) of the slide valve (4) may be formed to extend in a direction corresponding to the extending direction of the opposing screw land (42) in an operating state with a load factor of 25%.
- the weight in the period performance coefficient is considered that the load factor 25% is larger (the cumulative appearance frequency is higher in the year) between the load factor 25% and the load factor 100%. Therefore, even in the above-described case, the discharge-side end face (4a) of the slide valve (4) is formed to extend in a direction corresponding to the extending direction of the screw land (42) facing at the rated load. Thus, the period performance coefficient can be improved and the period power consumption can be reduced.
- the discharge side end surface (4a) of the slide valve (4) is formed to extend in a direction corresponding to the suction side end of the predetermined portion of the screw land (42). Further, it may be formed to extend in a direction corresponding to the discharge side end, or may be formed to extend in a direction between a direction corresponding to the discharge side end and a direction corresponding to the suction side end.
- the discharge side end surface (4a) of the slide valve (4) is formed on a slope extending in a direction corresponding to the suction side end of the predetermined portion of the screw land (42).
- the curved shape corresponding to the suction side end of the predetermined portion of the screw land (42) may be formed.
- Embodiment 3 of the Invention The third embodiment considers the following points in the screw compressor (1) according to the first embodiment.
- a single screw compressor (see FIG. 18) provided with a compression mechanism for compressing a refrigerant by a rotational movement of a screw rotor.
- This single screw compressor (hereinafter referred to as a screw compressor) (100) is formed through the opening of the cylinder wall (131) into the screw rotor (140) rotating in the cylinder wall (131) of the casing (130).
- the compression chamber (123) is formed by meshing the gate rotor (150).
- the screw rotor (140) has one end (the left end in the figure) on the suction side and the other end (the right end in the figure) on the discharge side.
- variable VI mechanism volume ratio adjusting mechanism
- VI volume ratio between the suction volume and the discharge volume
- a slide valve (104) that moves in a moving manner (for example, see Japanese Patent Application Laid-Open No. 2004-137934).
- the slide valve (104) is slid in the axial direction of the screw rotor (140) to change the discharge volume by changing the position at which high-pressure gas starts to be discharged (compression is completed). The ratio is changed.
- the screw compressor (100) is configured to change the rotational speed of an electric motor (not shown) by performing inverter control, thereby controlling the operating capacity.
- the operating capacity (refrigerant discharge amount per unit time) is controlled according to the load on the usage side of the refrigerant circuit.
- the slide valve (104) of the variable VI mechanism (103) is controlled so as to have a volume ratio (compression ratio) at which optimum compression efficiency is obtained with respect to the operating capacity controlled according to the load.
- the position of the slide valve (104) in the axial direction of the screw rotor (140) changes according to the operating capacity that changes depending on whether the operating state is the rated load (100% load) state or the partial load state. To do.
- the position of the slide valve (104) changes so that the opening on the discharge side is larger in the partial load operation state than in the rated load operation state.
- the third embodiment has been devised in view of such problems, and its purpose is to prevent the occurrence of problems due to communication between compression chambers having different pressures in an operating state at a rated load. It is to prevent the performance of the screw compressor from deteriorating by obtaining a sufficiently large discharge opening area in the partial load operation state.
- a first example of Embodiment 3 includes a screw rotor (40) in which a spiral groove (41) is formed on the outer peripheral surface, one end being a fluid suction side and the other end being a discharge side, and the screw rotor (40).
- a casing (30) having a cylinder wall (31) that is rotatably accommodated, a drive mechanism (26) that drives the screw rotor (40) in a variable rotation speed according to a load, and the cylinder wall (31)
- a volume ratio adjusting mechanism (3) having a slide valve (4) that is movably mounted in an axial direction in a slide groove (33) formed along the axial direction and adjusts a discharge start position, and the screw rotor (40) Single screw compression provided with a discharge port (28) formed in the casing (30) so as to communicate with a compression chamber (23) formed in the spiral groove (41) of the screw rotor (40) on the discharge side Machine is assumed.
- the discharge port (28) of the single screw compressor includes a main discharge port (28a) and a sub discharge port (28b, 28c, 28d), and the main discharge port (28a) is in an operating state at a rated load.
- a port whose opening shape is determined in accordance with the position of the slide valve (4). The port is opened without being blocked by the slide valve (4) in either the rated load operation state or the partial load operation state.
- the discharge port and the sub discharge ports (28b, 28c, 28d) are ports whose opening shape is determined according to the position of the slide valve (4) in the partial load operation state, and operated at the rated load. It is a port that is closed by the slide valve (4) in a state and is opened from the slide valve (4) in a partial load operation state and discharges fluid.
- the sub discharge ports (28b, 28c, 28d) are closed by the slide valve (4), so that the main discharge is performed.
- a fluid such as a refrigerant is discharged only from the port (28a). Since the main discharge port (28a) is formed in accordance with the position of the slide valve (4) in the rated load operating state, the adjacent compression chambers (23) do not communicate with each other.
- the slide valve (4) moves to a position corresponding to the operation capacity, and the sub discharge ports (28b, 28c, 28d) are opened from the slide valve (4). Therefore, fluid is discharged from both the main discharge port (28a) and the sub discharge ports (28b, 28c, 28d), and discharge resistance is reduced.
- the second example of the third embodiment is characterized in that, in the first example of the third embodiment, a plurality of sub discharge ports (28b, 28c, 28d) corresponding to a plurality of partial load operation states are provided. .
- a plurality of sub discharge ports (28b, 28c, 28d) are provided, a plurality of sub discharge ports (28b, 28c, 28d) are provided according to a plurality of partial load operation states. ) Will be used for control.
- a third example of the third embodiment is the second port in the second example of the third embodiment, in which the auxiliary discharge ports (28b, 28c) are two ports corresponding to the operating state of 75% load and 50% load,
- the sub discharge port (28b) corresponding to the 75% load operation state is closed by the slide valve (4) in the rated load operation state, and opened in the 75% load and 50% load operation state.
- the secondary discharge port (28c) that is formed and corresponds to the 50% load operating state is closed by the slide valve (4) at the rated load and 75% load operating state, and opened at the 50% load operating state. It is characterized in that it is formed at a position to be formed.
- the fourth example of the third embodiment corresponds to the operation state of the 75% load, the 50% load, and the 25% load in the sub discharge port (28b, 28c, 28d) in the second example of the third embodiment.
- the sub discharge port (28c) which is formed at a position opened in the load operating state and corresponds to the 50% load operating state, is blocked by the slide valve (4) in the rated load and 75% load operating states.
- the sub discharge port (28d) which is formed at a position opened in the operation state of 50% load and 25% load, corresponds to the operation state of 25% load, and 75% of the rated load by the slide valve (4).
- the infarction is characterized by being formed in a position which is opened in the operating state of the 25% load.
- the period coefficient of performance is known as the coefficient of performance (COP) of the refrigeration apparatus.
- This period coefficient of performance is a concept of obtaining the annual COP by weighting the COP at each load, since there are a period with a large load, a period with a small load, an intermediate period, etc. throughout the year.
- the sub discharge ports (28b, 28c) used at the partial load are formed on the basis of two operation states of 75% load and 50% load, and the third embodiment is described.
- the sub discharge ports (28b, 28c, 28d) used at the partial load are formed on the basis of three operating states of 75% load, 50% load and 25% load.
- a fifth example of the third embodiment is the same as any one of the second to fourth examples of the third embodiment, in which the discharge side end face (4a) of the slide valve (4) is slid in the partial load operation state.
- the sub-discharge ports (28b, 28c, 28d) are formed so as to be inclined in the direction corresponding to the inclination of the spiral groove (41) on the discharge side of the valve (4), and the discharge of the slide valve (4) It is characterized by being formed to be inclined along the inclination of the side end face (4a).
- the inclination of the spiral groove (41) corresponding to the position of the slide valve (4) at the partial load is the spiral groove corresponding to the position of the slide valve (4) at the rated load ( 41), the discharge side end face (4a) of the slide valve (4) has a gentle slope, and the side faces of the secondary discharge ports (28b, 28c, 28d) are slanted. Will also be moderate. If the inclination is steep, adjacent compression chambers (23) may communicate with each other. However, in the fifth example of the third embodiment, the inclination becomes gentle, so that the adjacent compression chambers (23 ) Can be reliably prevented from communicating with each other.
- the sixth example of the third embodiment corresponds to the fifth example of the third embodiment in which the sub discharge ports (28b, 28c, 28d) correspond to the inclination of the discharge side end surface (4a) of the slide valve (4).
- the land width of the inclined screw (referred to as the width of a mountain between adjacent spiral grooves (41)) is narrower than the land width.
- the sub discharge port (28b, 28c, 28d) since the width of the sub discharge port (28b, 28c, 28d) is narrower than the land width of the screw, the sub discharge port (28b, 28c, 28d) does not straddle the land. Adjacent compression chambers (23) (spiral grooves (41)) do not communicate with each other.
- the plurality of sub discharge ports (28b, 28c, 28d) are formed so that the width becomes narrower from the discharge side to the suction side. It is characterized by having.
- the width of the land corresponding to the discharge side of the slide valve (4) is narrowed from the discharge side to the suction side (see FIG. 16), the width of each sub discharge port (28b, 28c, 28d) is set. Therefore, also in the seventh example of the third embodiment, the sub discharge ports (28b, 28c, 28d) do not straddle the lands, and the adjacent compression chambers (23) (spiral grooves (41)) do not communicate with each other. .
- the screw compressor when the screw compressor is in the rated load operation state, the fluid is discharged only from the main discharge port (28a), and at this time, the adjacent compression chamber (23) Since they do not communicate with each other, it is possible to prevent the occurrence of problems due to the compression chambers (23) having different pressures communicating with each other.
- the screw compressor when the screw compressor is in a partial load operation state, fluid is discharged from both the main discharge port (28a) and the sub discharge ports (28b, 28c, 28d), so that a sufficiently large discharge opening area is provided. Obtainable. Therefore, since the pressure loss due to the discharge resistance does not increase, it is possible to prevent the performance of the screw compressor from being deteriorated.
- the sub discharge ports (28b, 28c) used at the partial load are formed on the basis of two operation states of 75% load and 50% load, and the third embodiment is described.
- the sub discharge ports (28b, 28c, 28d) used at the partial load are formed based on the three operating states of 75% load, 50% load and 25% load.
- the area of the discharge port (28) can be increased when these partial loads are operating. Therefore, since the discharge resistance in the partial load operation state can be reduced, the pressure loss is also reduced, and consequently the period coefficient of performance can be increased.
- the inclination of the discharge side end face (4a) of the slide valve (4) and the inclination of the side faces of the auxiliary discharge ports (28b, 28c, 28d) are made gentle. Therefore, it is possible to reliably prevent the adjacent compression chambers (23) from communicating with each other via the sub discharge ports (28b, 28c, 28d) during operation at the rated load. Therefore, it is possible to reliably prevent a problem that the desired compression ratio cannot be obtained.
- the width of the sub discharge ports (28b, 28c, 28d) is made narrower than the land width of the screw, and the adjacent discharge ports (28b, 28c, 28d) are compressed. Since the chambers (23) (spiral grooves (41)) do not communicate with each other, the adjacent compression chambers (23) do not communicate with each other during operation at the rated load, and the fifth example of the third embodiment. The effect can be made more certain.
- the width of the land corresponding to the discharge side of the slide valve (4) is reduced from the discharge side toward the suction side.
- 28b, 28c, and 28d) are narrowed from the discharge side toward the suction side, so that the compression chambers (23) adjacent to each other do not communicate with each other during operation at the rated load.
- the effect of the sixth example can be further ensured.
- the single screw compressor (1) of the third embodiment (hereinafter simply referred to as a screw compressor) is provided in a refrigerant circuit that performs a refrigeration cycle and compresses the refrigerant.
- the screw compressor (1) includes a compression mechanism (20) and a variable VI mechanism (volume ratio adjustment mechanism) that adjusts the ratio (volume ratio: VI) between the suction volume and the discharge volume in the compression mechanism (20). And 3).
- the compression mechanism (20) includes a cylinder wall (31) formed in a casing (30) of the screw compressor (1), and a cylinder wall (31).
- One screw rotor (40) rotatably arranged on the two and two gate rotors (50) meshing with the screw rotor (40).
- the communication part (32) includes a slide groove (33) extending along the axial direction of the cylinder wall (31), and a slide valve (4) described later can be moved in the axial direction in the slide groove (33). It is attached to.
- the slide groove (33) and the slide valve (4) constitute the variable VI mechanism (3).
- the discharge port (25) includes a valve side discharge port (27) formed in the slide valve (4) and a cylinder side discharge port (28) formed in the cylinder wall (31). It is.
- the drive shaft (21) extending from the electric motor (not shown) is inserted through the screw rotor (40).
- the screw rotor (40) and the drive shaft (21) are connected by a key (22), and the screw rotor (40) is driven by a drive mechanism (26) including the electric motor and the drive shaft (21). ing.
- the drive shaft (21) is arranged coaxially with the screw rotor (40).
- the tip of the drive shaft (21) is freely rotatable by a bearing holder (60) located on the discharge side of the compression mechanism (20) (the right side when the axial direction of the drive shaft (21) in FIG. 11 is the left-right direction). It is supported by.
- the bearing holder (60) supports the drive shaft (21) via a ball bearing (61).
- the screw rotor (40) is rotatably fitted to the cylinder wall (31), and its outer peripheral surface is in sliding contact with the inner peripheral surface of the cylinder wall (31) via an oil film.
- the motor is configured so that the rotation speed can be adjusted by inverter control.
- the screw compressor (1) can change the operating capacity by adjusting the rotational speed of the electric motor.
- the operating capacity (refrigerant discharge amount per unit time) of the screw compressor (1) is controlled according to the load on the usage side of the refrigerant circuit.
- the slide valve (4) of the variable VI mechanism (3) is controlled so as to obtain a volume ratio (compression ratio) at which an optimum compression efficiency is obtained with respect to the operation capacity controlled according to the load.
- the slide valve (4) moves in the axial direction of the screw rotor (40) according to the operating capacity that changes depending on whether the operating state is a rated load (100% load) state or a partial load state. The position changes.
- the slide valve (4) has a small load when compared with the operation state of the rated load (state of FIG. 11) and the operation state of the partial load (state of FIG. 12). In the operating state, the position changes to the left side (suction side) in FIG. 11 so that the area of the cylinder side discharge port (28) becomes larger.
- the screw rotor (40) shown in FIGS. 14 and 15 is a metal member formed in a substantially cylindrical shape. On the outer peripheral surface of the screw rotor (40), a spiral groove extending in a spiral shape from one end of the screw rotor (40) (end on the suction side of the fluid (refrigerant)) to the other end (end on the discharge side) 41) are formed (six in the third embodiment).
- Each screw groove (41) of the screw rotor (40) has a left end (end portion on the suction side) in FIG. 15 as a start end and a right end in the drawing ends (end on the fluid discharge side). Further, the screw rotor (40) has a tapered left end in the figure. In the screw rotor (40) shown in FIG. 15, the start end of the spiral groove (41) is opened at the left end surface formed in a tapered surface, while the end of the spiral groove (41) is not opened at the right end surface. .
- Each gate rotor (50) is a resin member.
- Each gate rotor (50) is provided with a plurality of (11 in the third embodiment) gates (51) formed in a rectangular plate shape in a radial pattern.
- Each gate rotor (50) is arranged outside the cylinder wall (31) so as to be axially symmetric with respect to the rotational axis of the screw rotor (40). That is, in the screw compressor (1) of the third embodiment, the two gate rotors (50) are arranged at equiangular intervals (180 ° intervals in the third embodiment) around the rotation center axis of the screw rotor (40). Has been.
- each gate rotor (50) is orthogonal to the axis of the screw rotor (40).
- Each gate rotor (50) is arranged so that the gate (51) penetrates a part (not shown) of the cylinder wall (31) and meshes with the spiral groove (41) of the screw rotor (40).
- the gate rotor (50) is attached to a metal rotor support member (55) (see FIG. 14).
- the rotor support member (55) includes a base portion (56), an arm portion (57), and a shaft portion (58).
- the base (56) is formed in a slightly thick disk shape.
- the same number of arms (57) as the gates (51) of the gate rotor (50) are provided and extend radially outward from the outer peripheral surface of the base (56).
- the shaft portion (58) is formed in a rod shape and is erected on the base portion (56).
- the central axis of the shaft portion (58) coincides with the central axis of the base portion (56).
- the gate rotor (50) is attached to a surface of the base portion (56) and the arm portion (57) opposite to the shaft portion (58). Each arm part (57) is in contact with the back surface of the gate (51).
- the rotor support member (55) to which the gate rotor (50) is attached is accommodated in a gate rotor chamber (90) defined in the casing (30) adjacent to the cylinder wall (31) (see FIG. 13).
- the rotor support member (55) disposed on the right side of the screw rotor (40) in FIG. 13 is installed in such a posture that the gate rotor (50) is on the lower end side.
- the rotor support member (55) disposed on the left side of the screw rotor (40) in the figure is installed in such a posture that the gate rotor (50) is on the upper end side.
- each rotor support member (55) is rotatably supported by a bearing housing (91) in the gate rotor chamber (90) via ball bearings (92, 93).
- Each gate rotor chamber (90) communicates with the suction chamber (S1).
- the compression chamber (23) includes a first compression chamber (23a) located above the horizontal center line in FIG. 13 and a second compression chamber (23b) located below the center line. (See FIG. 15).
- the spiral groove (41) of the screw rotor (40) is opened to the suction chamber (S1) at the suction side end, and this open part is the suction port (24) of the compression mechanism (20).
- variable VI mechanism (3) includes a slide groove (33) of the communicating portion (32) of the cylinder wall (31) and a slide accommodated so as to be slidably fitted in the slide groove (33).
- valve (4) includes a hydraulic cylinder (5) fixed to the discharge side of the bearing holder (60) and positioned in the discharge chamber (S2) (see FIGS. 11 and 12).
- the slide valve (4) is provided in both the first and second compression chambers (23a, 23b). As described above, the slide valve (4) and the cylinder wall (31) are provided on the valve side discharge port (27) and the cylinder side discharge port (28) constituting the discharge port (25) of the compression mechanism (20). ) Are formed, and the compression chamber (23) and the discharge chamber (S2) communicate with each other through the discharge port (25). Further, the inner surface of the slide valve (4) constitutes a part of the inner peripheral surface of the cylinder wall (31) and is slidable in the axial direction of the cylinder wall (31). One end of the slide valve (4) faces the discharge chamber (S2), and the other end faces the suction chamber (S1).
- the hydraulic cylinder (5) includes a cylinder tube (6), a piston (7) loaded in the cylinder tube (6), and an arm (9) connected to the piston rod (8) of the piston (7). ), A connecting rod (10a) for connecting the arm (9) and the slide valve (4), and the arm (9) in the right direction in FIG. 11 (direction in which the arm (9) is separated from the casing (30)). And a spring (10b) for biasing. Further, on both sides of the piston (7) in the cylinder tube (6), a first cylinder chamber (11) (left side of the piston (7) in FIG. 11) and a second cylinder chamber (12) (piston (in FIG. The right side of 7) is formed.
- the hydraulic cylinder (5) is configured to adjust the position of the slide valve (4) by adjusting the pressure in the left and right cylinder chambers (11, 12) of the piston (7).
- FIG. 11 shows a state in which the slide valve (4) is slid to the right. In this state, the discharge port (25) is opened substantially near the end of the spiral groove (41).
- This state is a state corresponding to the rated load operation state (high VI operation state). In the screw compressor (1), this state is the state with the latest discharge timing, and the compression ratio is the largest.
- FIG. 12 shows a state in which the slide valve (4) is slid to the left.
- the discharge port (25) is opened near the middle of the spiral groove (41).
- This state is a state corresponding to the partial load operation state (low VI operation state).
- the discharge timing is earlier than in the high VI operation state (see FIG. 11), and the compression ratio is smaller than in the high VI operation state.
- the optimum VI value is selected so that the screw compressor (1) has the highest efficiency in accordance with the operating state of the refrigerant circuit, and the position of the slide valve (4) is adjusted. It has become.
- the rotational speed of the electric motor is controlled by inverter control according to the operating state (use side load) by a control mechanism (not shown), and capacity control is performed.
- the slide valve (4) is provided with a detent (not shown) so that the inner peripheral surface is in sliding contact with the outer peripheral surface of the valve guide (15) regardless of the position during operation.
- the inner peripheral surface of the slide valve (4) is held in a state of being located on the same cylinder as the inner peripheral surface of the cylinder wall (31) of the casing (30). Therefore, in the third embodiment, the slide valve (4) does not rotate, and the inner peripheral surface of the slide valve (4) and the outer peripheral surface of the screw rotor (40) do not interfere with each other.
- the cylinder side discharge port (28) constituting the discharge port (25) has a main discharge port (28a) and sub discharge ports (28b, 28c) as shown in FIGS. 16 (A) to 16 (D). 28d).
- the main discharge port (28a) is a port whose opening shape is determined in accordance with the position of the slide valve (4) in the operating state of the rated load, and is shown in FIGS. 16 (A) to 16 (D). As described above, the port is opened without being closed by the slide valve (4) in both the rated load operation state and the partial load operation state, and the fluid is discharged.
- the auxiliary discharge ports are ports whose opening shape is determined according to the position of the slide valve (4) in the partial load operation state. While being closed by 4), it is a port that is opened from the slide valve (4) in a partially loaded state and discharges fluid.
- a plurality of ports are provided as the auxiliary discharge ports (28b, 28c, 28d) so as to correspond to a plurality of partial load operation states.
- the sub-discharge ports (28b, 28c, 28d) are composed of three ports corresponding to the operating states of 75% load, 50% load and 25% load.
- the main discharge port (28a) and the sub discharge ports (28b, 28c, 28d) are formed at positions separated from each other.
- Each sub discharge port (28b, 28c, 28d) is formed on the suction side with respect to the main discharge port (28a).
- FIGS. 16A to 16D are views showing the positional relationship between the slide valve (4) and the cylinder-side discharge port (28) in a state where the screw rotor (40) is deployed.
- the sub discharge port (28b) (referred to as the first sub discharge port (28b)) corresponding to the 75% load operation state is blocked by the slide valve (4) in the rated load operation state as shown in FIG.
- FIGS. 16 (B) to 16 (D) it is formed at a position where it is opened in the operating state of 75% load, 50% load and 25% load.
- the sub discharge port (28c) (referred to as the second sub discharge port (28c)) corresponding to the operating state of 50% load is shown in FIGS.
- FIGS. 16 (A) and 16 (B) by the slide valve (4). While closed at the rated load and 75% load operating conditions, as shown in FIGS. 16 (C) and 16 (D), it is formed at a position where it is opened at the 50% load and 25% load operating conditions. . Also, the sub discharge port (28d) (referred to as the third sub discharge port (28d)) corresponding to the operating state of 25% load is shown in FIGS. 16 (A) to 16 (C) by the slide valve (4). As shown in FIG. 16 (D), it is formed in a position where it is closed in the operating state of the rated load, 75% load and 50% load.
- the discharge side end face (4a) of the slide valve (4) is formed to be inclined in a direction corresponding to the inclination of the spiral groove (41) on the discharge side of the slide valve (4) in the partial load operation state. ing. Specifically, the discharge-side end face (4a) of the slide valve (4) is spiral in an operating state between 75% load and 50% load, as shown in FIGS. 16 (B) and 16 (C). Inclination of the groove (this inclination is determined in the direction perpendicular to the axis of the two points P and Q of the corner of the discharge side end face (4a) of the slide valve (4) in FIGS. 16 (B) and 16 (C).
- Each of the sub-discharge ports (28b, 28c, 28d) corresponds to the portion of the spiral groove (41) (line segment P'Q ') that serves as a reference for the inclination of the discharge-side end face (4a) of the slide valve (4)
- the width of the land (referred to as the land width of the screw).
- the plurality of sub discharge ports (28b, 28c, 28d) are formed so that the width becomes narrower from the discharge side toward the suction side.
- the land width corresponding to the discharge side of the slide valve (4) is changed from the discharge side to the suction side.
- the width of each sub discharge port (28b, 28c, 28d) is set in accordance with the narrowing toward the surface.
- a period performance coefficient is known as a coefficient of performance (COP) of a refrigeration apparatus.
- This period coefficient of performance is a concept of obtaining the annual COP by weighting the COP at each load, since there are a period with a large load, a period with a small load, an intermediate period, etc. throughout the year.
- the weighting numbers are considered to be different between the United States and Japan, there is no change in the importance of COP at partial load when calculating the period coefficient of performance. To that end, increase the operating efficiency at partial load. Is desirable. Therefore, in the third embodiment, when the slide valve (4) is set to the position of the partial load operation state, the discharge resistance is reduced by increasing the area of the cylinder side discharge port (28), It is possible to prevent a decrease in efficiency due to pressure loss in the operation state of a partial load, thereby increasing the period coefficient of performance.
- the compression chamber (23) with dots is in communication with the suction chamber (S1). Further, the spiral groove (41) in which the compression chamber (23) is formed meshes with the gate (51) of the gate rotor (50) located on the lower side of the figure.
- the gate (51) relatively moves toward the terminal end of the spiral groove (41), and the volume of the compression chamber (23) increases accordingly. As a result, the low-pressure gas refrigerant in the suction chamber (S1) is sucked into the compression chamber (23) through the suction port (24).
- the compression chamber (23) to which dots are attached is completely closed. That is, the spiral groove (41) in which the compression chamber (23) is formed meshes with the gate (51) of the gate rotor (50) located on the upper side of the drawing, and the suction chamber (51) is formed by the gate (51). It is partitioned from S1).
- the gate (51) moves toward the end of the spiral groove (41) as the screw rotor (40) rotates, the volume of the compression chamber (23) gradually decreases. As a result, the gas refrigerant in the compression chamber (23) is compressed.
- variable VI mechanism (3) volume ratio adjustment mechanism
- FIG. 11 shows a state in which the slide valve (4) is slid to the right.
- the discharge port (25) opens near the end of the spiral groove (41), and the refrigeration apparatus is operated at the rated load.
- this state is the state with the latest discharge timing, and the compression ratio is the largest.
- FIG. 12 shows a state in which the slide valve (4) slides to the left.
- the discharge port (25) opens near the middle of the spiral groove (41), and the refrigeration apparatus is operated at a partial load. It is in the low VI operation state corresponding to.
- the discharge timing is earlier than in the high VI operation state (see FIG. 11), and the compression ratio is smaller than in the high VI operation state.
- the second sub discharge port (28c) and the third sub discharge port (28d) are connected to the slide valve (4).
- the main discharge port (28a) and the first sub discharge port (28b) are opened from the slide valve (4).
- the refrigerant compressed in the compression chamber (23) flows out to the discharge chamber (S2) through the main discharge port (28a) and the first sub discharge port (28b).
- the third auxiliary discharge port (28d) is closed by the slide valve (4), and the main discharge port (28a ), The first sub discharge port (28b) and the second sub discharge port (28c) are opened from the slide valve (4).
- the refrigerant compressed in the compression chamber (23) flows out into the discharge chamber (S2) through the main discharge port (28a), the first sub discharge port (28b), and the second sub discharge port (28c). .
- the refrigerant is discharged not only from the main discharge port (28a) but also from the corresponding auxiliary discharge ports (28b, 28c, 28d) in all of the operating states of the plurality of partial loads. The Therefore, the discharge resistance is reduced and the pressure loss is reduced. Further, in the operation state at the rated load, the refrigerant is discharged only from the main discharge port (28a).
- the discharge-side end face (4a) of the slide valve (4) is inclined with respect to the inclination (line segment P ′) of the spiral groove (41) on the discharge side of the slide valve (4) in the partial load operation state. (Tilt of Q ′).
- the discharge side end face (4a) of the slide valve (4) is inclined so as to correspond to the inclination of the spiral groove (41) on the discharge side of the slide valve (4) in the rated load operating state (see FIG. 16 (A) (see the imaginary line)) and the slope thereof is steep, so when the partial load operation state is reached, the adjacent compression chambers (23) as indicated by the phantom line in FIG. 16 (D) They may communicate with each other.
- the inclination of the slide valve (4) is set so as to correspond to the inclination of the spiral groove (41) in the partial load state.
- the inclination of the spiral groove (41) becomes steeper than in the partial load state. Therefore, in the third embodiment, in all the operation states, the adjacent spiral groove (41) (compression chamber (23 )) They do not communicate with each other.
- the side surfaces of the respective width discharge ports (28b, 28c, 28d) are inclined, and from the discharge side toward the suction side, that is, from the first sub discharge port (28b) to the third sub discharge port. (28d), the width of each sub discharge port (28b, 28c, 28d) is made narrower than the land width of the screw corresponding to each partial load.
- Embodiment 3- by providing the sub discharge ports (28b, 28c, 28d) in addition to the main discharge port (28a), it is possible to reduce the pressure loss due to the refrigerant discharge resistance at the partial load. Therefore, the operation efficiency at the time of partial load can be improved, and consequently the period coefficient of performance can be improved. Further, since the refrigerant is discharged only from the main discharge port (28a) and the adjacent compression chambers (23) do not communicate with each other in the rated load operating state, there is no problem that the desired compression ratio cannot be obtained.
- the inclination of the spiral groove (41) corresponding to the position of the slide valve (4) at the partial load is greater than the inclination of the spiral groove (41) corresponding to the position of the slide valve (4) at the rated load. Since it is gentle, the inclination of the discharge side end face (4a) of the slide valve (4) becomes gentle, and the inclination of the side faces of the sub discharge ports (28b, 28c, 28d) also becomes gentle. If this inclination is steep, it is conceivable that the adjacent compression chambers (23) communicate with each other. However, in the third embodiment, the inclination becomes gentle, so that the adjacent compression chambers (23) communicate with each other. It can be surely prevented. Therefore, it is possible to reliably prevent a problem that the desired compression ratio cannot be obtained.
- the width of the sub discharge port (28b, 28c, 28d) is made narrower than the land width of the screw, and the slide valve (4) is moved within the movable range of the slide valve (4).
- the width of each sub-discharge port (28b, 28c, 28d) also becomes narrower from the discharge side toward the suction side.
- the sub discharge ports (28b, 28c, 28d) do not straddle the lands, and the adjacent compression chambers (23) (spiral grooves (41)) do not communicate with each other. Therefore, it is possible to more reliably and reliably prevent a problem that the desired compression ratio cannot be obtained.
- Embodiment 3 Other Forms of Embodiment 3 >> About the said Embodiment 3, it is good also as the following structures.
- three sub-discharge ports (28b, 28c, 28d) are provided in addition to the main discharge port (28a), but two corresponding to the operating state of 75% load and 50% load are provided. Only the sub discharge ports (28b, 28c) may be provided. In addition, the number of sub discharge ports may be one or four or more depending on circumstances. In these cases, the value set as the partial load is not limited to 75%, 50%, and 25%, and can be changed as appropriate.
- main discharge port (28a) coincides with the point P on the discharge side end face (4a) when the slide valve (4) is in the position at the rated load, as indicated by a virtual line in FIG. If the width is widened to the suction side to the position, the discharge resistance can be further reduced.
- auxiliary discharge ports (28b, 28c, 28d) are provided only on the lower side of FIGS. 16 (A) to 16 (D) with respect to the slide valve. May be provided on both the lower side and the upper side.
- the present invention is useful for a single screw compressor provided with a variable VI mechanism (volume ratio adjusting mechanism) that adjusts the ratio between the suction volume and the discharge volume.
- a variable VI mechanism volume ratio adjusting mechanism
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Abstract
Description
IPLV=0.01A+0.42B+0.45C+0.12D
で求められると定められている。このことは、IPLVの対象になっている全ての冷凍機を平均すれば、年間の運転時間の45%が負荷率50%運転、年間の運転時間の42%が負荷率75%運転で、負荷率25%運転と負荷率100%運転は、それぞれ年間の運転時間の12%と1%であると考えられていることを意味している。
本実施形態1のシングルスクリュー圧縮機(1)(以下、単にスクリュー圧縮機と言う。)は、冷凍サイクルを行う冷媒回路に設けられて冷媒を圧縮するためのものである。
上記圧縮機構(20)は、図1~図3に示すように、上記スクリュー圧縮機(1)のケーシング(30)内に形成されたシリンダ壁(31)と、このシリンダ壁(31)の中に回転可能に配置された1つのスクリューロータ(40)と、このスクリューロータ(40)に噛み合う2つのゲートロータ(50)とを備えている。
上記可変VI機構(3)は、上述したシリンダ壁(31)の連通部(32)のスライド溝(33)と、このスライド溝(33)に摺動自在に嵌合するように収容されたスライドバルブ(4)に加え、上記ベアリングホルダ(60)の吐出側に固定されて上記吐出室(S2)に位置する油圧シリンダ(5)を含んでいる(図1,2を参照)。
IPLV=0.01A+0.42B+0.45C+0.12D
で求められると定められている。このことは、IPLVの対象になっている全ての冷凍機を平均すれば、年間の運転時間の45%が負荷率50%運転、年間の運転時間の42%が負荷率75%運転で、負荷率25%運転と負荷率100%運転は、それぞれ年間の運転時間の12%と1%であると考えられていることを意味している。
上記スクリュー圧縮機(1)における圧縮機構(20)及び可変VI機構(3)の運転動作について説明する。
上記電動機を起動すると、駆動軸(21)が回転するのに伴ってスクリューロータ(40)が回転する。このスクリューロータ(40)の回転に伴ってゲートロータ(50)も回転し、上記圧縮機構(20)が吸入行程、圧縮行程および吐出行程を繰り返す。ここでは、図7においてドットを付した圧縮室(23)に着目して説明する。
次に、可変VI機構(3)の動作について説明する。
本実施形態1によれば、スライドバルブ(4)の吐出側端面(4a)形状を、部分負荷時に対向するスクリューランド(42)の傾斜に対応させることにより、部分負荷時にも定格負荷時にも、スライドバルブ(4)の吐出側端面(4a)が対向するスクリューランド(42)に跨らなくなるため、該スクリューランド(42)を挟んで隣り合う圧縮室(23,23)同士の連通を防止することができる。従って、部分負荷時及び定格負荷時の吐出流体の圧力損失及び効率低下を防止することができる。
実施形態2は、実施形態1に係るスクリュー圧縮機(1)において、スライドバルブ(4)の吐出側端面(4a)の形状を変更したものである。
上記実施形態1及び2については、以下のような構成としてもよい。
実施形態3は、実施形態1に係るスクリュー圧縮機(1)において、以下の点について考慮したものである。
IPLV=0.01A+0.42B+0.45C+0.12D
で求められると定められている。このことは、IPLVの対象になっている全ての冷凍機を平均すれば、年間の運転時間の45%が50%負荷、年間の運転時間の42%が75%負荷で、25%負荷時と100%負荷時は、それぞれ年間の運転時間の12%と1%であると考えられていることを意味している。
上記圧縮機構(20)は、図11~図13に示すように、上記スクリュー圧縮機(1)のケーシング(30)内に形成されたシリンダ壁(31)と、このシリンダ壁(31)の中に回転可能に配置された1つのスクリューロータ(40)と、このスクリューロータ(40)に噛み合う2つのゲートロータ(50)とを備えている。
上記可変VI機構(3)は、上述したシリンダ壁(31)の連通部(32)のスライド溝(33)と、このスライド溝(33)に摺動自在に嵌合するように収容されたスライドバルブ(4)に加え、上記ベアリングホルダ(60)の吐出側に固定されて上記吐出室(S2)に位置する油圧シリンダ(5)を含んでいる(図11,12を参照)。
IPLV=0.01A+0.42B+0.45C+0.12D
で求められると定められている。このことは、IPLVの対象になっている全ての冷凍機を平均すれば、年間の運転時間の45%が50%負荷、年間の運転時間の42%が75%負荷で、25%負荷時と100%負荷時は、それぞれ年間の運転時間の12%と1%であると考えられていることを意味している。
上記スクリュー圧縮機(1)における圧縮機構(20)及び可変VI機構(3)の運転動作について説明する。
上記電動機を起動すると、駆動軸(21)が回転するのに伴ってスクリューロータ(40)が回転する。このスクリューロータ(40)の回転に伴ってゲートロータ(50)も回転し、上記圧縮機構(20)が吸入行程、圧縮行程および吐出行程を繰り返す。ここでは、図17においてドットを付した圧縮室(23)に着目して説明する。
次に、可変VI機構(3)の動作について説明する。
本実施形態3によれば、主吐出ポート(28a)に加えて副吐出ポート(28b,28c,28d)を設けることにより、部分負荷時の冷媒の吐出抵抗に起因する圧力損失を低減できる。そのため、部分負荷時の運転効率を高めることができ、ひいては期間成績係数を向上させることが可能となる。また、定格負荷の運転状態では主吐出ポート(28a)だけから冷媒が吐出され、隣り合う圧縮室(23)同士が連通しないので、所期の圧縮比が得られなくなる不具合は生じない。
上記実施形態3については、以下のような構成としてもよい。
3 可変VI機構
4 スライドバルブ
4a 吐出側端面
23 圧縮室
26 駆動機構
30 ケーシング
31 シリンダ壁
33 スライド溝
40 スクリューロータ
41 螺旋溝
42 スクリューランド(ランド)
42a 幅狭部
Claims (5)
- 外周面に一端が流体の吸入側となり他端が吐出側となる螺旋溝(41)が形成されたスクリューロータ(40)と、該スクリューロータ(40)を回転可能に収納するシリンダ壁(31)と、上記スクリューロータ(40)を負荷に応じて回転速度可変に駆動する駆動機構(26)と、上記シリンダ壁(31)に形成されたスライド溝(33)において上記スクリューロータ(40)の外周面に対向すると共に軸方向に移動可能に設けられ、上記回転速度に応じて軸方向に移動して吐出開始位置を調整するスライドバルブ(4)とを備えたシングルスクリュー圧縮機であって、
上記スライドバルブ(4)の吐出側端面(4a)は、定格負荷よりも小さい部分負荷の運転状態におけるスライド位置において対向するスクリューロータ(40)のランド(42)の延伸方向に対応した方向に延びるように形成されている
ことを特徴とするシングルスクリュー圧縮機。 - 請求項1において、
上記スライドバルブ(4)の吐出側端面(4a)は、負荷率50%以上75%以下の運転状態におけるスライド位置において対向するスクリューロータ(40)のランド(42)の延伸方向に対応した方向に延びるように形成されている
ことを特徴とするシングルスクリュー圧縮機。 - 請求項2において、
上記スライドバルブ(4)の吐出側端面(4a)は、負荷率50%以上75%以下の運転状態におけるスライド位置において対向するスクリューロータ(40)のランド(42)の吸入側端に対応した方向に延びるように形成されている
ことを特徴とするシングルスクリュー圧縮機。 - 請求項3において、
上記スライドバルブ(4)の吐出側端面(4a)は、負荷率50%以上75%以下の運転状態におけるスライド位置において対向するスクリューロータ(40)のランド(42)の吸入側端に対応した曲面形状に形成されている
ことを特徴とするシングルスクリュー圧縮機。 - 請求項1において、
上記スライドバルブ(4)の吐出側端面(4a)は、上記スクリューロータ(40)のランド(42)の最も幅の狭い幅狭部(42a)の延伸方向に対応した方向に延びるように形成されている
ことを特徴とするシングルスクリュー圧縮機。
Priority Applications (5)
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US13/516,924 US9051935B2 (en) | 2009-12-22 | 2010-12-22 | Single screw compressor |
ES10838962T ES2721149T3 (es) | 2009-12-22 | 2010-12-22 | Compresor de tornillo simple |
BR112012015082-0A BR112012015082B1 (pt) | 2009-12-22 | 2010-12-22 | Compressor de uma hélice |
EP10838962.8A EP2518322B1 (en) | 2009-12-22 | 2010-12-22 | Single-screw compressor |
CN201080056876.8A CN102656367B (zh) | 2009-12-22 | 2010-12-22 | 单螺杆式压缩机 |
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JP2009291027A JP4735757B2 (ja) | 2009-12-22 | 2009-12-22 | シングルスクリュー圧縮機 |
JP2009291153A JP5526760B2 (ja) | 2009-12-22 | 2009-12-22 | シングルスクリュー圧縮機 |
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EP (1) | EP2518322B1 (ja) |
CN (1) | CN102656367B (ja) |
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JP2013127203A (ja) * | 2011-12-16 | 2013-06-27 | Mitsubishi Electric Corp | スクリュー圧縮機 |
US11913452B2 (en) | 2019-04-19 | 2024-02-27 | Daikin Industries, Ltd. | Screw compressor |
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JP5734438B2 (ja) | 2010-09-14 | 2015-06-17 | ジョンソン コントロールズ テクノロジー カンパニーJohnson Controls Technology Company | 容積比制御システムおよび方法 |
EP3006740B1 (en) * | 2013-05-30 | 2018-11-14 | Mitsubishi Electric Corporation | Screw compressor and refrigeration cycle device |
CN105247216B (zh) * | 2013-05-30 | 2017-05-17 | 三菱电机株式会社 | 螺杆式压缩机和冷冻循环装置 |
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CN105508243B (zh) * | 2016-01-19 | 2019-07-23 | 珠海格力电器股份有限公司 | 一种单螺杆压缩机 |
CN108167186A (zh) * | 2018-03-05 | 2018-06-15 | 珠海格力电器股份有限公司 | 螺杆压缩机及空调机组 |
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Also Published As
Publication number | Publication date |
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US20120258005A1 (en) | 2012-10-11 |
BR112012015082B1 (pt) | 2020-12-15 |
CN102656367A (zh) | 2012-09-05 |
EP2518322A1 (en) | 2012-10-31 |
ES2721149T3 (es) | 2019-07-29 |
CN102656367B (zh) | 2014-10-08 |
EP2518322B1 (en) | 2019-01-23 |
US9051935B2 (en) | 2015-06-09 |
EP2518322A4 (en) | 2014-06-11 |
BR112012015082A2 (pt) | 2017-03-07 |
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