EP3199814B1 - Screw compressor and refrigeration cycle device - Google Patents
Screw compressor and refrigeration cycle device Download PDFInfo
- Publication number
- EP3199814B1 EP3199814B1 EP14902615.5A EP14902615A EP3199814B1 EP 3199814 B1 EP3199814 B1 EP 3199814B1 EP 14902615 A EP14902615 A EP 14902615A EP 3199814 B1 EP3199814 B1 EP 3199814B1
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- EP
- European Patent Office
- Prior art keywords
- economizer
- compression chamber
- screw compressor
- screw
- slidable valve
- Prior art date
- Legal status (The legal status 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 status listed.)
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- 238000005057 refrigeration Methods 0.000 title claims description 43
- 238000007906 compression Methods 0.000 claims description 95
- 230000006835 compression Effects 0.000 claims description 94
- 239000003507 refrigerant Substances 0.000 claims description 39
- 230000002093 peripheral effect Effects 0.000 claims description 13
- 230000000149 penetrating effect Effects 0.000 claims 1
- 230000036961 partial effect Effects 0.000 description 16
- 230000018109 developmental process Effects 0.000 description 8
- 230000000694 effects Effects 0.000 description 8
- 238000004891 communication Methods 0.000 description 6
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 230000002411 adverse Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000002401 inhibitory effect Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000006837 decompression Effects 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000012447 hatching Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 230000002829 reductive effect Effects 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
Images
Classifications
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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
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
- F04C29/0014—Injection of a fluid in the working chamber for sealing, cooling and lubricating with control systems for the injection of the fluid
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
- F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type
Definitions
- the present invention relates to a screw compressor and a refrigeration cycle apparatus.
- Some traditional refrigeration cycle apparatuses are equipped with an intermediate cooler in the refrigeration cycle in order to increase the refrigeration capacity and improve the performance or coefficient of performance (ratio of the refrigeration capacity to an input to a compressor) of the refrigeration cycle (see, for example, Patent Literature 1).
- the refrigeration cycle apparatus After cooling main-stream liquid in the intermediate cooler with refrigerant gas, the refrigeration cycle apparatus performs economizing operation to introduce the refrigerant gas (hereinafter referred to as "economizer gas”) into an intermediate part of the compressor.
- the intermediate cooler is disposed between a condenser and an evaporator in the refrigeration cycle.
- the refrigeration cycle apparatus further includes an economizer pipe branching from an intermediate portion of the passage from the condenser to the evaporator, an expansion valve for intermediate cooling disposed on the economizer pipe, and a screw compressor having an economizer port connected to the economizer pipe.
- Some traditional screw compressors include a screw rotor and a casing accommodating the screw rotor.
- the casing has an economizer port for injecting refrigerant into a compression chamber defined between the screw rotor and the inner surface of the casing (see, for example, Patent Literature 2).
- EP 2 166 229 A1 relates to a compressor being capable of maximally utilizing effects of an economizer regardless of rotating speed of a screw rotor.
- a control unit advances timing of opening of economizer ports to compression chambers in accordance with increase in the rotating speed of the screw rotor.
- the economizer ports are opened earlier than complete closure of the compression chambers in highspeed operation of the screw rotor, while the economizer ports are opened with delay in low-speed operation of the screw rotor.
- EP 3 006 740 A1 relates to a compressor which comprises an economizer passage provided in a casing and allowing an outside of the casing and a slide groove in which a slide valve is provided to communicate with each other, and an economizer port provided in the slide valve and allowing the economizer passage to communicate with one of compression chambers in accordance with a position of the slide valve.
- the slide valve gradually advances a timing of starting discharge by moving from a discharge side toward a suction side.
- the economizer port is provided at a position where the economizer port communicates with a suction-pressure chamber when the slide valve is positioned at an extreme end on the suction side.
- the energy saving performance was generally represented by the coefficient of performance (ratio of the refrigeration capacity to an electric power consumption) under the rated condition (full load mode: 100% load).
- indexes based on approximately the actual operational conditions, for example, an integrated part load value (IPLV) standardized in the United States.
- IPLV integrated part load value
- Atypical refrigeration cycle apparatus runs under the rated condition in a very short period of the year. In specific, more than 90% of the annual operation is operated in a partial load mode. Most of the partial load mode is operated under 75% to 50% of the full load. The full load mode differs from the partial load mode in the flow rate of refrigerant circulation, operational compression ratio, and coefficient of performance. These circumstances of the actual operation draw attention on the IPLV. In specific, the IPLV is an index based on the coefficient of performance in the partial load mode.
- the full load mode has a large pressure difference in the refrigeration cycle, which indicates high capacity operation, whereas the partial load mode has a small pressure difference in the refrigeration cycle, which indicates low capacity operation.
- the economizing operation is effective to increase the coefficient of performance.
- the economizing operation becomes less effective. Under some conditions in the partial load mode, the economizing operation is less effective for an increase in the refrigeration capacity and adversely increases the electric power consumption, resulting in a decrease in the coefficient of performance.
- the economizing operation can be switched between the drive and halt depending on operational conditions, such as the full load mode and the partial load mode.
- An object of the invention which has been accomplished to overcome the above problems, is to provide a screw compressor and a refrigeration cycle apparatus that include an economizer port in a better position and can achieve high coefficient of performance and high refrigeration capacity in a wide range of operation.
- a screw compressor of the invention includes the features as defined in independent claim 1.
- a refrigeration cycle apparatus of the invention includes a refrigerant circuit including the screw compressor, a condenser, a high-pressure unit of an intermediate cooler, an expansion device, and an evaporator connected in sequence with a refrigerant pipe; and an economizer pipe branching from a portion between the intermediate cooler and the expansion device and connected to the economizer gas passage of the screw compressor through an expansion valve for the intermediate cooler and a low-pressure unit of the intermediate cooler.
- the invention can provide a screw compressor and a refrigeration cycle apparatus that include an economizer port in an optimized position and can achieve high coefficient of performance and high refrigeration capacity in a wide range of operation.
- Fig. 1 illustrates a refrigerant circuit of a refrigeration cycle apparatus including a screw compressor according to example 1 not within the scope of the claims, but useful for the understanding of the invention.
- the components referred to by the same reference sign are same as or equivalent to each other throughout the following description.
- the examples and embodiments of the components disclosed in the entire specification are given for mere illustration and should not be construed to limit the invention.
- the combinations of the components in the examples and the embodiment should not be construed to limit the invention.
- Hligh and low pressures are not absolutely determined relative to a fixed reference value, but relatively determined based on states and operations of the system and the apparatus, etc.
- a refrigeration cycle apparatus 100 is equipped with a refrigerant circuit including a screw compressor 102 driven by an inverter 101, a condenser 103, a high-pressure unit of an intermediate cooler 104, an expansion valve 105 (expansion device), and an evaporator 106, which are connected in sequence with a refrigerant pipe.
- the refrigeration cycle apparatus 100 further includes an economizer pipe 108, which branches from a portion between the intermediate cooler 104 and the expansion valve 105 and is connected to the screw compressor 102 through an intermediate-cooler expansion valve 107 (expansion valve for the intermediate cooler) and a low-pressure unit of the intermediate cooler 104.
- the condenser 103 cools and condenses gas discharged from the screw compressor 102.
- the expansion valve 105 performs throttle expansion to main-stream refrigerant flowing out from the intermediate cooler 104.
- the evaporator 106 evaporates the main-stream refrigerant from the expansion valve 105.
- the intermediate cooler 104 has the high-pressure unit and the low-pressure unit, as described above. High-pressure refrigerant (main-stream refrigerant between the condenser 103 and the expansion valve 105) passes through the high-pressure unit, whereas intermediate-pressure refrigerant (the pressure of part of the high-pressure refrigerant is reduced by the intermediate-cooler expansion valve 107 to an intermediate pressure within the whole pressure range in the refrigeration cycle) passes through the low-pressure unit.
- the intermediate cooler 104 then causes heat exchange between the high-pressure refrigerant and the intermediate-pressure refrigerant to cool the high-pressure refrigerant.
- the refrigeration cycle apparatus 100 further includes a controller 109.
- the controller 109 controls the inverter 101, the expansion valve 105, and the intermediate-cooler expansion valve 107, controls the position of at least one slidable valve (described below) of the screw compressor 102, and controls the drive and halt of economizing operation for injecting economizer gas into a compression chamber.
- Fig. 2 is a schematic longitudinal-sectional view of the screw compressor according to example 1.
- the screw compressor 102 includes a tubular casing 1 accommodating a motor 2.
- the motor 2 is equipped with a stator 2a fixed to the inner surface of the casing 1 and a motor rotor 2b disposed inside the stator 2a.
- the casing 1 also accommodates a screw rotor 3.
- the screw rotor 3 and the motor rotor 2b are disposed on the same axis and fixed to a screw shaft 4.
- the screw rotor 3 has helical screw grooves 5a on the outer peripheral surface, and is coupled to the motor rotor 2b fixed to the screw shaft 4 to be rotated.
- the screw grooves 5a engage with teeth 6a of gate rotors 6.
- a space surrounded by the teeth 6a of the gate rotors 6, the screw grooves 5a, and the inner peripheral surface of the casing 1 defines a compression chamber 5.
- the casing 1 is divided by a partition (not shown) into a low-pressure compartment (adjacent to the suction end) and a high-pressure compartment (adjacent to the discharge end).
- the high-pressure compartment has an outlet 7 ( Fig. 3 described below) in communication with a discharge chamber (not shown).
- the inner peripheral surface of the casing 1 has a slide groove 1a extending along the direction of the rotational axis of the screw rotor 3.
- the slide groove 1a slidably accommodates a slidable valve 8 (first slidable valve).
- the slidable valve 8 constitutes part of the inner peripheral surface with the casing 1 to define the compression chamber 5.
- the slidable valve 8 has an economizer port 8a.
- the economizer port 8a penetrates the slidable valve 8 from its outer surface to slide on the slide groove 1a to its inner surface to slide on the screw rotor 3.
- Fig. 2 illustrates an example of the casing 1 that accommodates a single slidable valve 8 having the economizer port 8a.
- the casing 1 has an economizer gas passage 1b for introducing refrigerant gas from the intermediate cooler 104 into the compression chamber 5 (the screw grooves 5a during a compression stroke).
- the economizer gas passage 1b communicates with the compression chamber 5 through the economizer port 8a.
- the economizer gas passage 1b is also connected to the economizer pipe 108.
- the refrigerant gas from the intermediate cooler 104 separates from the main stream to cool the main-stream liquid, and then flows into the compression chamber 5 through the economizer pipe 108, the economizer gas passage 1b, and the economizer port 8a.
- the economizer gas passage 1b of the casing 1 may have a space (not shown) for reducing the pulsation of flowing gas and communicate with the compression chamber 5 through the space, for example.
- the slidable valve 8 is coupled to a drive unit 10 including a piston or the like, with a coupling rod 9, and is driven by the drive unit 10 to slide in the slide groove 1a along the direction of the rotational axis of the screw rotor 3.
- the drive unit 10 for driving the slidable valve 8 a unit such as those powered by gas pressure or oil pressure, or powered by a motor other than a piston, that is, the driving method is not limited.
- the screw compressor 102 sucks refrigerant gas flowing from the evaporator 106, and compresses and discharges the refrigerant gas.
- the discharged refrigerant gas is cooled in the condenser 103.
- the refrigerant cooled in the condenser 103 flows into the intermediate cooler 104.
- the intermediate cooler 104 causes heat exchange between high-pressure refrigerant, which flows from the condenser 103 into the high-pressure unit, and intermediate-pressure refrigerant, which branches off after passing through the intermediate cooler 104, undergoes decompression in the intermediate-cooler expansion valve 107, and then enters the low-pressure unit.
- the high-pressure refrigerant that flows directly from the condenser 103 into the high-pressure unit of the intermediate cooler 104 is subcooled by the heat exchange with the intermediate-pressure refrigerant.
- the addition of subcooling degree enhances the refrigerating effects of the evaporator 106.
- the intermediate-pressure refrigerant entering the low-pressure unit of the intermediate cooler 104 cools the high-pressure refrigerant in the high-pressure unit, flows through the economizer pipe 108 and the economizer gas passage 1b, and is injected from the economizer port 8a of the slidable valve 8 into the compression chamber 5.
- the difference of the high-pressure side pressure and the intermediate pressure of the economizer gas as the high-pressure side from the pressure in the compression chamber 5 causes the economizer gas to be injected from the economizer port 8a into the compression chamber 5.
- the injected economizer gas is mixed with compressed gas.
- the pressure difference is small between the exit of the intermediate cooler and the compression chamber 5.
- Such a small pressure difference prevents the economizer gas from readily entering the compression chamber 5.
- the small pressure difference thus destabilizes the economizing operation.
- the small pressure difference impairs the effects of the increased refrigeration capacity and adversely increases the electric power consumption due to the injection of the economizer gas during compression, resulting in a decrease in the coefficient of performance.
- the intermediate-cooler expansion valve 107 is closed to halt the economizing operation under a small-pressure-difference condition.
- Fig. 3 illustrates the principle of compression in the screw compressor according to example 1.
- Fig. 3(a) illustrates a state of the compression chamber 5 during the intake stroke.
- the screw rotor 3 is driven by the motor 2 to rotate along the direction of the solid arrow. This rotation reduces the volume of the compression chamber 5, as illustrated in Fig. 3(b) .
- the economizer gas in the economizing operation enters the compression chamber 5 from the economizer port 8a during the compression stroke.
- the economizer gas in the compression chamber 5 is compressed together with sucked gas, and is discharged to the outside during the discharge stroke.
- Fig. 4 is a schematic sectional view illustrating the position of the economizer port of the screw compressor according to example 1 under a large-pressure-difference condition, such as the full load mode.
- Fig. 5 is a development view of the inner peripheral surface of the casing and the screw rotor of the screw compressor according to example 1 under a large-pressure-difference condition, such as the full load mode.
- the controller 109 controls the slidable valve 8 having the economizer port 8a to move toward the discharge end (the left of Fig. 4 or 5 ), as illustrated with the outline arrow of Fig. 4 or 5 , such that the economizer port 8a is disposed in a position (first position) so as to communicate with the economizer gas passage 1b and the compression chamber 5.
- the economizer gas passage 1b of the casing 1 thus communicates with the compression chamber 5 through the economizer port 8a.
- the economizer gas While the compression chamber 5 is being in communication with the economizer port 8a in the compression stroke, the economizer gas is injected through the economizer gas passage 1b and the economizer port 8a into the compression chamber 5.
- the pressure (intermediate pressure) in the economizer port 8a in communication with the compression chamber 5 increases, the effects of increasing the refrigeration capacity by the economizing operation decrease.
- the economizer gas which is injected into the compression chamber 5 before completion of closing of the compression chamber 5, flows from the compression chamber 5 toward the suction end and inhibits sucked gas from entering the screw grooves 5a.
- the slidable valve 8 is moved for shifting the economizer port 8a to the position illustrated in Fig. 5 , so that the economizer gas is injected into the compression chamber 5 at a low pressure as much as possible without inhibiting the sucked gas from entering the compression chamber 5. The details will be explained below.
- the economizer port 8a is disposed in the position illustrated in Fig. 5 , i.e., the position from which the economizer port 81a is open to communication with the compression chamber 5 upon the completion of trapping of the sucked gas (upon the start of compression).
- the economizer gas can thus be injected into the compression chamber 5 at a low pressure as much as possible without inhibiting the sucked gas from entering the compression chamber 5.
- the controller 109 Even in the partial load mode, the controller 109 also performs the economizing operation if the pressure difference is relatively large to ensure the economization.
- the controller 109 controls the slidable valve 8 to move to the position illustrated in Fig. 5 such that the economizer gas passage 1b of the casing 1, the economizer port 8a, and the compression chamber 5 communicate with each other. The economizer gas is thus injected into the compression chamber 5.
- Fig. 6 is a schematic sectional view illustrating the position of the economizer port of the screw compressor according to example 1 under a small-pressure-difference condition, such as the partial load mode.
- Fig. 7 is a development view of the inner peripheral surface of the casing and the screw rotor of the screw compressor according to example 1 under a small-pressure-difference condition, such as the partial load mode.
- the controller 109 controls the slidable valve 8 having the economizer port 8a to move toward the suction end (the right of Fig. 6 or 7 ), as illustrated with the outline arrow of Fig. 6 or 7 .
- the economizer port 8a is shifted to a position (hereinafter referred to as "second position") along the axis direction so as not to communicate with the compression chamber 5 (screw grooves 5a).
- the economizer port 8a thus does not communicate with the economizer gas passage 1b of the casing 1 or the compression chamber 5.
- the economizer port 8a is completely separated from the compression chamber 5 during the halt of the economizing operation.
- the economizer port 8a is shifted to the position along the axis direction so as not to communicate with the compression chamber 5 (screw grooves 5a), in other words, so as to be separated from the compression chamber 5 (screw grooves 5a) during the halt of the economizing operation. Accordingly, the economizer port 8a and the economizer gas passage 1b do not affect the compression chamber 5 from the intake stroke to the discharge stroke during the halt of the economizing operation.
- This configuration prevents the economizer port 8a and the economizer gas passage 1b from being a volume part (dead volume) that is subject to useless compression. That is, the screw compressor 102 according to example 1 has no dead volume.
- the controller 109 halts the economizing operation under the condition of a relatively small pressure difference not causing effective economization.
- the controller 109 controls the slidable valve 8 to move to the second position such that the economizer gas passage 1b of the casing 1, the economizer port 8a, and the compression chamber 5 do not communicate with each other.
- the slidable valve 8 having the economizer port 8a is accommodated in the casing 1 so as to be slidable along the direction of the rotational axis of the screw rotor 3 according to example 1.
- the slidable valve 8 can move between the first position, which allows the economizer gas passage 1b, the economizer port 8a, and the compression chamber 5 to communicate with each other, and the second position, which prevents the economizer gas passage 1b, the economizer port 8a, and the compression chamber 5 from communicating with each other.
- example 1 can provide the screw compressor 102 and the refrigeration cycle apparatus 100 that can achieve a high coefficient of performance in a wide range of operation.
- the slidable valve 8 may have any range of movement.
- the slidable valve 8, the coupling rod 9, and the drive unit 10 may be disposed, such that the first position of the slidable valve 8 is "most adjacent to the discharge end" in the range of movement of the slidable valve 8 whereas the second position of the slidable valve 8 is "most adjacent to the suction end" in the range of movement of the slidable valve 8.
- the economizer port 8a is shifted toward the suction end (the right of Fig. 8 ) during performing the economizing operation, as illustrated with the outline arrow of Fig. 8 .
- the economizer port 8a is disposed in the position along the axis direction so as to communicate with the economizer gas passage 1b and the compression chamber 5.
- the economizer gas passage 1b of the casing 1 thus communicates with the compression chamber 5 through the economizer port 8a.
- the economizer port 8a is shifted toward the discharge end (the left of Fig. 9 ) during the halt of the economizing operation, as illustrated with the outline arrow of Fig. 9 .
- the economizer port 8a is disposed in the position along the axis direction so as not to communicate with the compression chamber 5 (screw grooves 5a).
- the position to communicate the economizer passage with the compression chamber and the position not to communicate may be interchangeable.
- Example 2 differs from example 1 only in the shape of the suction end surface of the slidable valve 8 having the economizer port 8a.
- Fig. 10 is a development view of the inner peripheral surface of the casing and the screw rotor of the screw compressor according to example 2 not within the scope of the claims, but useful for the understanding of the invention.
- the following explanation of example 2 focuses on the difference from example 1.
- the components not described in example 2 are identical to those in example 1.
- the slidable valve 8 having the economizer port 8a has a suction end surface 8b, which extends along the slope of each of the screw grooves 5a.
- This shape of the suction end surface 8b in comparison to a suction end surface 8b of the slidable valve 8 perpendicular to the screw shaft 4 in example 1, can bring about the following advantageous effects: the configuration does not require an extra space for movement of the slidable valve 8 and can thus achieve a reduction in size of the components in addition to the effects comparable to those in example 1.
- the suction end surface 8b of the slidable valve 8 extends along the slope of the screw groove 5a in this example, the suction end surface 8b may be any inclined surface.
- suction end surface 8b of the slidable valve 8 extending along the slope of the screw groove 5a can ensure to have necessary surface for closing the screw groove 5a, leading to further optimization of the shape (a reduction in size).
- a reduction in the surfaces of the slidable valve 8 useless for the closing can decrease the viscous resistance of the oil between the slidable valve 8 and the outer surface of the screw rotor.
- a volume-controllable screw compressor 102 according to Embodiment: 1 further includes a slidable valve for varying the internal volume ratio.
- Fig. 11 is a development view of the inner peripheral surface of the casing and the screw rotor of the screw compressor according to Embodiment: 1 of the invention.
- the following explanation of Embodiment: 1 focuses on the differences from example 1.
- the components not described in Embodiment 1 are identical to those in example 1.
- the casing 1 further accommodates a slidable valve 11 (second slidable valve) for varying the internal volume ratio, in addition to the slidable valve 8, such that the slidable valve 11 is slidable along the direction of the rotational axis of the screw rotor 3.
- the slidable valve 11 adjusts the timing to start discharge of high-pressure gas compressed in the compression chamber 5 (the timing of completion of compression) depending on the slide position of the slidable valve 11.
- the slidable valve 11 has a discharge end surface 11a constituting part of the outlet 7. A change in the discharging area of the outlet 7 depending on the slide position varies the discharge timing and the internal volume ratio. In specific, advanced discharge timing provides an operation with a small internal volume ratio, whereas delayed discharge timing provides an operation with a large internal volume ratio.
- the internal volume ratio indicates the ratio of the volume of the compression chamber 5 just before the discharge to the volume of the compression chamber 5 upon the completion of an intake operation (start of compression), i.e., the ratio of the volume upon the opening of the outlet 7 to the volume upon the completion of the intake operation.
- start of compression i.e., the ratio of the volume upon the opening of the outlet 7 to the volume upon the completion of the intake operation.
- a screw compressor does not cause loss due to improper compression under an operational condition of a proper compression ratio, i.e., in the case of the actual compression ratio matching the internal volume ratio.
- the gas is over-compressed before the opening of an outlet to have a pressure higher than the discharge pressure, resulting in excess compression.
- the outlet opens before achieving the discharge pressure, resulting in insufficient compression that causes reverse flow of gas.
- the position of the slidable valve 11 is adjusted for optimizing the discharge timing.
- the slidable valve 8 having the economizer port 8a moves between two positions, i.e., the position allowing for communication and the position preventing the communication between the economizer gas passage 1b, the economizer port 8a, and the compression chamber 5.
- the slidable valve 11 for varying the internal volume ratio can freely move in accordance with any proper discharge timing.
- Embodiment 1 further includes the slidable valve 11 for varying the internal volume ratio that can move to a position for optimizing the discharge timing.
- the configuration can thus prevent over-compression and insufficient compression and increase the coefficient of performance in addition to bringing about the effects comparable to those in example 1. That is, Embodiment: 1 can provide the screw compressor 102 and the refrigeration cycle apparatus 100 that can achieve a higher coefficient of performance in a wide range of operation.
- the screw compressor according to the embodiment of the invention may be replaced with a twin-screw compressor including male and female screw rotors that engage with each other to define a compression chamber 5, other than a single-screw compressor.
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- Applications Or Details Of Rotary Compressors (AREA)
Description
- The present invention relates to a screw compressor and a refrigeration cycle apparatus.
- Some traditional refrigeration cycle apparatuses are equipped with an intermediate cooler in the refrigeration cycle in order to increase the refrigeration capacity and improve the performance or coefficient of performance (ratio of the refrigeration capacity to an input to a compressor) of the refrigeration cycle (see, for example, Patent Literature 1). After cooling main-stream liquid in the intermediate cooler with refrigerant gas, the refrigeration cycle apparatus performs economizing operation to introduce the refrigerant gas (hereinafter referred to as "economizer gas") into an intermediate part of the compressor. In the refrigeration cycle apparatus, the intermediate cooler is disposed between a condenser and an evaporator in the refrigeration cycle. The refrigeration cycle apparatus further includes an economizer pipe branching from an intermediate portion of the passage from the condenser to the evaporator, an expansion valve for intermediate cooling disposed on the economizer pipe, and a screw compressor having an economizer port connected to the economizer pipe.
- Some traditional screw compressors include a screw rotor and a casing accommodating the screw rotor. The casing has an economizer port for injecting refrigerant into a compression chamber defined between the screw rotor and the inner surface of the casing (see, for example, Patent Literature 2).
-
EP 2 166 229 A1 -
EP 3 006 740 A1 relates to a compressor which comprises an economizer passage provided in a casing and allowing an outside of the casing and a slide groove in which a slide valve is provided to communicate with each other, and an economizer port provided in the slide valve and allowing the economizer passage to communicate with one of compression chambers in accordance with a position of the slide valve. The slide valve gradually advances a timing of starting discharge by moving from a discharge side toward a suction side. The economizer port is provided at a position where the economizer port communicates with a suction-pressure chamber when the slide valve is positioned at an extreme end on the suction side. -
- Patent Literature 1: Japanese Unexamined Patent Application Publication No.
H11-248264 Fig. 1 ) - Patent Literature 2: Japanese Patent No.
4140488 Fig. 1 ) - For these refrigeration cycle apparatuses equipped with the screw compressors, the energy saving performance was generally represented by the coefficient of performance (ratio of the refrigeration capacity to an electric power consumption) under the rated condition (full load mode: 100% load). Recently, interest has focused on indexes based on approximately the actual operational conditions, for example, an integrated part load value (IPLV) standardized in the United States.
- Atypical refrigeration cycle apparatus runs under the rated condition in a very short period of the year. In specific, more than 90% of the annual operation is operated in a partial load mode. Most of the partial load mode is operated under 75% to 50% of the full load. The full load mode differs from the partial load mode in the flow rate of refrigerant circulation, operational compression ratio, and coefficient of performance. These circumstances of the actual operation draw attention on the IPLV. In specific, the IPLV is an index based on the coefficient of performance in the partial load mode.
- The full load mode has a large pressure difference in the refrigeration cycle, which indicates high capacity operation, whereas the partial load mode has a small pressure difference in the refrigeration cycle, which indicates low capacity operation. In the full load mode having a large pressure difference, the economizing operation is effective to increase the coefficient of performance. In the partial load mode having a smaller pressure difference, however, the economizing operation becomes less effective. Under some conditions in the partial load mode, the economizing operation is less effective for an increase in the refrigeration capacity and adversely increases the electric power consumption, resulting in a decrease in the coefficient of performance. To increase the IPLV, the economizing operation can be switched between the drive and halt depending on operational conditions, such as the full load mode and the partial load mode.
- Unfortunately, the economizer ports disclosed in
Patent Literatures - An object of the invention, which has been accomplished to overcome the above problems, is to provide a screw compressor and a refrigeration cycle apparatus that include an economizer port in a better position and can achieve high coefficient of performance and high refrigeration capacity in a wide range of operation.
- A screw compressor of the invention includes the features as defined in
independent claim 1. - A refrigeration cycle apparatus of the invention includes a refrigerant circuit including the screw compressor, a condenser, a high-pressure unit of an intermediate cooler, an expansion device, and an evaporator connected in sequence with a refrigerant pipe; and an economizer pipe branching from a portion between the intermediate cooler and the expansion device and connected to the economizer gas passage of the screw compressor through an expansion valve for the intermediate cooler and a low-pressure unit of the intermediate cooler.
- The invention can provide a screw compressor and a refrigeration cycle apparatus that include an economizer port in an optimized position and can achieve high coefficient of performance and high refrigeration capacity in a wide range of operation.
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- [
Fig. 1] Fig. 1 illustrates a refrigerant circuit of a refrigeration cycle apparatus including a screw compressor according to example 1 not within the scope of the claims, but useful for the understanding of the invention. - [
Fig. 2] Fig. 2 is a schematic longitudinal-sectional view of a screw compressor according to example 1. - [
Fig. 3] Fig. 3 illustrates the principle of compression in a screw compressor according to example 1. - [
Fig. 4] Fig. 4 is a schematic sectional view illustrating the position of an economizer port of a screw compressor according to example 1 under a large-pressure-difference condition, such as a full load mode. - [
Fig. 5] Fig. 5 is a development view of the inner peripheral surface of a casing and a screw rotor of a screw compressor according to example 1 under a large-pressure-difference condition, such as a full load mode. - [
Fig. 6] Fig. 6 is a schematic sectional view illustrating the position of an economizer port of a screw compressor according to example 1 under a small-pressure-difference condition, such as a partial load mode. - [
Fig. 7] Fig. 7 is a development view of the inner peripheral surface of a casing and a screw rotor of a screw compressor according to example 1 under a small-pressure-difference condition, such as a partial load mode. - [
Fig. 8] Fig. 8 is a schematic sectional view illustrating the position of an economizer port of a screw compressor according to example 1 under a large-pressure-difference condition, such as a full load mode. - [
Fig. 9] Fig. 9 is a schematic sectional view illustrating the position of an economizer port of a screw compressor according to example 1 under a small-pressure-difference condition, such as a partial load mode. - [
Fig. 10] Fig. 10 is a development view of the inner peripheral surface of a casing and a screw rotor of a screw compressor according to example 2 not within the scope of the claims, but useful for the understanding of the invention. - [
Fig. 11] Fig. 11 is a development view of the inner peripheral surface of a casing and a screw rotor of a screw compressor according to Embodiment: 1 of the invention. - Examples not within the scope of the claims, but useful for the understanding of the invention and the Embodiment of the invention will now be described with reference to the accompanying drawings. The description of the embodiments of the invention focuses on an example single-screw compressor equipped with a single screw rotor engaged with two gate rotors.
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Fig. 1 illustrates a refrigerant circuit of a refrigeration cycle apparatus including a screw compressor according to example 1 not within the scope of the claims, but useful for the understanding of the invention. In the accompanying drawings includingFig. 1 , the components referred to by the same reference sign are same as or equivalent to each other throughout the following description. The examples and embodiments of the components disclosed in the entire specification are given for mere illustration and should not be construed to limit the invention. In specific, the combinations of the components in the examples and the embodiment should not be construed to limit the invention. Hligh and low pressures are not absolutely determined relative to a fixed reference value, but relatively determined based on states and operations of the system and the apparatus, etc. - A
refrigeration cycle apparatus 100 is equipped with a refrigerant circuit including ascrew compressor 102 driven by aninverter 101, acondenser 103, a high-pressure unit of anintermediate cooler 104, an expansion valve 105 (expansion device), and anevaporator 106, which are connected in sequence with a refrigerant pipe. Therefrigeration cycle apparatus 100 further includes aneconomizer pipe 108, which branches from a portion between theintermediate cooler 104 and theexpansion valve 105 and is connected to thescrew compressor 102 through an intermediate-cooler expansion valve 107 (expansion valve for the intermediate cooler) and a low-pressure unit of theintermediate cooler 104. - The
condenser 103 cools and condenses gas discharged from thescrew compressor 102. Theexpansion valve 105 performs throttle expansion to main-stream refrigerant flowing out from theintermediate cooler 104. Theevaporator 106 evaporates the main-stream refrigerant from theexpansion valve 105. Theintermediate cooler 104 has the high-pressure unit and the low-pressure unit, as described above. High-pressure refrigerant (main-stream refrigerant between thecondenser 103 and the expansion valve 105) passes through the high-pressure unit, whereas intermediate-pressure refrigerant (the pressure of part of the high-pressure refrigerant is reduced by the intermediate-cooler expansion valve 107 to an intermediate pressure within the whole pressure range in the refrigeration cycle) passes through the low-pressure unit. Theintermediate cooler 104 then causes heat exchange between the high-pressure refrigerant and the intermediate-pressure refrigerant to cool the high-pressure refrigerant. - The
refrigeration cycle apparatus 100 further includes acontroller 109. Thecontroller 109 controls theinverter 101, theexpansion valve 105, and the intermediate-cooler expansion valve 107, controls the position of at least one slidable valve (described below) of thescrew compressor 102, and controls the drive and halt of economizing operation for injecting economizer gas into a compression chamber. - The
screw compressor 102 according to example 1 not within the scope of the claims, but useful for the understanding of the invention will now be described with reference toFig. 2 . -
Fig. 2 is a schematic longitudinal-sectional view of the screw compressor according to example 1. - As illustrated in
Fig. 2 , thescrew compressor 102 includes atubular casing 1 accommodating amotor 2. Themotor 2 is equipped with astator 2a fixed to the inner surface of thecasing 1 and amotor rotor 2b disposed inside thestator 2a. - The
casing 1 also accommodates ascrew rotor 3. Thescrew rotor 3 and themotor rotor 2b are disposed on the same axis and fixed to ascrew shaft 4. Thescrew rotor 3 hashelical screw grooves 5a on the outer peripheral surface, and is coupled to themotor rotor 2b fixed to thescrew shaft 4 to be rotated. Thescrew grooves 5a engage withteeth 6a ofgate rotors 6. A space surrounded by theteeth 6a of thegate rotors 6, thescrew grooves 5a, and the inner peripheral surface of thecasing 1 defines acompression chamber 5. Thecasing 1 is divided by a partition (not shown) into a low-pressure compartment (adjacent to the suction end) and a high-pressure compartment (adjacent to the discharge end). The high-pressure compartment has an outlet 7 (Fig. 3 described below) in communication with a discharge chamber (not shown). - With reference to
Fig. 2 , the inner peripheral surface of thecasing 1 has aslide groove 1a extending along the direction of the rotational axis of thescrew rotor 3. Theslide groove 1a slidably accommodates a slidable valve 8 (first slidable valve). Theslidable valve 8 constitutes part of the inner peripheral surface with thecasing 1 to define thecompression chamber 5. Theslidable valve 8 has aneconomizer port 8a. Theeconomizer port 8a penetrates theslidable valve 8 from its outer surface to slide on theslide groove 1a to its inner surface to slide on thescrew rotor 3.Fig. 2 illustrates an example of thecasing 1 that accommodates a singleslidable valve 8 having theeconomizer port 8a. - The
casing 1 has aneconomizer gas passage 1b for introducing refrigerant gas from theintermediate cooler 104 into the compression chamber 5 (thescrew grooves 5a during a compression stroke). Theeconomizer gas passage 1b communicates with thecompression chamber 5 through theeconomizer port 8a. Theeconomizer gas passage 1b is also connected to theeconomizer pipe 108. In this configuration, the refrigerant gas from theintermediate cooler 104 separates from the main stream to cool the main-stream liquid, and then flows into thecompression chamber 5 through theeconomizer pipe 108, theeconomizer gas passage 1b, and theeconomizer port 8a. Theeconomizer gas passage 1b of thecasing 1 may have a space (not shown) for reducing the pulsation of flowing gas and communicate with thecompression chamber 5 through the space, for example. - The
slidable valve 8 is coupled to a drive unit 10including a piston or the like, with acoupling rod 9, and is driven by thedrive unit 10 to slide in theslide groove 1a along the direction of the rotational axis of thescrew rotor 3. Thedrive unit 10 for driving theslidable valve 8 a unit such as those powered by gas pressure or oil pressure, or powered by a motor other than a piston, that is, the driving method is not limited. - The operation according to example 1 will now be explained.
- With reference to
Fig. 1 , the operation of the refrigerant circuit will now be explained under a large-pressure-difference condition, such as a full load (100% load) mode, in the refrigeration cycle. - The
screw compressor 102 sucks refrigerant gas flowing from theevaporator 106, and compresses and discharges the refrigerant gas. The discharged refrigerant gas is cooled in thecondenser 103. The refrigerant cooled in thecondenser 103 flows into theintermediate cooler 104. Theintermediate cooler 104 causes heat exchange between high-pressure refrigerant, which flows from thecondenser 103 into the high-pressure unit, and intermediate-pressure refrigerant, which branches off after passing through theintermediate cooler 104, undergoes decompression in the intermediate-cooler expansion valve 107, and then enters the low-pressure unit. In other words, the high-pressure refrigerant that flows directly from thecondenser 103 into the high-pressure unit of theintermediate cooler 104 is subcooled by the heat exchange with the intermediate-pressure refrigerant. The addition of subcooling degree enhances the refrigerating effects of theevaporator 106. - The intermediate-pressure refrigerant entering the low-pressure unit of the
intermediate cooler 104, cools the high-pressure refrigerant in the high-pressure unit, flows through theeconomizer pipe 108 and theeconomizer gas passage 1b, and is injected from theeconomizer port 8a of theslidable valve 8 into thecompression chamber 5. In specific, the difference of the high-pressure side pressure and the intermediate pressure of the economizer gas as the high-pressure side from the pressure in thecompression chamber 5 causes the economizer gas to be injected from theeconomizer port 8a into thecompression chamber 5. The injected economizer gas is mixed with compressed gas. - The operation of the refrigerant circuit will now be explained under a small-pressure-difference condition, such as a partial load (lower than 100% load) mode, in the refrigeration cycle.
- Under the small-pressure-difference condition, the pressure difference is small between the exit of the intermediate cooler and the
compression chamber 5. Such a small pressure difference prevents the economizer gas from readily entering thecompression chamber 5. The small pressure difference thus destabilizes the economizing operation. In addition, the small pressure difference impairs the effects of the increased refrigeration capacity and adversely increases the electric power consumption due to the injection of the economizer gas during compression, resulting in a decrease in the coefficient of performance. To address this problem, the intermediate-cooler expansion valve 107 is closed to halt the economizing operation under a small-pressure-difference condition. - The operation of the
screw compressor 102 according to example 1 will now be explained. -
Fig. 3 illustrates the principle of compression in the screw compressor according to example 1. - With reference to
Fig. 3 , the rotation of thescrew rotor 3 driven by the motor 2 (seeFig. 2 ) with the screw shaft 4 (seeFig. 2 ) relatively moves theteeth 6a of thegate rotors 6 in the compression chamber 5 (screwgrooves 5a). With this operation, an intake stroke, compression stroke, and discharge stroke are carried out at thecompression chamber 5 as one cycle, and the cycle is repeated. The following will explain the individual strokes focusing on thecompression chamber 5, which is illustrated with dotted hatching inFig. 3 . -
Fig. 3(a) illustrates a state of thecompression chamber 5 during the intake stroke. Thescrew rotor 3 is driven by themotor 2 to rotate along the direction of the solid arrow. This rotation reduces the volume of thecompression chamber 5, as illustrated inFig. 3(b) . - Further rotation of the
screw rotor 3 causes thecompression chamber 5 to communicate with theoutlet 7, as illustrated inFig. 3(c) . The high-pressure refrigerant gas compressed in thecompression chamber 5 is thus discharged to the outside through theoutlet 7. The same compression is performed again behind thescrew rotor 3. - Although the
economizer port 8a, theslidable valve 8 having theeconomizer port 8a, and theslide groove 1a are not illustrated inFig. 3 , the economizer gas in the economizing operation enters thecompression chamber 5 from theeconomizer port 8a during the compression stroke. The economizer gas in thecompression chamber 5 is compressed together with sucked gas, and is discharged to the outside during the discharge stroke. - The following explanation focuses on the positional relationship of the
economizer port 8a with theeconomizer gas passage 1b and the compression chamber 5 (screwgrooves 5a) under a large-pressure-difference condition, such as a full load mode. -
Fig. 4 is a schematic sectional view illustrating the position of the economizer port of the screw compressor according to example 1 under a large-pressure-difference condition, such as the full load mode.Fig. 5 is a development view of the inner peripheral surface of the casing and the screw rotor of the screw compressor according to example 1 under a large-pressure-difference condition, such as the full load mode. - During the drive of the economizing operation, the
controller 109 controls theslidable valve 8 having theeconomizer port 8a to move toward the discharge end (the left ofFig. 4 or5 ), as illustrated with the outline arrow ofFig. 4 or5 , such that theeconomizer port 8a is disposed in a position (first position) so as to communicate with theeconomizer gas passage 1b and thecompression chamber 5. Theeconomizer gas passage 1b of thecasing 1 thus communicates with thecompression chamber 5 through theeconomizer port 8a. - While the
compression chamber 5 is being in communication with theeconomizer port 8a in the compression stroke, the economizer gas is injected through theeconomizer gas passage 1b and theeconomizer port 8a into thecompression chamber 5. In this configuration, as the pressure (intermediate pressure) in theeconomizer port 8a in communication with thecompression chamber 5 increases, the effects of increasing the refrigeration capacity by the economizing operation decrease. In addition, the economizer gas, which is injected into thecompression chamber 5 before completion of closing of thecompression chamber 5, flows from thecompression chamber 5 toward the suction end and inhibits sucked gas from entering thescrew grooves 5a. To address this problem, theslidable valve 8 is moved for shifting theeconomizer port 8a to the position illustrated inFig. 5 , so that the economizer gas is injected into thecompression chamber 5 at a low pressure as much as possible without inhibiting the sucked gas from entering thecompression chamber 5. The details will be explained below. - The
compression chamber 5, which is surrounded by a thick broken line inFig. 5 , is in the position at which suction of gas (trapping of sucked gas) is completed. Theeconomizer port 8a is disposed in the position illustrated inFig. 5 , i.e., the position from which the economizer port 81a is open to communication with thecompression chamber 5 upon the completion of trapping of the sucked gas (upon the start of compression). The economizer gas can thus be injected into thecompression chamber 5 at a low pressure as much as possible without inhibiting the sucked gas from entering thecompression chamber 5. - Even in the partial load mode, the
controller 109 also performs the economizing operation if the pressure difference is relatively large to ensure the economization. In specific, thecontroller 109 controls theslidable valve 8 to move to the position illustrated inFig. 5 such that theeconomizer gas passage 1b of thecasing 1, theeconomizer port 8a, and thecompression chamber 5 communicate with each other. The economizer gas is thus injected into thecompression chamber 5. - The following explanation focuses on the positional relationship of the
economizer port 8a with theeconomizer gas passage 1b and the compression chamber 5 (screwgrooves 5a) under a small-pressure-difference condition, such as a partial load mode. -
Fig. 6 is a schematic sectional view illustrating the position of the economizer port of the screw compressor according to example 1 under a small-pressure-difference condition, such as the partial load mode.Fig. 7 is a development view of the inner peripheral surface of the casing and the screw rotor of the screw compressor according to example 1 under a small-pressure-difference condition, such as the partial load mode. - During the halt of the economizing operation, the
controller 109 controls theslidable valve 8 having theeconomizer port 8a to move toward the suction end (the right ofFig. 6 or7 ), as illustrated with the outline arrow ofFig. 6 or7 . In specific, theeconomizer port 8a is shifted to a position (hereinafter referred to as "second position") along the axis direction so as not to communicate with the compression chamber 5 (screwgrooves 5a). Theeconomizer port 8a thus does not communicate with theeconomizer gas passage 1b of thecasing 1 or thecompression chamber 5. In other words, theeconomizer port 8a is completely separated from thecompression chamber 5 during the halt of the economizing operation. - The
economizer port 8a is shifted to the position along the axis direction so as not to communicate with the compression chamber 5 (screwgrooves 5a), in other words, so as to be separated from the compression chamber 5 (screwgrooves 5a) during the halt of the economizing operation. Accordingly, theeconomizer port 8a and theeconomizer gas passage 1b do not affect thecompression chamber 5 from the intake stroke to the discharge stroke during the halt of the economizing operation. This configuration prevents theeconomizer port 8a and theeconomizer gas passage 1b from being a volume part (dead volume) that is subject to useless compression. That is, thescrew compressor 102 according to example 1 has no dead volume. - Even in the full load mode, the
controller 109 halts the economizing operation under the condition of a relatively small pressure difference not causing effective economization. In specific, thecontroller 109 controls theslidable valve 8 to move to the second position such that theeconomizer gas passage 1b of thecasing 1, theeconomizer port 8a, and thecompression chamber 5 do not communicate with each other. - As described above, the
slidable valve 8 having theeconomizer port 8a is accommodated in thecasing 1 so as to be slidable along the direction of the rotational axis of thescrew rotor 3 according to example 1. Theslidable valve 8 can move between the first position, which allows theeconomizer gas passage 1b, theeconomizer port 8a, and thecompression chamber 5 to communicate with each other, and the second position, which prevents theeconomizer gas passage 1b, theeconomizer port 8a, and thecompression chamber 5 from communicating with each other. - With this configuration, the economizing operation is effectively performed under a large-pressure-difference condition (where the pressure difference is larger than a predetermined pressure difference in the refrigeration cycle), resulting in an increase in the coefficient of performance. The economizing operation is halted under a small-pressure-difference condition (where the pressure difference is equal to or smaller than the predetermined pressure difference in the refrigeration cycle). The configuration has no dead volume during the halt, as described above, and thus causes no re-expansion loss, resulting in an increase in the coefficient of performance. That is, example 1 can provide the
screw compressor 102 and therefrigeration cycle apparatus 100 that can achieve a high coefficient of performance in a wide range of operation. - The
slidable valve 8 may have any range of movement. Theslidable valve 8, thecoupling rod 9, and thedrive unit 10 may be disposed, such that the first position of theslidable valve 8 is "most adjacent to the discharge end" in the range of movement of theslidable valve 8 whereas the second position of theslidable valve 8 is "most adjacent to the suction end" in the range of movement of theslidable valve 8. - Alternatively, the
economizer port 8a is shifted toward the suction end (the right ofFig. 8 ) during performing the economizing operation, as illustrated with the outline arrow ofFig. 8 . In specific, theeconomizer port 8a is disposed in the position along the axis direction so as to communicate with theeconomizer gas passage 1b and thecompression chamber 5. Theeconomizer gas passage 1b of thecasing 1 thus communicates with thecompression chamber 5 through theeconomizer port 8a. In this case, theeconomizer port 8a is shifted toward the discharge end (the left ofFig. 9 ) during the halt of the economizing operation, as illustrated with the outline arrow ofFig. 9 . In specific, theeconomizer port 8a is disposed in the position along the axis direction so as not to communicate with the compression chamber 5 (screwgrooves 5a). As described above, the position to communicate the economizer passage with the compression chamber and the position not to communicate may be interchangeable. - Example 2 differs from example 1 only in the shape of the suction end surface of the
slidable valve 8 having theeconomizer port 8a. -
Fig. 10 is a development view of the inner peripheral surface of the casing and the screw rotor of the screw compressor according to example 2 not within the scope of the claims, but useful for the understanding of the invention. The following explanation of example 2 focuses on the difference from example 1. The components not described in example 2 are identical to those in example 1. - According to example 2, the
slidable valve 8 having theeconomizer port 8a has asuction end surface 8b, which extends along the slope of each of thescrew grooves 5a. This shape of thesuction end surface 8b, in comparison to asuction end surface 8b of theslidable valve 8 perpendicular to thescrew shaft 4 in example 1, can bring about the following advantageous effects: the configuration does not require an extra space for movement of theslidable valve 8 and can thus achieve a reduction in size of the components in addition to the effects comparable to those in example 1. Although thesuction end surface 8b of theslidable valve 8 extends along the slope of thescrew groove 5a in this example, thesuction end surface 8b may be any inclined surface. It should be noted that thesuction end surface 8b of theslidable valve 8 extending along the slope of thescrew groove 5a can ensure to have necessary surface for closing thescrew groove 5a, leading to further optimization of the shape (a reduction in size). In addition, a reduction in the surfaces of theslidable valve 8 useless for the closing can decrease the viscous resistance of the oil between theslidable valve 8 and the outer surface of the screw rotor. - In comparison to the
screw compressor 102 according to example 1 or 2 including theslidable valve 8 for varying the position of theeconomizer port 8a, a volume-controllable screw compressor 102 according to Embodiment: 1 further includes a slidable valve for varying the internal volume ratio. -
Fig. 11 is a development view of the inner peripheral surface of the casing and the screw rotor of the screw compressor according to Embodiment: 1 of the invention. The following explanation of Embodiment: 1 focuses on the differences from example 1. The components not described inEmbodiment 1 are identical to those in example 1. - In the
screw compressor 102 according to Embodiment: 1, thecasing 1 further accommodates a slidable valve 11 (second slidable valve) for varying the internal volume ratio, in addition to theslidable valve 8, such that theslidable valve 11 is slidable along the direction of the rotational axis of thescrew rotor 3. Theslidable valve 11 adjusts the timing to start discharge of high-pressure gas compressed in the compression chamber 5 (the timing of completion of compression) depending on the slide position of theslidable valve 11. Theslidable valve 11 has adischarge end surface 11a constituting part of theoutlet 7. A change in the discharging area of theoutlet 7 depending on the slide position varies the discharge timing and the internal volume ratio. In specific, advanced discharge timing provides an operation with a small internal volume ratio, whereas delayed discharge timing provides an operation with a large internal volume ratio. - The internal volume ratio indicates the ratio of the volume of the
compression chamber 5 just before the discharge to the volume of thecompression chamber 5 upon the completion of an intake operation (start of compression), i.e., the ratio of the volume upon the opening of theoutlet 7 to the volume upon the completion of the intake operation. In general, a screw compressor does not cause loss due to improper compression under an operational condition of a proper compression ratio, i.e., in the case of the actual compression ratio matching the internal volume ratio. In an operation of a small compression ratio, however, the gas is over-compressed before the opening of an outlet to have a pressure higher than the discharge pressure, resulting in excess compression. In an operation of a high compression ratio, the outlet opens before achieving the discharge pressure, resulting in insufficient compression that causes reverse flow of gas. To address this problem, the position of theslidable valve 11 is adjusted for optimizing the discharge timing. - The
slidable valve 8 having theeconomizer port 8a moves between two positions, i.e., the position allowing for communication and the position preventing the communication between theeconomizer gas passage 1b, theeconomizer port 8a, and thecompression chamber 5. In contrast, theslidable valve 11 for varying the internal volume ratio can freely move in accordance with any proper discharge timing. - As described above, the configuration according to
Embodiment 1 further includes theslidable valve 11 for varying the internal volume ratio that can move to a position for optimizing the discharge timing. The configuration can thus prevent over-compression and insufficient compression and increase the coefficient of performance in addition to bringing about the effects comparable to those in example 1. That is, Embodiment: 1 can provide thescrew compressor 102 and therefrigeration cycle apparatus 100 that can achieve a higher coefficient of performance in a wide range of operation. - The screw compressor according to the embodiment of the invention may be replaced with a twin-screw compressor including male and female screw rotors that engage with each other to define a
compression chamber 5, other than a single-screw compressor. -
- 1
casing 1a slide groove 1beconomizer gas passage 2motor 2a stator2b motor rotor 3screw rotor 4screw shaft 5compression chamber 5a screw groove 6gate 7rotor 6a toothoutlet 8slidable valve 8a economizer port 8bintake end surface 9coupling rod 10drive unit 11slidable valve 11a dischargeend surface 100refrigeration cycle apparatus 101inverter 102screw compressor 103condenser 104 intermediate cooler 105expansion valve 106 evaporator - 107 intermediate-
cooler expansion valve 108economizer pipe 109 controller
Claims (7)
- A screw compressor comprising:a casing (1);a screw rotor (3) rotatable in the casing (1);a compression chamber (5) defined between the casing (1) and the screw rotor (3) and configured to compress refrigerant gas;a slide groove (1a) disposed on an inner peripheral surface of the casing (1) and extending along a direction of a rotational axis of the screw rotor (3);an economizer gas passage (1b), connectable to an economizer, extending through the casing (1) to communicate between an outside of the casing (1) and the slide groove (1a);a first slidable valve (8) disposed in the slide groove (1a) to be slidable along the direction of the rotational axis of the screw rotor (3);an economizer port (8a) penetrating through the first slidable valve (8) to communicate between the economizer gas passage (1b) and the compression chamber (5) depending on a position of the first slidable valve (8),the screw compressor is characterised bythe first slidable valve (8) being configured to move between a first position and a second position, the first slidable valve (8) at the first position allowing the economizer gas passage (1b) to communicate with the compression chamber (5), the first slidable valve (8) at the second position preventing the economizer port (8a) from communicating with the compression chamber (5); anda second slidable valve (11) disposed in the casing (1), the second slidable valve (11) being slidable along the direction of the rotational axis of the screw rotor (3) to adjust timing of discharge from the compression chamber (5).
- The screw compressor of claim 1, wherein, the economizer port (8a) is configured to open from the first position to communicate with the compression chamber (5) upon completion of trapping of the refrigerant gas in the compression chamber (5).
- The screw compressor (102) of any one of claims 1 to 2, wherein
the screw compressor (102) is included in a refrigeration cycle, and
the first slidable valve (8) is situated in the first position under a large-pressure-difference condition where a high-low pressure difference in the refrigeration cycle is larger than a predetermined pressure difference in the refrigeration cycle, and the first slidable valve (8) is situated in the second position under a small-pressure-difference condition where the high-low pressure difference is equal to or smaller than the predetermined pressure difference in the refrigeration cycle. - The screw compressor (102) of any one of claims 1 to 3, wherein a suction end surface of the first slidable valve (8) is an inclined surface.
- The screw compressor of claim 4, wherein the inclined surface extends along a slope of a screw groove (5a) defining the compression chamber (5).
- The screw compressor (102) of any one of claims 1 to 5, further comprising an electric motor (2) driven by an inverter (101) and configured to rotate the screw rotor (3).
- A refrigeration cycle apparatus comprising:a refrigerant circuit comprising the screw compressor (102) of any one of claims 1 to 6, a condenser (103), a high-pressure unit of an intermediate cooler (104), an expansion device (105), and an evaporator (106) connected in sequence with a refrigerant pipe; andan economizer pipe (108) branching from a portion between the intermediate cooler (104) and the expansion device (105), the economizer pipe (108) being connected to the economizer gas passage (1b) of the screw compressor (102) through an expansion valve (107) for the intermediate cooler (104) and a low-pressure unit of the intermediate cooler (104).
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EP3505765B1 (en) * | 2016-08-23 | 2020-04-29 | Mitsubishi Electric Corporation | Screw compressor and refrigeration cycle device |
EP3569950B1 (en) * | 2017-01-11 | 2022-03-16 | Mitsubishi Electric Corporation | Refrigeration cycle device |
CN107461222A (en) * | 2017-09-13 | 2017-12-12 | 北京工业大学 | A kind of single-screw expander of integrated guiding valve |
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CN114216173B (en) * | 2021-12-16 | 2023-02-17 | 珠海格力电器股份有限公司 | Compressor with fresh air conveying function, air conditioner and control method of air conditioner |
CN115666026B (en) * | 2022-09-15 | 2023-09-19 | 南京晗创智能科技有限公司 | Deep foundation pit monitoring measuring point protection device |
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JPS6035169U (en) * | 1983-08-17 | 1985-03-11 | 株式会社神戸製鋼所 | screw refrigeration compressor |
JPH0820137B2 (en) * | 1990-09-26 | 1996-03-04 | ダイキン工業株式会社 | Screw refrigeration equipment |
JPH05106572A (en) * | 1991-10-17 | 1993-04-27 | Daikin Ind Ltd | Single shaft type screw compressor |
JP4183021B1 (en) * | 2007-06-11 | 2008-11-19 | ダイキン工業株式会社 | Compressor and refrigeration equipment |
CN103486038B (en) * | 2012-06-12 | 2016-07-06 | 珠海格力电器股份有限公司 | Guiding valve, guiding valve governor motion and there is the helical-lobe compressor of this guiding valve governor motion |
CN103527485A (en) * | 2012-07-02 | 2014-01-22 | 珠海格力电器股份有限公司 | Slide valve for screw compressor and screw compressor including slide valve |
CN202628525U (en) * | 2012-07-02 | 2012-12-26 | 珠海格力电器股份有限公司 | Slide valve for screw compressor and screw compressor comprising slide valve |
CN102909580B (en) * | 2012-08-23 | 2015-04-01 | 联德机械(杭州)有限公司 | Sliding valve tool for twin-screw compressor and sliding valve processing method |
JP6058133B2 (en) * | 2013-05-30 | 2017-01-11 | 三菱電機株式会社 | Screw compressor and refrigeration cycle apparatus |
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2014
- 2014-09-24 WO PCT/JP2014/075230 patent/WO2016046907A1/en active Application Filing
- 2014-09-24 CN CN201480080608.8A patent/CN106605069B/en active Active
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JPWO2016046907A1 (en) | 2017-04-27 |
EP3199814A1 (en) | 2017-08-02 |
EP3199814A4 (en) | 2018-05-09 |
CN106605069A (en) | 2017-04-26 |
WO2016046907A1 (en) | 2016-03-31 |
CN106605069B (en) | 2019-07-12 |
JP6177449B2 (en) | 2017-08-09 |
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