US20220082099A1 - Screw compressor - Google Patents

Screw compressor Download PDF

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Publication number
US20220082099A1
US20220082099A1 US17/419,356 US201917419356A US2022082099A1 US 20220082099 A1 US20220082099 A1 US 20220082099A1 US 201917419356 A US201917419356 A US 201917419356A US 2022082099 A1 US2022082099 A1 US 2022082099A1
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Prior art keywords
variable
valve
value
screw compressor
ratio
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US17/419,356
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English (en)
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Shun OKADA
Masaaki Kamikawa
Masahiro Kanda
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: OKADA, SHUN, KAMIKAWA, MASAAKI, KANDA, MASAHIRO
Publication of US20220082099A1 publication Critical patent/US20220082099A1/en
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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
    • 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
    • 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
    • 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

Definitions

  • the present disclosure relates to a screw compressor used for refrigerant compression in, for example, a refrigerator or an air-conditioning apparatus.
  • variable Vi valve a variable internal-volume-ratio valve
  • the internal volume ratio in the screw compressor is a ratio between a tooth groove space volume at the time of suction and a tooth groove space volume immediately before discharge, and represents a ratio between a volume when the suction is completed and a volume when a discharge port is opened.
  • the variable Vi valve of Patent Literature 1 is controlled such that the difference between an optimum Vi value calculated from a discharge pressure HP and a suction pressure LP and a current Vi value obtained from a position detecting unit decreases.
  • the opening degree of the variable Vi valve is adjusted to minimize motor driving power.
  • the screw compressor has an appropriate compression ratio corresponding to the internal volume ratio, and an inappropriate compression loss is not generated under an operating condition where the compression ratio at the time of actual operation is the appropriate compression ratio.
  • gas is excessively compressed to a pressure equal to or higher than a discharge pressure before the discharge port opens, and excessive compression work is performed.
  • the discharge port opens before the pressure reaches the discharge pressure, causing a state of insufficient compression in which backflow of gas is generated. Both of the operation at the low compression ratio and the operation at the high compression ratio cause a loss of power and cause a decrease in efficiency.
  • Patent Literature 1 a technique has been proposed in which the internal volume ratio is made variable by steplessly adjusting the position of the variable Vi valve to attain the internal volume ratio at which a high compressor efficiency is obtained for a compression ratio (discharge pressure/suction pressure) depending on an operation load.
  • position control of the variable Vi valve is steplessly performed, and a control amount of the variable Vi valve is calculated from detection results of a discharge pressure, a suction pressure, and a rotation frequency. That is, in Patent Literature 1, the position control of the variable Vi valve is stepless control, and hence the configuration and control are complicated.
  • the present disclosure has been made to address the above-described problems, and an object of the present disclosure is to obtain a screw compressor whose configuration and control can be simplified while an internal volume ratio is made variable.
  • a screw compressor of an embodiment of the present disclosure includes an internal-volume-ratio variable mechanism including a variable Vi valve configured to make a Vi value being an internal volume ratio variable.
  • the screw compressor controls a position of the variable Vi valve in two stages.
  • the position of the variable Vi valve when the Vi value is set to be large is set to attain a Vi value with which a compressor efficiency during operation under a predetermined high-load condition or a predetermined high-compression-ratio condition is equal to or higher than a set efficiency set in advance.
  • FIG. 1 is a general configuration diagram of a screw compressor according to Embodiment 1 of the present disclosure.
  • FIG. 2 is a schematic diagram of an internal-volume-ratio variable mechanism including a driving device for the screw compressor according to Embodiment 1 of the present disclosure.
  • FIG. 3 is an operation schematic diagram when a Vi value is large in the screw compressor according to Embodiment 1 of the present disclosure.
  • FIG. 4 is an operation schematic diagram when a Vi value is small in the screw compressor according to Embodiment 1 of the present disclosure.
  • FIG. 5 is an operation schematic diagram when a Vi value is large in the screw compressor according to Embodiment 2 of the present disclosure.
  • FIG. 6 is an operation schematic diagram when a Vi value is small in the screw compressor according to Embodiment 2 of the present disclosure.
  • FIG. 7 illustrates a modification of the screw compressor according to any one of Embodiment 1 and Embodiment 2 of the present disclosure.
  • FIG. 1 is a general configuration diagram of a screw compressor according to Embodiment 1 of the present disclosure.
  • the screw compressor according to Embodiment 1 is a single screw compressor, and as schematically illustrated in FIG. 1 , the screw compressor includes a cylindrical casing main body 1 , a screw rotor 3 housed in the casing main body 1 , and a motor 2 that rotatably drives the screw rotor 3 .
  • the motor 2 includes a stator 2 a that is secured in contact with the inside of the casing main body 1 and a motor rotor 2 b that is disposed inside the stator 2 a .
  • the rotation speed of the motor 2 is controlled by an inverter method.
  • the capacity control for operating the screw compressor at a desired operation compression ratio may be implemented through rotation speed control by driving the motor 2 with an inverter.
  • the screw rotor 3 and the motor rotor 2 b are disposed on the same axis, and both are secured to a screw shaft 4 .
  • a plurality of helical grooves (hereinafter referred to as screw grooves) 3 a are formed in the outer peripheral surface of the screw rotor 3 .
  • the screw rotor 3 is coupled to and rotatably driven by the motor rotor 2 b secured to the screw shaft 4 .
  • the space in the screw grooves 3 a formed in the screw rotor 3 is surrounded by the inner cylindrical surface of the casing main body 1 and a pair of gate rotors (not illustrated) that mesh with and are engaged with the grooves to define a compression chamber 5 .
  • a discharge pressure side and a suction pressure side are separated from each other by a separation wall (not illustrated).
  • a discharge chamber 6 and a discharge port 7 that opens to the discharge chamber 6 are formed on the discharge pressure side.
  • a suction chamber 16 is formed on the suction pressure side.
  • the casing main body 1 is further provided with a pair of variable Vi valves 8 that are coupled to a pair of rods 9 and a pair of driving devices 10 and are movable in the axial direction.
  • the variable Vi valves 8 define part of the discharge port 7 . Illustration of the driving device 10 coupled to the other variable Vi valve 8 is omitted.
  • FIG. 2 is a schematic diagram of an internal-volume-ratio variable mechanism including a driving device for the screw compressor according to Embodiment 1 of the present disclosure.
  • the driving device 10 forms part of an internal-volume-ratio variable mechanism (hereinafter, referred to as a variable Vi mechanism), and is configured to couple a piston 12 provided in a cylinder 11 and the variable Vi valve 8 to each other by the rod 9 .
  • a variable Vi mechanism an internal-volume-ratio variable mechanism
  • the variable Vi valve 8 includes a valve main body 8 a , a guide portion 8 b , and a coupling portion 8 c .
  • the coupling portion 8 c is provided at a discharge-port-side end portion 8 e of the guide portion 8 b .
  • the rod 9 is coupled to an end surface of the guide portion 8 b on the side near the driving device 10 .
  • the discharge-port-side end portion 8 d of the valve main body 8 a and a discharge-port-side end portion 8 e of the guide portion 8 b are coupled to each other by the coupling portion 8 c , and the gap therebetween serves as a discharge gap 8 f communicating with the discharge port 7 .
  • the inside of the cylinder 11 is partitioned into two spatial chambers by the piston 12 .
  • a cylinder chamber 13 a is formed on the front side (on the side of the variable Vi valve) of the piston 12
  • a cylinder chamber 13 b is formed on the rear side (on the side opposite to the variable Vi valve) of the piston 12 .
  • the cylinder 11 has a pressure introduction hole 113 a provided on the cylinder chamber 13 a side close to the variable Vi valve 8 .
  • the cylinder 11 also has a pressure introduction hole 113 b provided on the cylinder chamber 13 b side far from the variable Vi valve 8 .
  • the cylinder chamber 13 a communicates with the discharge chamber 6 illustrated in FIG. 1 via the pressure introduction hole 113 a and a flow path 15 a , and a discharge pressure is normally introduced into the cylinder chamber 13 a .
  • the cylinder chamber 13 b communicates with the discharge chamber 6 illustrated in FIG. 1 through the pressure introduction hole 113 b and a flow path 15 b and communicates with the suction chamber 16 illustrated in FIG. 1 through a flow path 15 c branched from the middle of the flow path 15 b .
  • the flow path 15 b is provided with a solenoid valve 14 b that opens and closes the flow path 15 b
  • the flow path 15 c is provided with a solenoid valve 14 a that opens and closes the flow path 15 c .
  • a discharge pressure or a suction pressure is selectively introduced into the cylinder chamber 13 b by opening and closing of the solenoid valve 14 a and the solenoid valve 14 b.
  • the solenoid valve 14 a and the solenoid valve 14 b described above are examples, and each may be any valve unit that is capable of opening and closing a flow path or switching flow paths.
  • the solenoid valve 14 a and the solenoid valve 14 b each may be a stop valve or a three-way valve. In the case of a three-way valve capable of switching flow paths, it is sufficient that one three-way valve is provided at a branch portion of the flow paths, and thus the solenoid valve 14 a and the solenoid valve 14 b may be omitted.
  • the flow path 15 a , the flow path 15 b , and the flow path 15 c may be formed inside the wall of the casing main body 1 and the wall of the cylinder 11 , or may be connected by using a pipe.
  • the Vi value can be set to two values of a large value and a small value.
  • FIG. 3 is an operation schematic diagram when a Vi value is large in the screw compressor according to Embodiment 1 of the present disclosure.
  • the driving device 10 positions the variable Vi valve 8 in the left direction represented by the arrow in the drawing, thereby delaying the timing at which the discharge port 7 opens.
  • the solenoid valve 14 a when the Vi value is large, the solenoid valve 14 a is opened and the solenoid valve 14 b is closed so that the pressure in the cylinder chamber 13 b is a suction pressure.
  • the cylinder chamber 13 a is coupled to the discharge chamber 6 , and a discharge pressure is normally introduced into the cylinder chamber 13 a .
  • the piston 12 is to move in the left direction in the drawing due to the pressure difference in the cylinder 11 .
  • variable Vi valve 8 coupled to the piston 12 , a suction pressure acts on a suction-side end portion 8 g of the valve main body 8 a , and a discharge pressure immediately after discharge acts on the discharge-port-side end portion 8 d .
  • the same pressure as the pressure acting on the discharge-port-side end portion 8 d acts on the discharge-port-side end portion 8 e of the guide portion 8 b in directions opposite to each other.
  • a discharge pressure acts on a driving-device-side end portion 8 h of the guide portion 8 b .
  • the loads acting on the discharge-port-side end portion 8 d and the discharge-port-side end portion 8 e in the variable Vi valve 8 cancel out each other.
  • the variable Vi valve 8 is to move in the right direction in the drawing due to the pressure difference between the pressure acting on the driving-device-side end portion 8 h and the pressure acting on the suction-side end portion 8 g.
  • the area of each of both end surfaces in the movement direction of the piston 12 is set to be larger than the area of the driving-device-side end portion 8 h of the variable Vi valve 8 .
  • the piston 12 and the variable Vi valve 8 move in the left direction in the drawing due to the pressure difference received in both the areas. Since the variable Vi valve 8 stops at a position at which the piston 12 abuts against the wall surface of the cylinder chamber 13 , the variable Vi valve 8 is accurately positioned at a position at which the Vi value is large.
  • FIG. 4 is an operation schematic diagram when the Vi value is small in the screw compressor according to Embodiment 1 of the present disclosure.
  • the driving device 10 positions the variable Vi valve 8 in the right direction represented by the arrow in the drawing, thereby advancing the timing at which the discharge port 7 opens.
  • the solenoid valve 14 a when the Vi value is small, the solenoid valve 14 a is closed and the solenoid valve 14 b is opened so that the pressure in the cylinder chamber 13 b is a discharge pressure.
  • the cylinder chamber 13 a is coupled to the discharge chamber 6 and a discharge pressure is normally introduced into the cylinder chamber 13 a , there is no pressure difference in the cylinder chamber 13 .
  • a suction pressure acts on the suction-side end portion 8 g of the valve main body 8 a
  • a discharge pressure immediately after discharge acts on the discharge-port-side end portion 8 d .
  • the same pressure as the pressure acting on the discharge-port-side end portion 8 d acts on the discharge-port-side end portion 8 e of the guide portion 8 b in directions opposite to each other.
  • a discharge pressure acts on the driving-device-side end portion 8 h of the guide portion 8 b.
  • variable Vi valve 8 moves in the right direction in the drawing due to the pressure difference between the discharge pressure acting on the driving-device-side end portion 8 h and the suction pressure acting on the suction-side end portion 8 g . Since the variable Vi valve 8 stops at a position at which the piston 12 abuts against the wall surface of the cylinder chamber 13 , the variable Vi valve 8 is accurately positioned at a position at which the Vi value is small. Alternatively, as illustrated in FIG. 1 , the variable Vi valve 8 may be positioned at a position where the suction-side end portion 8 g of the variable Vi valve 8 abuts against the wall surface of the casing main body 1 .
  • the large-side Vi value may be set as follows.
  • the operation range is set, for example, by setting an upper limit temperature for the temperature of discharged refrigerant gas, the temperature of windings of the motor stator, or another temperature.
  • the evaporating temperature is constant, increasing the condensing temperature as high as possible in a range lower than the upper limit temperature leads to securing a wide operation range.
  • the condensing temperature is constant, making the evaporating temperature as low or as high as possible leads to securing a wide operation range.
  • the temperature of the discharged refrigerant gas is likely to increase during operation under a high-compression-ratio condition, and the winding temperature is likely to increase under a high-load condition or a high-compression-ratio condition.
  • the high-compression-ratio condition involves conditions including a high condensing temperature and a low evaporating temperature.
  • the high-load condition involves conditions including a high condensing temperature and a high evaporating temperature.
  • a measure such as reducing the rotation speed of the compressor to decrease the condensing temperature has to be taken so that the operating temperature condition falls within the operation range. That is, when it is desired to continue the operation while keeping the condensing temperature high, the temperature of the discharged refrigerant gas and the winding temperature increase during operation under the high-load condition or the high-compression-ratio condition.
  • a measure such as decreasing the condensing temperature is required, and the operation range is narrowed.
  • the temperature of the discharged refrigerant gas and the winding temperature under a certain operating condition tend to decrease as the compressor efficiency under the operating condition increases.
  • the compressor efficiency is determined by the internal structure of the compressor and structural elements such as the number of winding turns of the motor.
  • the large-side Vi value is set to a Vi value with which the compressor efficiency is equal to or higher than a set efficiency set in advance during operation under a predetermined high-load condition or a predetermined high-compression-ratio condition.
  • the compressor efficiency is a value that changes depending on the Vi value, and is expressed by a graph that projects upward when the horizontal axis represents Vi and the vertical axis represents the compressor efficiency. That is, there is a Vi value with which the compressor efficiency is the maximum.
  • the large-side Vi value may be the Vi value when the compressor efficiency is the maximum, or in other words, only has to be set to a value with which the compressor efficiency is equal to or higher than the set efficiency.
  • the set efficiency only has to be appropriately set depending on performance or another factor required for the screw compressor. For example, when the maximum efficiency is 100%, the set efficiency may be 95% or more.
  • the Vi value is set as described above.
  • the position when the variable Vi valve 8 is moved to the side where the Vi value is large is set to attain the set Vi value.
  • the large-side Vi value is set so that the rated performance is improved.
  • the rated performance is performance under conditions defined by industrial standards or other standards, and represents the performance of the compressor.
  • the rated performance is a value that changes depending on the Vi value, and is represented by a graph that projects upward when the horizontal axis represents Vi and the vertical axis represents the rated performance. That is, there is a Vi value with which the rated performance is the maximum.
  • the large-side Vi value may be the Vi value when the rated performance is the maximum, or in other words, only has to be set to a Vi value with which the rated performance is equal to or higher than a set performance set in advance.
  • the set performance only has to be appropriately set depending on performance or another factor required for the screw compressor. For example, when the maximum performance is 100%, the set performance may be 95% or more.
  • the Vi value is set as described above.
  • the position when the variable Vi valve 8 is moved to the side where the Vi value is large is set to attain the set Vi value.
  • the small-side Vi value is set as follows.
  • COP representing energy consumption efficiency
  • IPLV integrated part load value
  • ESEER European seasonal energy efficiency ratio
  • an IPLV that is a primary annual performance factor is calculated by the following formula.
  • IPLV 0.01 ⁇ A+ 0.42 ⁇ B+ 0.45 ⁇ C+ 0.12 ⁇ D
  • the weight to be multiplied differs depending on the load during operation.
  • operation at 75% load accounts for 42%
  • operation at 50% load accounts for 45%.
  • the weights for the two conditions are large in the formula of the IPLV.
  • JRAIA Japan Refrigeration and Air Conditioning Industry Association
  • EUROVENT/CECOMAF EUROVENT/CECOMAF
  • IPLV In the case of the Japan Refrigeration and Air Conditioning Industry Association (JRAIA), an IPLV is defined as the following formula.
  • IPLV 0.01 ⁇ A+ 0.47 ⁇ B+ 0.37 ⁇ C+ 0.15 ⁇ D
  • an ESEER is defined as an European seasonal energy efficiency ratio. Like the IPLV, the ESEER is a value obtained by multiplying an energy efficiency ratio of four operation load conditions by a weighting factor, and is calculated by the following formula. For the calculation of the ESEER, an energy efficiency ratio (EER) that is a value representing an energy consumption efficiency is used as in the case of the COP.
  • EER energy efficiency ratio
  • the weight at 75% load and the weight at 50% load are large for various indexes representing the coefficients of performance throughout a year of the refrigerating and air-conditioning apparatus.
  • JRAIA Japan Refrigeration and Air Conditioning Industry Association
  • the small-side Vi value is set to perform efficient operation in partial load operation, and is set to a Vi value with which the value of “0.47 ⁇ B+0.37 ⁇ C+0.15 ⁇ D” is equal to or greater than a set value set in advance.
  • the small-side Vi value is set based on the top three operation loads having large weights in the primary annual performance factor.
  • the value of “0.47 ⁇ B+0.37 ⁇ C+0.15 ⁇ D” is a value that changes depending on the Vi value, and is represented by a graph that projects upward when the horizontal axis represents Vi and the vertical axis represents “0.47 ⁇ B+0.37 ⁇ C+0.15 ⁇ D”. That is, there is a Vi value with which the value of “0.47 ⁇ B+0.37 ⁇ C+0.15 ⁇ D” is the maximum. Based on this, the small-side Vi value may be the Vi value when “0.47 ⁇ B+0.37 ⁇ C+0.15 ⁇ D” is the maximum, or in other words, only has to be a value that is equal to or greater than the set value.
  • the set value only has to be appropriately set depending on performance or another factor required for the screw compressor. For example, when the maximum set value is 100%, the set value may be 95% or more.
  • the Vi value is set as described above.
  • the position when the variable Vi valve 8 is moved to attain the small-side Vi value is set to attain the set Vi value.
  • the small-side Vi value is set as described above and the large-side Vi value is set to a Vi value with which the compressor efficiency is equal to or higher than the set efficiency during operation under the high-load condition or the high-compression-ratio condition, a wide operation range can be secured and the IPLV can be improved.
  • both the rated performance and the IPLV can be improved.
  • the small-side Vi value is set based on the top three operation loads having large weights in the primary annual performance factor. However, as described above, operation at 75% load and operation at 50% load account for the majority of operation period per year. Thus, the small-side Vi value may be set based on the top one or top two operation loads having large weights in the primary annual performance factor.
  • the variable Vi valve is controlled under the simple two-stage control based on only the discharge pressure and the suction pressure.
  • the configuration and control can be simplified without necessity of a special device while the internal volume ratio is made variable.
  • the position of the variable Vi valve when the Vi value is set to be large is set to attain the Vi value with which the compressor efficiency is equal to or higher than the set efficiency during operation under the high-load condition or the high-compression-ratio condition.
  • a wide operation range can be secured.
  • the position of the variable Vi valve when the Vi value is set to be large is set to attain the Vi value with which the rated performance is equal to or higher than the set performance.
  • the rated performance can be improved.
  • the position of the variable Vi valve when the Vi value is set to be small is set to attain the Vi value with which a value obtained by multiplying each of the coefficients of performance at the top one to top three operation loads by the weight corresponding to the operation load is equal to or greater than the set value. This can improve the partial load performance and improve the compressor efficiency.
  • Embodiment 1 provides the configuration in which the pressure introduction hole 113 a of the cylinder chamber 13 a is coupled to the discharge chamber 6 .
  • Embodiment 1 also provides the configuration in which the pressure introduction hole 113 b of the cylinder chamber 13 b is coupled to the discharge chamber 6 in the casing main body 1 through the flow path 15 b via the solenoid valve 14 b , and is coupled to the suction chamber 16 in the casing main body 1 through the flow path 15 c via the solenoid valve 14 a .
  • Embodiment 2 has a configuration in which the pressure introduction hole 113 a is coupled to the discharge chamber 6 in the casing main body 1 through the flow path 15 b via the solenoid valve 14 b , and is coupled to the suction chamber 16 in the casing main body 1 through the flow path 15 c via the solenoid valve 14 a .
  • the pressure introduction hole 113 b is coupled to the suction chamber 16 in the casing main body 1 .
  • the Vi value can be set to two values of a large value and a small value.
  • FIG. 5 is an operation schematic diagram when a Vi value is large in the screw compressor according to Embodiment 2 of the present disclosure.
  • the driving device 10 positions the variable Vi valve 8 in the left direction represented by the arrow in the drawing, thereby delaying the timing at which the discharge port 7 opens.
  • the solenoid valve 14 a when the Vi value is large, the solenoid valve 14 a is closed and the solenoid valve 14 b is opened so that the pressure in the cylinder chamber 13 a is a discharge pressure.
  • the cylinder chamber 13 b is coupled to the suction chamber 16 , and a suction pressure is normally introduced into the cylinder chamber 13 b .
  • the piston 12 is to move in the left direction in the drawing due to the pressure difference in the cylinder chamber 13 .
  • a suction pressure acts on the suction-side end portion 8 g of the valve main body 8 a
  • a discharge pressure immediately after discharge acts on the discharge-port-side end portion 8 d .
  • the same pressure as the pressure acting on the discharge-port-side end portion 8 d acts on the discharge-port-side end portion 8 e of the guide portion 8 b in directions opposite to each other.
  • a discharge pressure acts on the driving-device-side end portion 8 h of the guide portion 8 b.
  • variable Vi valve 8 is to move in the right direction in the drawing due to the pressure difference between the pressure acting on the driving-device-side end portion 8 h and the pressure acting on the suction-side end portion 8 g .
  • the area of each of both end surfaces of the piston 12 in the movement direction is set to be larger than the area of the driving-device-side end portion 8 h of the variable Vi valve 8 , the piston 12 and the variable Vi valve 8 move in the left direction in the drawing due to the pressure difference received in both the areas. Since the variable Vi valve 8 stops at a position at which the piston 12 abuts against the wall surface of the cylinder chamber 13 , the variable Vi valve 8 is accurately positioned at a position at which the Vi value is large.
  • FIG. 6 is an operation schematic diagram when the Vi value is small in the screw compressor according to Embodiment 2 of the present disclosure.
  • the driving device 10 positions the variable Vi valve 8 in the right direction represented by the arrow in the drawing, thereby advancing the timing at which the discharge port 7 opens.
  • the solenoid valve 14 a is opened and the solenoid valve 14 b is closed so that the pressure in the cylinder chamber 13 a is a suction pressure.
  • the cylinder chamber 13 b is coupled to the suction chamber 16 and a suction pressure is normally introduced into the cylinder chamber 13 b , there is no pressure difference in the cylinder chamber 13 .
  • a suction pressure acts on the suction-side end portion 8 g of the valve main body 8 a
  • a discharge pressure immediately after discharge acts on the discharge-port-side end portion 8 d .
  • the same pressure as the pressure acting on the discharge-port-side end portion 8 d acts on the discharge-port-side end portion 8 e of the guide portion 8 b in directions opposite to each other.
  • a discharge pressure acts on the driving-device-side end portion 8 h of the guide portion 8 b.
  • variable Vi valve 8 moves in the right direction in the drawing due to the pressure difference between the discharge pressure acting on the driving-device-side end portion 8 h and the suction pressure acting on the suction-side end portion 8 g . Since the variable Vi valve 8 stops at a position at which the piston 12 abuts against the wall surface of the cylinder chamber 13 , the variable Vi valve 8 is accurately positioned at a position at which the Vi value is small. Alternatively, as illustrated in FIG. 1 , the variable Vi valve 8 may be positioned at a position where the suction-side end portion 8 g of the variable Vi valve 8 abuts against the wall surface of the casing main body 1 .
  • the screw compressor according to the present disclosure is not limited to those illustrated in FIGS. 1 to 6, and may be modified and implemented, for example, as described below within the scope not departing from the gist of the present disclosure.
  • FIG. 7 illustrates a modification of the screw compressor according to any one of Embodiment 1 and Embodiment 2 of the present disclosure.
  • the piston 12 illustrated in FIG. 1 is omitted, and a piston rod 17 is provided.
  • the piston rod 17 is coupled to rods 9 of two variable Vi valves 8 via a common attachment plate 18 , and the one piston rod 17 is provided for the two variable Vi valves 8 .
  • the number of pistons 12 for the variable Vi valves 8 is not limited.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
US17/419,356 2019-03-01 2019-03-01 Screw compressor Pending US20220082099A1 (en)

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WO2023248450A1 (ja) * 2022-06-24 2023-12-28 三菱電機株式会社 スクリュー圧縮機

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JP2013127203A (ja) * 2011-12-16 2013-06-27 Mitsubishi Electric Corp スクリュー圧縮機
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EP3933204A4 (en) 2022-03-09
WO2020178895A1 (ja) 2020-09-10
JPWO2020178895A1 (ja) 2021-09-30
EP3933204A1 (en) 2022-01-05

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