WO2024038656A1 - Compresseur à vis de type à alimentation en liquide - Google Patents

Compresseur à vis de type à alimentation en liquide Download PDF

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Publication number
WO2024038656A1
WO2024038656A1 PCT/JP2023/020259 JP2023020259W WO2024038656A1 WO 2024038656 A1 WO2024038656 A1 WO 2024038656A1 JP 2023020259 W JP2023020259 W JP 2023020259W WO 2024038656 A1 WO2024038656 A1 WO 2024038656A1
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WIPO (PCT)
Prior art keywords
pressure
valve body
working space
coolant
path
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PCT/JP2023/020259
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English (en)
Japanese (ja)
Inventor
茂幸 頼金
健太郎 山本
Original Assignee
株式会社日立産機システム
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Publication of WO2024038656A1 publication Critical patent/WO2024038656A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation

Definitions

  • the present invention relates to a liquid feed type screw compressor.
  • Some screw compressors have a liquid supply system that supplies liquid into the working chamber of the compression stroke for the purpose of sealing the internal gap between the screw rotor and casing, cooling the compressed gas, and lubricating sliding parts.
  • lubricating oil is often used as the liquid.
  • a separator is used to separate the lubricating oil from the compressed gas. The lubricating oil separated by the separator is self-circulated using the pressure difference between the discharge pressure generated by the compressor itself and the pressure in the working space of the compressor body, and is then supplied to the compressor body again (e.g. , see Patent Document 1).
  • a typical screw compressor is connected to customer equipment that uses compressed air via an air tank and various filters.
  • the pressure in the air tank varies depending on the amount of air used, so the screw compressor is controlled to switch between load operation and no-load operation, and to stop the screw compressor, depending on the information obtained from the pressure detection device attached to the compressor. It is common to do so.
  • the pressure at which the motor changes from load operation to no-load operation (hereinafter referred to as the upper limit pressure) and the pressure at which the rotation speed changes from no-load operation to load operation are determined.
  • the air tank is filled with compressed air and control is performed to maintain the pressure.
  • control pressure a preset pressure (hereinafter referred to as control pressure).
  • the air tank is filled with compressed air and controlled to maintain the pressure.
  • Patent Document 1 discloses that an oil-fed screw compressor has a structure that includes a normal oil feed path for the compressor body and another oil feed path provided with a oil feed valve, and reduces power loss by lubricating in consideration of the rated state.
  • a method for suppressing water condensation by supplying oil in consideration of water condensation is disclosed.
  • the temperature of the lubricating oil in the oil tank is measured, and if the temperature of the lubricating oil is higher than a predetermined temperature, the temperature of the lubricating oil is measured, and if the temperature of the lubricating oil is higher than a predetermined temperature, the temperature is Oil is supplied from both oil supply paths located in the high-pressure side working space provided at the On the other hand, if the temperature of the lubricating oil in the oil tank is lower than the specified temperature, the oil supply valve is closed and the oil is supplied only through the oil supply path located in the low-pressure side working space of the compressor body, reducing power loss. At the same time, water condensation is suppressed by lubricating with consideration given to moisture condensation.
  • Patent Document 1 discloses that the amount of oil supplied to the compressor body is adjusted in the rated state to reduce power loss, the amount of oil supplied to the compressor body is adjusted in consideration of the customer's usage condition. The method was not disclosed.
  • a liquid-fed screw compressor includes a compressor main body in which a screw rotor is housed, and a cooling liquid path that separates coolant from discharge gas discharged from the compressor main body and returns it to the compressor main body.
  • a liquid supply type screw compressor that supplies liquid by a pressure difference between the working space pressure of the compressor body and the coolant pressure of the coolant path, the first operation in which the working space pressure is a first pressure.
  • a second valve body position that opens the first supply passage and closes the second supply passage; a second valve body position that opens the first supply passage and the second supply passage; and a second valve body position that opens the first supply passage and the second supply passage; a valve body that can be slid in order to a third valve body position where the first supply passage is closed and the second supply passage is opened; a drive mechanism that slides and drives the valve body by a first biasing force and a second biasing force in a direction from the third valve body position to the first valve body position due to the discharge pressure of the discharged gas.
  • a liquid-fed screw compressor includes a compressor body in which a screw rotor is housed, and a cooling liquid that is separated from discharge gas discharged from the compressor body and returned to the compressor body.
  • a liquid supply type screw compressor which is equipped with a liquid path and supplies liquid by a differential pressure between the working space pressure of the compressor main body and the coolant pressure of the coolant path
  • pressure detection detects the pressure of the discharged gas.
  • a first supply path for supplying the coolant of the coolant path to a first working space where the working space pressure is a first pressure; and a second pressure where the working space pressure is lower than the first pressure.
  • a second supply path that supplies the coolant of the coolant path to a second working space; a first valve body position that opens the first supply path and closes the second supply path; and a first valve body position that opens the first supply path and closes the second supply path; a valve body that is movable between a second valve body position that opens the second supply path; a drive device that moves the valve body; a control device that controls movement of the valve body, and the control device moves the valve body to the first valve body when the coolant pressure based on the detected pressure value is higher than the first pressure. position, and if the coolant pressure based on the detected pressure value is less than or equal to the first pressure and greater than the second pressure, the valve body is moved to the second valve body position.
  • the amount of oil supplied to the compressor body can be appropriately adjusted regardless of the customer's operating pressure, and the reliability of the compressor body can be improved.
  • FIG. 1 is a diagram showing an example of a system diagram of a liquid supply type screw compressor in a first embodiment.
  • FIG. 2 is a diagram showing a switching device for lubricating oil that is circulated and supplied to the compressor main body.
  • FIG. 3 is a PV diagram illustrating the suction process, compression process, and discharge process of the compressor main body.
  • FIG. 4 is an enlarged view of the area in which the switching device of FIG. 2 is provided.
  • FIG. 5 is a diagram showing the sliding position of the refueling switching valve in a state where the discharge pressure is lower than the upper limit value of the discharge pressure.
  • FIG. 6 is a diagram showing a second embodiment of the liquid feed type screw compressor according to the present invention.
  • FIG. 1 is a diagram showing an example of a system diagram of a liquid supply type screw compressor 100 in the first embodiment.
  • a liquid supply type screw compressor water, oil, or the like is used as the liquid to be supplied, and below, a case will be described using lubricating oil as an example of the cooling liquid.
  • the liquid supply type screw compressor 100 will be simply called the compressor 100.
  • the compressor 100 includes a casing that reduces noise generated from the compressor main body 3.
  • Suction gas for example, air
  • the compressor main body 3 is rotationally driven by a main electric motor 4. Electric power is supplied to the main motor 4 from a control device 9 equipped with a compressor control board.
  • the lubricating oil contained in the compressed gas (for example, compressed air) compressed by the compressor main body 3 is separated by an oil separator 5, and then passed through a pressure regulating check valve 6, an aftercooler 7, a dryer (not shown), etc. After passing through, it is stored in a storage tank 10 installed downstream of the compressor.
  • the pressure value of the compressed gas supplied from the compressor 100 is detected by the pressure detection device 11 and displayed on a display section (not shown) provided in the control device 9.
  • the compressed gas stored in the storage tank 10 is used as a gas source for customer equipment.
  • the pressure value detected by the pressure detection device 11 becomes lower than the discharge pressure of the compressor main body 3 due to pressure loss when the compressed gas passes through the oil separator 5 and the aftercooler 7. Operation control of the screw compressor is performed based on the pressure value obtained by the pressure detection device 11.
  • the pressure detection device 11 is installed between the aftercooler 7 and the storage tank 10, but the installation location is not limited to this and can be installed anywhere from the compressor body 3 to the storage tank 10. It's okay.
  • the lubricating oil separated by the oil separator 5 is sent to the oil cooler 8 via the temperature control valve 12 and cooled. Thereafter, after passing through an oil filter (not shown), etc., the oil is returned to the compressor main body 3 through the return pipe 13 of the lubricating oil path, and is supplied to the rotor, bearings, etc. housed inside the compressor main body 3.
  • the temperature control valve 12 controls the amount of lubricating oil that bypasses the oil cooler 8 to keep the temperature of the lubricating oil supplied to the compressor main body 3 constant. In this way, the lubricating oil circulates through the lubricating oil path of the compressor 100.
  • variable speed control In general, there are roughly two types of control methods for the compressor 100.
  • the first type is constant speed control in which the main motor 4 is operated at a constant rotational speed
  • variable speed control in which the main electric motor 4 is operated at a variable rotational speed. Constant speed control is achieved by opening and closing the suction throttle valve 2 and repeating load operation and no-load operation so that the pressure detection value obtained from the pressure detection device 11 is within a preset upper limit pressure and return pressure range. This is a control that maintains pressure.
  • variable speed control is control that adjusts the rotational speed of the main motor 4 connected to the control device 9 so that the pressure value obtained from the pressure detection device 11 becomes a preset control pressure.
  • the rated state is a state in which the compressor main body 3 discharges a specified amount of gas at a specified pressure.
  • the lubricating oil supply position a in the compressor main body 3 where the lubricating oil has returned to the compressor main body 3 through the lubricating oil path is predetermined to be the position where the efficiency is highest in the rated state.
  • FIG. 2 is a diagram showing a switching device 40 for lubricating oil that is circulated and supplied to the compressor main body 3.
  • the switching device 40 is provided integrally with the casing of the compressor main body 3.
  • the compressor 100 of this embodiment is a twin-screw rotor compressor, and the rotor casing 30 includes a female rotor 31 in which a plurality of spiral grooves are formed and a male rotor (not shown).
  • a pair of screw rotors are provided.
  • a pair of screw rotors are arranged along the front and back directions of the page.
  • the female rotor 31 is rotatably supported by bearings 33 and 34 provided in a bearing casing 32 and a bearing 35 provided in the rotor casing 30.
  • the female rotor 31 is rotationally driven by the main electric motor 4 shown in FIG.
  • a suction port 300 is formed in the upper part of the rotor casing 30 in the drawing, and a discharge port 301 is formed in the bearing casing 32.
  • a closed working space is formed by the combination of the female rotor 31 and the male rotor and the rotor casing 30, and as the rotor rotates, the working space moves from the suction side (right side in the figure) to the discharge side (left side in the figure). Moving.
  • suction process a time when the air is connected only to the suction port 300
  • a time when it is connected only to the discharge port 301 There is a continuous time (discharge process), and the process of sucking in, compressing, and expelling gas such as air is performed continuously.
  • a part of the lubricating oil that has returned through the return pipe 13 shown in FIG. 1 is supplied into the rotor casing 30 via the switching device 40.
  • the switching device 40 is formed integrally with the rotor casing 30, but it may be formed separately.
  • a valve body chamber 41 is formed in the switching device 40 .
  • the valve body chamber 41 is provided with a refueling switching valve 42 that slides within the valve body chamber 41 in the left-right direction in the drawing.
  • the valve body chamber 41 is divided into an elastic body chamber 411, an oil passage chamber 412, and a control chamber 413 by the oil supply switching valve 42.
  • An elastic body 43 such as a spring is arranged in the elastic body chamber 411 .
  • the control chamber 413 is supplied with discharged gas from the discharge port 301 through a piping path 46 .
  • the piping route 46 connects the control chamber 413 to the discharge port 301 of the compressor main body 3, but it can be connected anywhere between the compressor main body 3 and the pressure regulating check valve 6. Also good.
  • the elastic body chamber 411 communicates with the surrounding outside air, and the internal pressure is maintained at atmospheric pressure.
  • the refueling switching valve 42 is urged to the right in the drawing by the elastic force of the elastic body 43, and to the left in the drawing by the pressure of the discharged gas from the control chamber 413. Therefore, the refueling switching valve 42 slides left and right depending on the magnitude of the discharge gas pressure.
  • Three working space oil supply paths 45a, 45b, and 45c are formed in the valve body chamber 41 and communicate with mutually different working spaces in the rotor casing 30.
  • a working space oil supply path 45a, a working space oil supply path 45b, and a working space oil supply path 45c are provided in order from the one with the highest working space pressure.
  • FIG. 3 is a PV diagram illustrating the suction process, compression process, and discharge process of the compressor main body 3, where the horizontal axis is the working space volume V, and the vertical axis is the working space pressure P.
  • curve L (ABC1) shows the PV diagram in the rated state
  • curve L (ABD1) shows the PV diagram when the set pressure is lower than the rated state.
  • C1 is a set pressure in the rated state
  • the discharge pressure is controlled to be C1.
  • D1 is the set pressure when the set pressure is lower than the rated state.
  • the compressor 100 will be described as being set between a set pressure C1 and a set pressure D1. Therefore, the pressures C1 and D1 are sometimes referred to as the discharge pressure upper limit value C1 and the discharge pressure lower limit value D1.
  • a lubricating screw compressor that is lubricated by differential pressure is lubricated by self-circulation using the pressure difference between the discharge pressure of the compressor main body 3 and the pressure in the working space that feeds the compressor main body 3 with lubricant.
  • the pressure of the return lubricating oil at the oil supply port a in FIG. 1 (hereinafter referred to as oil supply pressure) is the pressure loss when the lubricating oil passes through the oil separator 5, oil cooler 8, oil filter (not shown), etc.
  • the pressure decreases due to ⁇ P and becomes a pressure value C2, D2 lower than the discharge pressure C1, D1.
  • the working space volumes E and F are volumes corresponding to the oil supply pressures C2 and D2, and indicate the oil supply limit position.
  • the set pressure is set to the discharge pressure upper limit value C1
  • the lubrication possible range of the working space volume in the rated state is section BE
  • the set pressure is set to the discharge pressure lower limit value D1
  • the lubrication possible range is section BF.
  • the oil supply pressure C2 at the discharge pressure upper limit value C1 may be called the oil supply pressure upper limit value
  • the oil supply pressure D2 at the discharge pressure lower limit value D1 may be called the oil supply pressure lower limit value.
  • the oil supply pressure becomes the oil supply pressure lower limit value D2. Therefore, if a refueling position is provided near the refueling limit position of point E in consideration of the best efficiency in the rated state, the working space cannot be refueled in the area EF, and the reliability of the rotor decreases. On the other hand, if the setting pressure is lower than the rated state and the oil supply position is provided in the range of section BF, the amount of lubricating oil supplied will be excessive in the rated state of the delivery pressure C1 and the oil supply pressure D1, which means that the power This causes a problem of loss and reduced performance.
  • FIG. 4 is an enlarged view of the area in which the switching device 40 of FIG. 2 is provided.
  • the working space of the female rotor 31 is schematically shown instead of the rotor tooth shape shown in FIG. Band-shaped regions indicated by symbols 311, 312, and 313 represent operating spaces.
  • the working space oil supply paths 45a, 45b, and 45c communicate with different working spaces 313, 312, and 311, respectively.
  • the pressure of the working space 311 is P1, and the volume is V1.
  • the pressure of the working space 312 is P2 and the volume is V2
  • the pressure of the working space 313 is P3 and the volume is V3.
  • FIG. 4 shows the position of each working space at a certain moment, and as the female rotor 31 rotates over time, the working spaces 311, 312, and 313 move to the left in the figure.
  • the hatched area with the symbol G indicates the gas trapped in the working space, and the working space in which the gas G is trapped moves to the left as the rotor rotates.
  • the gas G When the working space in which the gas G is confined moves to the position indicated by the reference numeral 311 where it communicates with the working space oil supply path 45c, the gas G has a pressure of P1 and a volume of V1.
  • the term "working space 311" refers to the working space that has been moved to a position where it communicates with the working space oil supply path 45c.
  • the gas G when the working space in which the gas G is confined moves to a position called the working space 312, the gas G has a pressure of P2 and a volume of V2, and is in communication with the working space oil supply path 45b.
  • the pressure P3 in the working space 313 is higher than the oil supply pressure D2 when the discharge pressure lower limit value D1 is reached, and the pressures P1 and P2 in the working spaces 311 and 312 are lower than the oil supply pressure D2. That is, the working space oil supply paths 45b, 45c are formed to communicate with the working spaces 312, 311 in the oil supply possible range BF at the oil supply pressure lower limit value D2 when the set pressure is set to the discharge pressure lower limit value D1.
  • the refueling switching valve 42 When the refueling switching valve 42 has the same diameter as the valve body that partitions the valve body chamber 41, the refueling switching valve 42 of the switching device 40 is subjected to a rightward force FR by the elastic body 43 and a gas in the control chamber 413. A leftward force FL due to the pressure acts. The gas pressure in the control chamber 413 is the discharge pressure of the compressor main body 3. Then, the refueling switching valve 42 slides to a position where the force FR and the force FL are balanced. Note that the leftward movement of the refueling switching valve 42 is restricted by a locking portion 44a shown in FIG. 4, and the rightward movement is restricted by a locking portion 44b shown in FIG.
  • the movement range of the refueling switching valve 42 is from the locking portion 44a to the locking portion 44b.
  • the spring constant of the elastic body 43 satisfies FR(44a) ⁇ FL(C1) when the refueling switching valve 42 is in contact with the locking portion 44a, and the refueling switching valve 42 is in contact with the locking portion 44b.
  • the state is set so that FR(44b)>FL(D1) is satisfied. That is, the spring constant of the elastic body 43 is set as FL(C1)>FR(44a)>FR(44b)>FL(D1).
  • FIG. 4 shows the sliding position of the oil supply switching valve 42 when the discharge pressure of the compressor main body 3 is the discharge pressure upper limit value C1.
  • FIG. 5 shows the sliding position of the refueling switching valve 42 in a state where the discharge pressure is lower than the discharge pressure upper limit value C1.
  • the refueling switching valve 42 is in a state where the working space refueling path 45c is about to switch from the closed state to the opening state, as shown in the upper part of FIG.
  • the working space oil supply paths 45a, 45b, and 45c are in an open state, as shown in the middle part of FIG.
  • the working space oil supply path 45a is closed by the oil supply switching valve 42, and the working space oil supply paths 45b and 45c are opened. .
  • the oil supply switching valve 42 moves further to the right in the figure while the working space oil supply paths 45b and 45c remain open, and is stopped by the locking portion 44b.
  • the state will be as follows. Therefore, at the discharge pressure lower limit value D1, which is the oil supply pressure lower limit value D2, the oil supply switching valve 42 is in a state of being locked by the locking portion 44b.
  • the pressure in the working space 313 is the pressure P3 in state H3 in FIG.
  • return lubricating oil is supplied to the working spaces 313, 312 from the working space oil supply paths 45a, 45b.
  • the state is configured to realize the optimum oil supply state in the rated state (discharge pressure C1).
  • discharge pressure C1 discharge pressure
  • the working space to which lubricating oil is supplied is changed as shown in FIG.
  • the switching is made as follows: working spaces 312, 313) ⁇ (working spaces 311, 312, 313) ⁇ (working spaces 311, 312), so that appropriate lubricant oil is supplied according to the discharge pressure.
  • the oil supply switching valve 42 is slid according to the discharge pressure of the compressor body 3 regardless of the customer's usage status, and the oil supply to the compressor body 3 is controlled. It is possible to adjust the amount of oil supplied. Thereby, it is possible to provide an oil-fed screw compressor in which the reliability of the compressor main body 3 is improved.
  • FIG. 6 is a diagram showing a second embodiment of the liquid feed type screw compressor according to the present invention.
  • the driving method of the refueling switching valve 42 in the switching device 40B is different, and the refueling switching valve 42 is slidably driven by the driving device 18 such as a motor. I decided to do so.
  • the drive device 18 is controlled by the control device 9 based on the pressure value related to the discharge pressure detected by the pressure detection device 11.
  • the other configurations are the same as those of the first embodiment described above.
  • the valve body chamber 41 is divided by the oil supply switching valve 42 into an elastic body chamber 411B, an oil passage chamber 412, and a control chamber 413B.
  • the piping route 46 shown in FIG. 2 has been deleted.
  • the elastic body chamber 411B and the control chamber 413B communicate with the oil passage chamber 412, and the elastic body chamber 411B, the oil passage chamber 412, and the control chamber 413B are all at the same pressure.
  • the other configurations are the same as those in the first embodiment, and description thereof will be omitted.
  • the locking portions 44a and 44b may or may not be provided.
  • the pressure detection device 11 is provided to detect the pressure of the compressed gas discharged from the compressor main body 3B, but the pressure is different from the discharge pressure at the discharge port 301 of the compressor main body 3B. A pressure value lower by the pressure loss in the path to the detection device 11 is detected.
  • the control device 9 calculates a value obtained by adding the pressure loss amount to the detected pressure value as a discharge pressure, and controls the sliding drive of the oil supply switching valve 42 by the drive device 18 based on the calculated discharge pressure.
  • the control device 9 positions the refueling switching valve 42 at the position shown in FIG. 4.
  • the discharge pressure is "J1>(discharge pressure)>K1”
  • the refueling switching valve 42 is slid from the position shown in FIG. 4 to the right in the drawing in accordance with the pressure drop.
  • the discharge pressure is J1
  • the arrangement is as shown in FIG. 4
  • the discharge pressure is K1
  • the arrangement is as shown in the lower part of FIG.
  • the oil supply switching valve 42 is slid to a position where the working space oil supply passage 45a is completely closed and the working space oil supply passage 45c is completely opened.
  • the refueling switching valve 42 is moved according to the magnitude of the discharge pressure to switch the working space to be refueled so that the differential pressure for refueling does not become zero or less.
  • the refueling switching valve 42 may be positioned at a position corresponding to the set pressure based on the set pressure by the user.
  • the user inputs set pressure information into the control device 9.
  • the relationship between the set pressure in the control device 9 and the position of the refueling switching valve 42 may be the same as the relationship between the discharge pressure and the slide position described above, or if the set pressure satisfies "C1 ⁇ set pressure ⁇ predetermined value".
  • the open/close state of the working space oil supply paths 45a, 45b, 45c is set as (open, open, closed), and when the set pressure is "predetermined value ⁇ set pressure ⁇ D1", the working space oil supply paths 45a, 45b, 45c
  • the open/close state may be (closed, open, open).
  • oil is used as an example of the liquid to be supplied, but other liquids (for example, water) may be used.
  • other liquids for example, water
  • the left and right valve bodies of the refueling switching valve 42 have the same diameter, they may have different diameters.
  • the oil supply path 45b is configured to always communicate with the working space 312 to supply oil, but it may be omitted as long as the amount of oil supply is sufficient.
  • return lubricating oil is supplied to the twin screw female rotor 31 having male and female screw rotors via the switching devices 40 and 40B, but the male rotor is lubricated.
  • the present invention is not limited to a twin-screw configuration, but can be similarly applied to a liquid-fed screw compressor with a single-screw configuration.
  • the working space oil supply path 45a and the working space oil supply path 45c which communicate with two working spaces with different pressures, are configured to be opened and closed by the oil supply switching valve 42, but three or more It is also possible to adopt a configuration in which opening and closing of the working space oil supply path is switched.
  • the switching devices 40 and 40B are switching valves in which the valve body slides, various configurations are possible without being limited to the sliding type.
  • the liquid supply type screw compressor 100 separates lubricating oil from the compressor body 3 in which the screw rotor is housed and the discharge gas discharged from the compressor body 3.
  • a return pipe 13 that returns to the compressor main body 3 is provided, and oil is supplied by the differential pressure between the working space pressure of the compressor main body 3 and the oil supply pressure.
  • the liquid supply type screw compressor 100 has a working space oil supply path 45a that supplies lubricating oil of the return pipe 13 to the working space 313 where the working space pressure is pressure P3, and a working space oil supply path 45a that supplies the lubricating oil of the return pipe 13 to the working space 313 where the working space pressure is pressure P3.
  • a working space oil supply path 45c that supplies the lubricating oil of the return pipe 13 to the working space 311, which is P1, and a first valve body position that opens the working space oil supply path 45a shown in the upper part of FIG. 5 and closes the working space oil supply path 45c
  • the second valve body position opens the working space oil supply path 45a and the working space oil supply path 45c shown in the middle row of FIG. 5, and the third valve closes the working space oil supply path 45a and opens the working space oil supply path 45c shown in the bottom row of FIG.
  • a valve body chamber 41 that constitutes a drive mechanism that slides and drives the refueling switching valve 42 by the second biasing force FL in the direction from the position to the first valve body position is provided.
  • the oil supply switching valve 42 When the discharge pressure of the discharged gas is equal to or lower than the discharge pressure K1 at which the oil supply pressure becomes the pressure P3 and greater than the discharge pressure P0 at which the oil supply pressure becomes the pressure P1, the oil supply switching valve 42 is moved to the third valve body position ( 5), and if the discharge pressure is higher than the discharge pressure K1 and lower than the predetermined pressure J1 which is higher than the discharge pressure K1, the refueling switching valve 42 is moved to the second valve body position. (See the middle part of FIG. 5), and when the discharge pressure is equal to or higher than the predetermined pressure J1, the refueling switching valve 42 is slid to the first valve body position (see the upper part of FIG. 5).
  • the oil supply switching valve 42 is slid and driven according to the magnitude of the discharge pressure.
  • the working spaces to which lubricating oil is supplied are switched as follows: (working spaces 312, 313) ⁇ (working spaces 311, 312, 313) ⁇ (working spaces 311, 312). This makes it possible to maintain the lubricating oil supply in an appropriate state based on the differential pressure, and it is possible to improve the reliability of the compressor main body 3.
  • the liquid supply type screw compressor 100 separates lubricating oil from the compressor body 3B in which the screw rotor is housed and the discharge gas discharged from the compressor body 3B. and a return pipe 13 for returning the compressor main body 3B to the compressor main body 3B, and oil supply is performed by the differential pressure between the working space pressure of the compressor main body 3B and the oil supply pressure of the return pipe 13.
  • the pressure detection device 11 detects the pressure of discharged gas, the working space oil supply path 45a supplies lubricating oil of the return pipe 13 to the working space 313 whose working space pressure is pressure P3, and the working space oil supply path 45a which supplies lubricating oil of the return pipe 13 to the working space 313 whose working space pressure is pressure P3.
  • a first working space oil supply path 45c that supplies the lubricating oil of the return pipe 13 to the working space 311 whose pressure P1 is lower than
  • the refueling switching valve 42 is movable between the valve body position and the second valve body position shown in the lower part of FIG. 5 where the working space oiling path 45a is closed and the working space oiling path 45c is opened.
  • the control device 9 includes a drive device 18 and a control device 9 that controls movement of the oil supply switching valve 42 by the drive device 18 based on the pressure detection value of the pressure detection device 11. is larger than the pressure P3, the refueling switching valve 42 is moved to the first valve body position, and when the refueling pressure based on the pressure detection value is lower than the pressure P3 and larger than the pressure P1, the refueling switching valve 42 is moved. Move to the second valve body position.
  • the control device 9 controls the control device 9 to set the oil supply pressure based on the pressure detection value to a predetermined oil supply pressure J2 higher than the pressure P3. If it is smaller than , the refueling switching valve 42 is moved to the third valve body position (see the middle part of FIG. 5) where the working space refueling path 45a and the working space refueling path 45c are opened.
  • the configuration (C2) above by providing a third valve body position between the first valve body position and the second valve body position, which opens the working space oil supply path 45a and the working space oil supply path 45c, the supply Sudden changes in the amount of lubricating oil can be suppressed.
  • the working space pressure is higher than the pressure P1 and lower than the pressure P3.
  • the small working space 312 is further provided with a working space oil supply path 45b for supplying lubricating oil to the return pipe 13, so that lubricating oil is always supplied through the working space oiling path 45b regardless of the position of the valve body of the oil supply switching valve 42.
  • piping route 100 ...Liquid supply screw compressor, 300...Suction port, 301...Discharge port, 311-313...Working space, 411, 411B...Elastic body chamber, 412...Oil passage chamber, 413, 413B...Control room

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

Abstract

Dans ce compresseur à vis de type à alimentation en liquide, un mécanisme d'entraînement entraîne de manière coulissante un corps de vanne au moyen : d'une première force de sollicitation due à une force élastique d'un corps élastique dans un sens allant d'une première position de corps de vanne à une troisième position de corps de vanne ; et d'une seconde force de sollicitation due à la pression de refoulement d'un gaz de refoulement dans un sens allant de la troisième position de corps de vanne à la première position de corps de vanne. Le mécanisme d'entraînement : entraîne de manière coulissante le corps de vanne vers la troisième position de corps de vanne lorsqu'une pression de refoulement n'est pas supérieure à une première pression de refoulement si une pression de liquide de refroidissement est égale à une première pression, et est supérieure à une seconde pression de refoulement si la pression de liquide de refroidissement est égale à une seconde pression ; entraîne de manière coulissante le corps de vanne vers une deuxième position de corps de vanne lorsque la pression de refoulement est supérieure à la première pression de refoulement et inférieure à une pression prédéterminée supérieure à la première pression de refoulement ; et entraîne de manière coulissante le corps de vanne vers la première position de corps de vanne lorsque la pression de refoulement est au moins égale à la pression prédéterminée.
PCT/JP2023/020259 2022-08-15 2023-05-31 Compresseur à vis de type à alimentation en liquide WO2024038656A1 (fr)

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JP2022-129445 2022-08-15
JP2022129445A JP2024026012A (ja) 2022-08-15 2022-08-15 給液式スクリュー圧縮機

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120207634A1 (en) * 2011-02-10 2012-08-16 Joseph Heger Lubricant control valve for a screw compressor
JP2018021494A (ja) * 2016-08-03 2018-02-08 株式会社日立製作所 スクリュー流体機械

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120207634A1 (en) * 2011-02-10 2012-08-16 Joseph Heger Lubricant control valve for a screw compressor
JP2018021494A (ja) * 2016-08-03 2018-02-08 株式会社日立製作所 スクリュー流体機械

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