EP3421800B1 - Screw compressor and refrigeration cycle device - Google Patents

Screw compressor and refrigeration cycle device Download PDF

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Publication number
EP3421800B1
EP3421800B1 EP16891410.9A EP16891410A EP3421800B1 EP 3421800 B1 EP3421800 B1 EP 3421800B1 EP 16891410 A EP16891410 A EP 16891410A EP 3421800 B1 EP3421800 B1 EP 3421800B1
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EP
European Patent Office
Prior art keywords
discharge port
port valve
stepped shape
discharge
screw compressor
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EP16891410.9A
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German (de)
English (en)
French (fr)
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EP3421800A1 (en
EP3421800A4 (en
Inventor
Masahiro Kanda
Masaaki Kamikawa
Hideaki Nagata
Mihoko Shimoji
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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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
    • 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
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves

Definitions

  • the present invention relates to a screw compressor and a refrigeration cycle apparatus that do not require complex control.
  • variable inner volume ratio valve which is a slide valve adjusting a timing of starting discharge to make an inner volume ratio Vi adjustable, to thereby adjust an opening degree of the variable inner volume ratio valve by a driving force from a driving device in accordance with an operating pressure ratio (for example, refer to Patent Literature 1).
  • a conventional variable inner volume ratio valve used for the screw compressor is controlled as shown in Fig. 1 and Fig. 2 of Patent Literature 1. Specifically, upon calculating an optimum inner volume ratio value from a discharge pressure HP and a suction pressure LP and obtaining a current inner volume ratio value from a position detection unit, the variable inner volume ratio valve is controlled by a driving device coupled to the variable inner volume ratio valve so that a difference between the current inner volume ratio value and the optimum inner volume ratio value will be decreased. Further, to bring the current inner volume ratio value close to the optimum inner volume ratio value in actual operation, the opening degree of the variable inner volume ratio valve is adjusted to minimize a motor driving power.
  • the inner volume ratio Vi in the screw compressor is, for example, as disclosed in Patent Literature 2, a ratio between a tooth groove space volume in sucking and a tooth groove space volume just before discharging, and represents a ratio between a volume when suction is completed and a volume when a discharge port is opened.
  • a discharge-side edge part of the discharge port valve facing an outer circumference of a screw rotor is formed into a corner-portion shape without steps in which an axial direction plane of a rotation shaft of the screw rotor and an orthogonal plane thereof are bent. Consequently, the minimum area of refrigerant flow in the discharge outlet, in which the refrigerant actually flows, becomes the size between the land part of the screw rotor and the discharge-side edge part of the discharge port valve.
  • the minimum area of refrigerant flow in the discharge outlet, in which the refrigerant actually flows is automatically determined to be broadened in accordance with the time course with rotation of the screw rotor.
  • the inner volume ratio Vi is adapted to a low-load operation with a low compression ratio and a low flow rate that occupies the large part of operation time of an air-conditioning device per year, in a high-load operation with a high compression ratio and a high flow rate, a discharge outlet is opened at a discharge port before reaching the discharge pressure. Further, since the minimum area of refrigerant flow in the discharge outlet after opening is large, a large amount of refrigerant gas flows back into a compression chamber, and thereby improper compression loss is generated.
  • the refrigerant gas is excessively compressed beyond the high-pressure side pressure until the discharge outlet is opened in the discharge port and the improper compression loss is increased by over compression, to thereby result in deterioration of efficiency throughout the year.
  • JP 2014 029133 A discloses a screw compressor including a slidable valve for making an internal volume ratio of a screw rotor variable, and a casing body internally divided into a discharge pressure space and a suction pressure space with a partition wall formed in opposition to a back side of the valve body of the valve.
  • a discharge port end portion of the valve body has a notch at an inner side so that a back side is projected with respect to the inner side, the valve body and a guide portion of the valve have projecting portions at their back sides, and a connecting portion of the valve connects the discharge port end portion of the valve body and the guide portion in an area including the projecting portions of the valve body and the guide portion.
  • the present invention has been made to solve the above problem, and has an object to obtain a highly efficient screw compressor and a refrigeration cycle apparatus simplifying control of a discharge port valve.
  • a screw compressor includes: a casing body having a hollow part; a screw rotor rotating around a rotation shaft in the hollow part of the casing body; a semi-cylindrical groove formed on an outer side in a radial direction of the hollow part of the casing body and extending in a direction of the rotation shaft of the screw rotor; and a discharge port valve contained in the semi-cylindrical groove, wherein an edge part of the discharge port valve, in which a discharge outlet facing an outer circumference of the screw rotor is opened, is formed into a stepped shape changing a flow path area of a discharge flow path in a stepwise manner.
  • the stepped shape includes a single step and end surface inclination of the stepped shape is formed by optimization in two conditions having a large weight of an integrated part load value IPLV, or the stepped shape includes two steps and end surface inclination of the stepped shape is formed by optimization in three conditions having a large weight of an integrated part load value IPLV, or the stepped shape includes three steps and end surface inclination of the stepped shape is formed by optimization in four conditions with which an integrated part load value IPLV is calculated.
  • a refrigeration cycle apparatus includes the above-described screw compressor.
  • an edge part of a discharge port valve in which a discharge outlet facing an outer circumference of a screw rotor was opened, was formed into a stepped shape changing a flow path area of a discharge flow path in a stepwise manner. Therefore, the minimum area of refrigerant flow in the discharge outlet, in which the refrigerant actually flows, can be adjusted between a land part of the screw rotor and the edge part of the discharge port valve formed into the stepped shape corresponding to the time course with rotation of the screw rotor.
  • Fig. 1 is a schematic configuration view of a screw compressor 100 according to Embodiment 1 of the present invention. By use of Fig. 1 , a schematic configuration of the screw compressor 100 will be described.
  • the screw compressor 100 according to Embodiment 1 is a single-screw compressor.
  • the screw compressor 100 is used in a refrigeration cycle apparatus expected to operate in a wide range of compression ratio of, for example, an air-conditioning apparatus, a refrigeration device, a water heater and the like.
  • the screw compressor 100 includes a cylindrical casing body 1 having a hollow part 1a inside thereof; and a screw rotor 2 contained in the hollow part 1a in the casing body 1.
  • a motor 3 for rotationally driving the screw rotor 2 is included.
  • the motor 3 is configured with a stator 3a fixed to the casing body 1 and a motor rotor 3b disposed inside the stator 3a with a gap.
  • the rotation speed of the motor 3 is controlled by an inverter system, which is not shown.
  • the screw rotor 2 and the motor rotor 3b are mutually disposed on a same shaft line of the rotation shaft, and both of them are fixed to a screw shaft 4.
  • the screw rotor 2 is coupled to the motor rotor 3b fixed to the screw shaft 4, to be rotationally driven.
  • a compression chamber 6 of the screw compressor 100 is formed by the multiple screw grooves 5 in the spiral shape, an inner cylinder surface forming the hollow part 1a of the casing body 1, the screw rotor 2 and a pair of gate rotors 7 having multiple teeth engaged with the screw rotor 2.
  • a discharge pressure side and a suction pressure side are divided by a dividing wall, which is not-shown.
  • the container groove 11 corresponds to a semi-cylindrical groove of the present invention.
  • the discharge port valve 10 forming part of the discharge outlet 9 and the discharge flow path 8 is provided.
  • the discharge port valve 10 is fixed inside the container groove 11.
  • the container groove 11 is opened on the left side of the figure to be closed by a lid material 12 on the left end part, in the figure, of the screw compressor 100.
  • the opening of the container groove 11 is to insert the discharge port valve 10 into the container groove 11.
  • a member 10a provided with a function of suppressing rotation of the discharge port valve 10 and a member 10b forming part of the discharge outlet 9 are integrated by providing a rod-shaped coupling part 10c therebetween.
  • the shape of the discharge port valve 10 is as shown in Figs. 9 to 14 in the embodiments to be described later.
  • An edge part of the discharge port valve 10, in which the discharge outlet 9 facing an outer circumference of the screw rotor 2 is opened, is formed into a stepped shape 13 changing a flow path area of the discharge flow path 8 in a stepwise manner.
  • the stepped shape 13 is formed in the edge part, in which the discharge outlet 9 is opened, of the member 10b forming part of the discharge outlet 9 on the suction pressure side in the direction of rotation shaft.
  • the stepped shape 13 includes a single step or multiple steps; here, the stepped shape 13 is assumed to include N steps.
  • the stepped shape 13 is formed only in the edge part, in which the discharge outlet 9 is opened, of the member 10b forming part of the discharge outlet 9.
  • the stepped shape 13 narrows the flow path width of the discharge flow path 8 in the rotation shaft direction in a stepwise manner from the discharge outlet 9 toward the outer side in the radial direction on the downstream side of the discharge flow path 8.
  • the stepped shape 13 narrows the flow path area of the discharge flow path 8 in a stepwise manner from the member 10a provided with a function of suppressing rotation of the discharge port valve 10 toward the rotation shaft side on the upstream side of the discharge flow path 8.
  • the discharge port valve 10 forms the outside of the radial direction on the downstream side of the discharge flow path 8 in the stepped shape 13 narrowing the flow path area of the discharge flow path 8 in the stepwise manner on one end surface 10d on the side of the coupling part, and reduces the thickness of the member 10a provided with the function of suppressing rotation of the discharge port valve 10, to thereby broaden the flow path area of the discharge flow path 8.
  • the discharge port valve 10 once narrows down the flow path area of the discharge flow path 8 from the discharge outlet 9, and thereafter enlarges thereof.
  • Fig. 2A is a diagram illustrating a suction process included in the compression principles of the screw compressor 100 according to Embodiment 1 of the present invention.
  • Fig. 2B is a diagram illustrating a compression process included in the compression principles of the screw compressor 100 according to Embodiment 1 of the present invention.
  • Fig. 2C is a diagram illustrating a discharge process included in the compression principles of the screw compressor 100 according to Embodiment 1 of the present invention.
  • Fig. 2A shows a state of the compression chamber 6 in the suction process.
  • the screw rotor 2 is driven by the motor 3 to be rotated in the direction of the solid-line arrow. This reduces the volume of the compression chamber 6 as shown in Fig. 2B , and thereby the compression process is performed.
  • Fig. 3A is a PV diagram illustrating a case of insufficient compression included in improper compression according to Embodiment 1 of the present invention.
  • Fig. 3B is a PV diagram illustrating a case of insufficient compression included in conventional improper compression.
  • Fig. 4A is a PV diagram illustrating a case of over compression included in the improper compression according to Embodiment 1 of the present invention.
  • Fig. 4B is a PV diagram illustrating a case of over compression included in the conventional improper compression.
  • Fig. 5A is a diagram illustrating a minimum area S of the refrigerant flow in the discharge outlet 9 at a start of opening thereof in the screw compressor 100 according to Embodiment 1 of the present invention.
  • Fig. 5A is a diagram illustrating a minimum area S of the refrigerant flow in the discharge outlet 9 at a start of opening thereof in the screw compressor 100 according to Embodiment 1 of the present invention.
  • Fig. 5A is a diagram illustrating a minimum area S of the
  • FIG. 5B is a diagram illustrating the minimum area S of the refrigerant flow in the discharge outlet 9 partway through opening thereof in the screw compressor 100 according to Embodiment 1 of the present invention.
  • Fig. 5C is a diagram illustrating the minimum area S of the refrigerant flow in the discharge outlet 9 close to maximum opening thereof in the screw compressor 100 according to Embodiment 1 of the present invention.
  • Fig. 6 is a diagram illustrating a relationship between a screw rotation angle of the screw compressor 100 and the minimum area S of the refrigerant flow according to Embodiment 1 of the present invention.
  • Fig. 7A is a diagram illustrating a minimum area S of the refrigerant flow in a discharge outlet at a start of opening thereof in a conventional screw compressor.
  • FIG. 7B is a diagram illustrating the minimum area S of the refrigerant flow in the discharge outlet partway through opening thereof in the conventional screw compressor.
  • Fig. 7C is a diagram illustrating the minimum area S of the refrigerant flow in the discharge outlet close to maximum opening thereof in the conventional screw compressor.
  • Fig. 8 is a diagram illustrating a relationship between a screw rotation angle of the conventional screw compressor and the minimum area S of the refrigerant flow.
  • the compression chamber is communicated to the discharge outlet before the refrigerant gas pressure in the compression chamber reaches a high pressure Pd.
  • the minimum area S of the refrigerant flow in the discharge outlet in which the refrigerant actually flows, is automatically determined to be broadened in accordance with the time course with rotation of the screw rotor.
  • the minimum area S of the refrigerant flow is broadened from the start of opening corresponding to the screw rotation angle. Therefore, as shown in Fig. 7A , the discharge outlet is opened in the discharge port before reaching the discharge pressure. Further, as shown in Fig.
  • the minimum area S of the refrigerant flow in the discharge outlet after opening is large. Consequently, the refrigerant gas in the discharge flow path flows from the discharge outlet back into the compression chamber, to thereby result in a pattern of conventional compression P2 in which the pressure is sharply increased as compared to a pattern of ideal compression Pid. Consequently, increase in power by the area of the shaded portion results in a loss as insufficient compression loss.
  • the minimum area S of the refrigerant flow in the discharge outlet 9, in which the refrigerant actually flows can be adjusted to be narrowed, not to be broadened, at the start of opening between the land part 2a of the screw rotor 2 and the edge part of the discharge port valve 10 formed into the stepped shape 13 corresponding to the time course with rotation of the screw rotor 2.
  • the adjustment portion in which the minimum area S of the refrigerant flow is adjusted not to be broadened at the start of opening is the portion A in the bumped shape of a single stage shown in Fig. 6 .
  • Embodiment 1 in the operation conditions of a low operation load factor with a low compression ratio and a low frequency, the compression results in a pattern of performed compression P3 shown in Fig. 4A due to a small refrigerant circulation amount, thereby the power loss by the area of the shaded portion is improved, and it is possible to keep the effect of discharge pressure loss to be small, and to keep the effect of increase in power to be small.
  • the edge part of the discharge port valve 10, in which the discharge outlet 9 is opened is formed into the stepped shape 13 of N steps.
  • the stepped shape 13 makes it difficult to broaden the minimum area S of the refrigerant flow in the discharge outlet 9, in which the refrigerant actually flows, immediately after the screw grooves 5 are communicated to the discharge outlet 9. Then, thereafter, the minimum area S of the refrigerant flow is broadened with the movement of the screw grooves 5 toward the discharge side.
  • Embodiment 1 it is possible to form the minimum area S of the refrigerant flow in the discharge outlet 9, in which the refrigerant actually flows, corresponding to wide operating pressure ratio without sliding the discharge port valve 10, and thereby the high-performance screw compressor 100 in the wide operation range can be obtained.
  • variable inner volume ratio mechanism and control for causing the discharge port valve 10 to serve as the variable inner volume ratio valve are unnecessary, a compact and inexpensive screw compressor 100 can be obtained.
  • Embodiment 1 the number of steps in the stepped shape 13 was assumed to be N steps including a single step and multiple steps.
  • Fig. 9 is a schematic view illustrating a discharge port valve 10 according to Embodiment 2 of the present invention.
  • Fig. 10 is an illustration diagram illustrating a cross section A-A of the discharge port valve 10 shown in Fig. 9 according to Embodiment 2 of the present invention.
  • a member 10a provided with a function of suppressing rotation of the discharge port valve 10 and a member 10b forming part of the discharge outlet 9 are integrated by providing a rod-shaped coupling part 10c therebetween.
  • the discharge port valve 10 is formed on the outer side in the radial direction of the hollow part 1a of the casing body 1 and contained in the semi-cylindrical container groove 11 extending in the direction of the rotation shaft of the screw rotor 2, and fixed thereto.
  • the edge part of the discharge port valve 10, in which the discharge outlet 9 facing an outer circumference of the screw rotor 2 is opened, is formed into a stepped shape 13 with a single step shifting the position thereof toward the outer side in the radial direction on the downstream side of the discharge flow path 8.
  • the stepped shape 13 with a single step refers to a shape having a step end surface 10e of a single step and two surfaces 10f arranged in line along the outer circumference of the screw rotor 2.
  • IPLV is a coefficient of performance of a refrigeration cycle apparatus during a period.
  • the coefficient of performance differs in response to the load in operation; moreover, the time with the load of 75% occupies 42% of the annual operation time and the time with the load of 50% occupies 45% of the annual operation time, and therefore, the weight is larger in these two conditions.
  • IPLV 0.01 ⁇ A + 0.47 ⁇ B + 0.37 ⁇ C + 0.15 ⁇ D , where
  • the weight is different in each operation load factor.
  • the time with the load of 75% occupies 47% of the annual operation time and the time with the load of 50% occupies 37% of the annual operation time, and therefore, the weight is larger in these two conditions.
  • one step end surface 10e of the stepped shape 13 and one end surface 10d closer to the coupling part 10c in the discharge port valve 10 are formed with end surface inclination optimized in the two conditions having a large weight of the integrated part load value IPLV.
  • two end surface inclinations are formed by optimization in the two conditions B and C having a large weight of the integrated part load value IPLV.
  • the end surface inclination is formed into a curved surface shape corresponding to a discharge side end of the land in the screw rotor, which the discharge port valve, not in the conventional stepped shape, in the two conditions B and C in the sliding position faces.
  • the screw compressor 100 having high integrated part load value IPLV. Moreover, since the discharge port valve 10 does not require a mechanism for serving as the variable inner volume ratio valve and control, the screw compressor 100, which is more compact and less expensive than a conventional one, can be obtained.
  • Fig. 11 is a schematic view illustrating the discharge port valve 10 according to Embodiment 3 of the present invention.
  • Fig. 12 is an illustration diagram illustrating a cross section B-B of the discharge port valve 10 shown in Fig. 11 according to Embodiment 3 of the present invention.
  • a member 10a provided with a function of suppressing rotation of the discharge port valve 10 and a member 10b forming part of the discharge outlet 9 are integrated by providing a rod-shaped coupling part 10c therebetween.
  • the discharge port valve 10 is formed on the outer side in the radial direction of the hollow part 1a of the casing body 1 and contained in the semi-cylindrical container groove 11 extending in the direction of the rotation shaft of the screw rotor 2, and fixed thereto.
  • the edge part of the discharge port valve 10, in which the discharge outlet 9 facing an outer circumference of the screw rotor 2 is opened, is formed into a stepped shape 13 with two steps shifting the position thereof toward the outer side in the radial direction on the downstream side of the discharge flow path 8.
  • the stepped shape 13 with two steps refers to a shape having a step end surface 10e of two steps and three surfaces 10f arranged in line along the outer circumference of the screw rotor 2.
  • three end surface inclinations are formed by optimization in the three conditions B, C and D having a large weight of the integrated part load value IPLV.
  • the end surface inclination is formed into a curved surface shape corresponding to a discharge side end of the land in the screw rotor, which the discharge port valve, not in the conventional stepped shape, in the three conditions B, C and D in the sliding position faces.
  • the screw compressor 100 having higher integrated part load value IPLV than Embodiment 2. Moreover, since the discharge port valve 10 does not require a mechanism for serving as the variable inner volume ratio valve and control, the screw compressor 100, which is more compact and less expensive than a conventional one, can be obtained.
  • Fig. 13 is a schematic view illustrating the discharge port valve 10 according to Embodiment 4 of the present invention.
  • Fig. 14 is an illustration diagram illustrating a cross section C-C of the discharge port valve 10 shown in Fig. 13 according to Embodiment 4 of the present invention.
  • a member 10a provided with a function of suppressing rotation of the discharge port valve 10 and a member 10b forming part of the discharge outlet 9 are integrated by providing a rod-shaped coupling part 10c therebetween.
  • the discharge port valve 10 is formed on the outer side in the radial direction of the hollow part 1a of the casing body 1 and contained in the semi-cylindrical container groove 11 extending in the direction of the rotation shaft of the screw rotor 2, and fixed thereto.
  • the edge part of the discharge port valve 10, in which the discharge outlet 9 facing an outer circumference of the screw rotor 2 is opened, is formed into a stepped shape 13 with three steps shifting the position thereof toward the outer side in the radial direction on the downstream side of the discharge flow path 8.
  • the stepped shape 13 with three steps refers to a shape having a step end surface 10e of three steps and four surfaces 10f arranged in line along the outer circumference of the screw rotor 2.
  • Embodiment 4 three step end surfaces 10e of the stepped shape 13 and one end surface 10d closer to the coupling part 10c in the discharge port valve 10 are formed with end surface inclination optimized in four conditions A, B, C and D of the integrated part load value IPLV.
  • the end surface inclination is formed into a curved surface shape corresponding to a discharge side end of the land in the screw rotor, which the discharge port valve, not in the conventional stepped shape, in the four conditions A, B, C and D in the sliding position faces.
  • the screw compressor 100 having higher integrated part load value IPLV than Embodiment 3. Moreover, since the discharge port valve 10 does not require a mechanism for serving as the variable inner volume ratio valve and control, the screw compressor 100, which is more compact and less expensive than a conventional one, can be obtained.
  • Fig. 15 is a refrigerant circuit diagram illustrating a refrigeration cycle apparatus 200 to which the screw compressor 100 according to Embodiment 5 of the present invention is applied.
  • the refrigeration cycle apparatus 200 includes the screw compressor 100, a condenser 80, an expansion valve 81 and an evaporator 82. These screw compressor 100, condenser 80, expansion valve 81 and evaporator 82 are connected via the refrigerant pipe to form the refrigeration cycle circuit. The refrigerant flowing out of the evaporator 82 is sucked into the screw compressor 100 to have high temperature and high pressure. The refrigerant that became high temperature and high pressure is condensed in the condenser 80 to become liquid.
  • the refrigerant that became liquid is subjected to pressure reduction and expansion by the expansion valve 81 to enter a two-phase gas-liquid state of low temperature and low pressure, and thereby the two-phase gas-liquid refrigerant is subjected to heat exchange in the evaporator 82.
  • the screw compressors 100 in the Embodiments 1 to 4 can be applied to such a refrigeration cycle apparatus 200.
  • the refrigeration cycle apparatus 200 include an air-conditioning apparatus, a refrigeration device, a water heater and the like.
  • the screw compressor 100 includes the casing body 1 having the hollow part 1a.
  • the screw compressor 100 also includes the screw rotor 2 rotating around the rotation shaft in the hollow part 1a of the casing body 1.
  • the screw compressor 100 also includes a semi-cylindrical container groove 11 formed on the outer side in the radial direction of the hollow part 1a of the casing body 1 and extending in the direction of the rotation shaft of the screw rotor 2.
  • the screw compressor 100 also includes the discharge port valve 10 contained in the container groove 11.
  • the edge part of the discharge port valve 10, in which the discharge outlet 9 facing an outer circumference of the screw rotor 2 is opened, is formed into a stepped shape 13 changing a flow path area of the discharge flow path 8 in a stepwise manner.
  • the edge part of the discharge port valve 10, in which the discharge outlet 9 facing an outer circumference of the screw rotor 2 is opened, is formed into a stepped shape 13 changing a flow path area of the discharge flow path 8 in a stepwise manner. Therefore, the minimum area S of refrigerant flow in the discharge outlet 9, in which the refrigerant actually flows, can be adjusted between a land part 2a of the screw rotor 2 and the edge part of the discharge port valve 10 formed into the stepped shape 13 corresponding to the time course with the rotation of the screw rotor 2.
  • a member 10a provided with a function of suppressing rotation of the discharge port valve 10 and a member 10b forming part of the discharge outlet 9 are integrated by providing a rod-shaped coupling part 10c therebetween.
  • the stepped shape 13 is formed in the edge part, in which the discharge outlet 9 is opened, of the member 10b forming part of the discharge outlet 9.
  • the discharge port valve 10 is fixed.
  • variable inner volume ratio mechanism and control for causing the discharge port valve 10 to serve as the variable inner volume ratio valve are unnecessary, a compact and inexpensive screw compressor 100 can be obtained.
  • the stepped shape 13 includes a single step and end surface inclination of the stepped shape 13 is formed by optimization in two conditions having a large weight of the integrated part load value IPLV.
  • the stepped shape 13 includes two steps and end surface inclination of the stepped shape 13 is formed by optimization in three conditions having a large weight of the integrated part load value IPLV.
  • the stepped shape 13 includes three steps and end surface inclination of the stepped shape 13 is formed by optimization in four conditions having a large weight of the integrated part load value IPLV.
  • the refrigeration cycle apparatus 200 includes the screw compressor 100.
  • the discharge port valve 10 was fixed inside the container groove 11.
  • the discharge port valve 10 may be driven by control in which, for example, the drive patterns are simplified into only two patterns or others. Even in such a case, it is possible to improve the improper compression loss by simplifying the control.
  • the above-described stepped shape 13 may be applied to a slide valve capable of adjusting the compression capacity.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP16891410.9A 2016-02-23 2016-02-23 Screw compressor and refrigeration cycle device Active EP3421800B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2016/055145 WO2017145251A1 (ja) 2016-02-23 2016-02-23 スクリュー圧縮機および冷凍サイクル装置

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EP3421800A1 EP3421800A1 (en) 2019-01-02
EP3421800A4 EP3421800A4 (en) 2019-01-02
EP3421800B1 true EP3421800B1 (en) 2020-03-25

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WO2019220562A1 (ja) * 2018-05-16 2019-11-21 三菱電機株式会社 スクリュー圧縮機
GB2581526A (en) * 2019-02-22 2020-08-26 J & E Hall Ltd Single screw compressor
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WO2017145251A1 (ja) 2017-08-31
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