WO2015010260A1 - Compresseur rotatif et appareil de circulation frigorifique pourvu de ce compresseur - Google Patents

Compresseur rotatif et appareil de circulation frigorifique pourvu de ce compresseur Download PDF

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Publication number
WO2015010260A1
WO2015010260A1 PCT/CN2013/079932 CN2013079932W WO2015010260A1 WO 2015010260 A1 WO2015010260 A1 WO 2015010260A1 CN 2013079932 W CN2013079932 W CN 2013079932W WO 2015010260 A1 WO2015010260 A1 WO 2015010260A1
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WO
WIPO (PCT)
Prior art keywords
winding
oil
motor
rotary compressor
winding cover
Prior art date
Application number
PCT/CN2013/079932
Other languages
English (en)
Chinese (zh)
Inventor
小津政雄
梁自强
王玲
Original Assignee
广东美芝制冷设备有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 广东美芝制冷设备有限公司 filed Critical 广东美芝制冷设备有限公司
Priority to PCT/CN2013/079932 priority Critical patent/WO2015010260A1/fr
Publication of WO2015010260A1 publication Critical patent/WO2015010260A1/fr

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Classifications

    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F04C28/28—Safety arrangements; Monitoring
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/81—Sensor, e.g. electronic sensor for control or monitoring
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/19—Temperature
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/20—Flow
    • F04C2270/205—Controlled or regulated

Definitions

  • the present invention relates to a rotary compressor for a rotary compressor, a scroll compressor, a vane compressor, and the like which are applied to an air conditioner, a freezing machine, a water heater, etc., and a high pressure side, and includes The refrigeration cycle device of the rotary compressor. Background technique
  • the internal pressure of the seal case is used as the high pressure side for the purpose of improving the compression efficiency, the lubrication of the sliding parts, and the miniaturization of the casing volume by direct suction of the refrigerant.
  • the crankshaft rotation axis is set to the vertical direction, and the so-called vertical type is often used.
  • the vertical rotary compressor has the following problems:
  • the amount of oil discharged is significantly increased due to the inhalation of a large amount of liquid refrigerant, and the oil level is also lowered.
  • the amount of oil discharged during startup will increase significantly due to the "deposition of refrigerant" in the casing.
  • oil overheating phenomenon occurs during operation, the viscosity of the oil will be significantly reduced due to the dilution of the refrigerant after condensation in the oil. This phenomenon is the main cause of wear failure of the compressor.
  • the performance of the heat exchanger is lowered due to the amount of oil discharged beyond the limit.
  • the internal pressure of the casing is an essential subject in the rotary compressor of the high pressure side.
  • a technique such as temperature control and rotational speed control of a refrigeration cycle apparatus including a compressor is being introduced, but the countermeasure effect is not insufficient enough, and the efficiency of the apparatus is also sacrificed. Therefore, it is necessary to study the fundamental solution of the compressor body. Summary of the invention
  • an object of the present invention is to provide a rotary compressor having a low fuel discharge amount and high reliability.
  • Another object of the present invention is to provide a refrigeration cycle apparatus having the rotary compressor.
  • a rotary compressor comprising: a sealed casing provided with an exhaust pipe, a lower portion of the casing has an oil storage chamber in which lubricating oil is stored; a motor, the motor is provided In the housing, the The motor includes a stator having a motor winding and a rotor sleeved inside the stator, a gap between the outer peripheral wall of the stator and an inner wall of the housing, and an oil separation chamber above the motor in the housing; a compression device, the compression device being disposed on a lower side of the motor and including a crankshaft, a main bearing, a sub-bearing, and a cylinder between the main bearing and the sub-bearing, the main bearing, the sub-bearing, and the cylinder Defining a compression chamber; a winding cover, the winding cover is disposed between the stator and the compression device, and the winding cover surrounds a lower end of the motor winding, wherein the oil discharged
  • the oil reservoir F includes a gap between the outer circumference of the winding cover and the casing, the capacity of the oil reservoir F is sufficient.
  • rotary compressor according to the present invention has the following additional technical features:
  • the exhaust pipe is connected to the housing at the oil separation chamber or the oil passage.
  • the oil passage is defined by an outer side of the winding cover, a gap between the stator and the housing.
  • the oil passage is constituted by a pipe provided outside the casing, and both ends of the pipe are connected to the oil reservoir and the oil separation chamber, respectively.
  • the winding cover includes: a first column segment, an upper end of the first column segment is sleeved outside the stator; a second column segment, the second column segment is disposed at Below the first column segment, and the inner diameter of the second column segment is smaller than the inner diameter of the first column segment, and the second column segment is sleeved outside the upper end of the main bearing of the compression device And a connecting section, the connecting section has an inverted truncated cone and is connected between the first column section and the second column section.
  • a plurality of core cuts are formed on an outer peripheral wall of the stator, and each of the core cuts is formed by cutting a part of an outer circumference of the stator, and the plurality of core cuts are penetrated In the axial direction of the stator, the outer peripheral wall of the stator forms the gap between the core cutout and the inner wall of the housing.
  • a plurality of the core cutouts of the stator are respectively recessed inwardly to form a core slot, the core slot extending through an axial direction of the stator; a plurality of protrusions extending upward from an outer side of the upper end of the first column segment, the number of the protrusions being less than the number of the core slots, each of the protrusions being embedded in a lower end of the corresponding core slot to cover the winding The upper end is mated with the stator.
  • the lower end of the second column segment of the winding cover extends outwardly from the flange; the rotary compressor further includes a spring, and the two ends of the spring respectively abut against the lower surface of the flange and The upper surface of the cylinder is such that the upper end surface of the first column segment abuts against the lower surface of the stator.
  • the core cut includes four and is evenly distributed in the circumferential direction, and the protrusions are opposite ones.
  • the rotary compressor further includes: an auxiliary winding cover, the auxiliary winding cover is disposed above the motor and surrounds an upper end of the motor winding, and a peripheral wall of the auxiliary winding cover There are a plurality of outer peripheral holes, and a vent hole is formed in the center.
  • the auxiliary winding cover is formed as an inverted buckle-shaped structure, and the lower end of the auxiliary winding cover extends downwardly from the two auxiliary protrusions, and the two auxiliary protrusions are embedded in the corresponding iron
  • the upper end of the core groove is adapted to engage the lower end of the auxiliary winding cover with the stator.
  • the housing includes: an upper casing, the upper casing is connected to the exhaust pipe, and a lower surface of the upper casing is provided with a coil spring disposed in an up and down direction; a lower casing, a The lower case is connected below the upper case, wherein the motor, the compression device, the winding cover and the auxiliary winding cover are both disposed in the lower case, wherein the coil spring The lower end is abutted on the upper surface of the auxiliary winding cover and has a position corresponding to the exhaust hole.
  • the upper end of the crankshaft is provided with a circular plate disposed coaxially therewith.
  • the upper side wall of the winding cover is provided with a bypass hole therethrough.
  • the winding cover is further provided with a differential pressure valve, and the differential pressure valve is disposed corresponding to the bypass hole to open or close the bypass hole according to a pressure difference between the inner side and the outer side of the winding cover.
  • the differential pressure valve is a reed valve and includes a main valve and an auxiliary valve fixed to an outer sidewall of the winding cover.
  • the motor uses a variable frequency motor in which the motor winding is a concentrated winding method.
  • the rotary compressor further includes: an exhaust muffler between the motor and the main bearing, the exhaust muffler having a muffler exhaust port, the muffling The exhaust port is sleeved on the hub of the main bearing; the compression device has a double cylinder therein, and the outer diameter of the flange of the main bearing is fixed on the inner wall of the casing.
  • the winding cover is formed into a bowl-like structure and a circular hole is formed in the center, the circular hole is fitted with an outer diameter of the muffler exhaust port;
  • the motor M has a winding disposed at the winding An outer winding insulation frame, wherein an inner diameter of the winding cover is fitted to the winding insulation frame such that a lower end of the motor winding is covered by the winding cover.
  • the rotary compressor further includes a second spring, the second spring is abutted on the winding cover Between the lower surface and the upper surface of the exhaust muffler.
  • the winding cover is made of a non-conductive material or a non-conductive material.
  • a refrigeration cycle apparatus comprising: a rotary compressor according to an embodiment of the first aspect of the present invention; a condenser connected to an exhaust pipe in the rotary compressor; An evaporator, the evaporator being connected to the condenser through an expansion device; and a reservoir connected between the evaporator and an intake pipe communicating with the compression chamber.
  • the refrigeration cycle apparatus further includes: a refrigerant injection pipe, one end of the refrigerant injection pipe is connected to a connection passage of the condenser and the expansion device, and the other end is connected to a flange side of the sub-bearing and is pressed
  • the contraction chamber is connected.
  • a flow regulating valve is disposed on the refrigerant injection pipe.
  • the refrigeration cycle apparatus further includes: a temperature sensor, the temperature sensor is connected to the exhaust pipe; and a control device, the control device is connected to the temperature sensor.
  • FIG. 1 is a longitudinal sectional view and a refrigerating cycle apparatus view of an internal constitution of a rotary compressor according to a first embodiment of the present invention
  • Figure 2 is a schematic view of the winding cover of the rotary compressor shown in Figure 1;
  • Figure 3 is a cross-sectional view showing the arrangement relationship of the motor, the winding cover, and the like of the rotary compressor shown in Figure 1.
  • Figure 4 is a view showing the operating body, the oil separation chamber, and the oil passage in the rotary compressor shown in Figure 1.
  • Figure 5 is a comparison view of the temperature of each portion of the rotary compressor shown in Figure 1 when comparing the presence or absence of the winding cover;
  • Figure 6 is a detailed sectional view of the compression device of the rotary compressor shown in Figure 1;
  • Figure 7 is a schematic view of one example of the rotary compressor shown in Figure 1, in which the exhaust pipe configuration is changed;
  • Figure 8 is a schematic view of another example of the rotary compressor shown in Figure 1, in which the oil passage design
  • Fig. 9 is a schematic view showing still another example of the rotary compressor shown in Fig. 1, in which the oil passage design is changed;
  • Fig. 10 is a schematic view of the rotary compressor according to the second embodiment of the present invention, in which the frequency conversion is applied Two-cylinder rotary compressor, and the design of the winding cover changes;
  • Figure 11 is a schematic view showing a further variation of the rotary compressor shown in Figure 10;
  • Figure 12 is a schematic view of a rotary compressor in accordance with a third embodiment of the present invention.
  • Figure 13 is a schematic view of a rotary compressor in accordance with a fourth embodiment of the present invention.
  • Figure 14 is a schematic view of a refrigeration cycle apparatus according to a fifth embodiment of the present invention.
  • FIG. 15 is a schematic illustration of a refrigeration cycle apparatus in accordance with a second embodiment of the present invention. detailed description
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” and “second” may include one or more of the features, either explicitly or implicitly.
  • “multiple” means two or more unless otherwise stated.
  • connection should be understood broadly, and may be fixed or detachable, for example, unless otherwise explicitly defined and defined. Connected, or connected in one piece; can be directly connected, or indirectly connected through an intermediate medium, and can be internal to the two elements.
  • the specific meaning of the above terms in the present invention can be understood in a specific case by those skilled in the art.
  • the first feature "on” or “below” the second feature may include direct contact of the first and second features, and may also include first and second features, unless otherwise explicitly defined and defined. It is not in direct contact but through additional features between them.
  • the first feature “above”, “above” and “above” the second feature includes the first feature directly above and above the second feature, or merely indicating that the first feature level is higher than the second feature.
  • the first feature “below”, “below” and “below” the second feature includes the first feature being directly above and above the second feature, or merely indicating that the first feature level is less than the second feature.
  • a rotary compressor RC according to an embodiment of the first aspect of the present invention, which can be used for a rotary compressor of an air conditioner, a freezing machine, a water heater, etc., vortex, is described below with reference to Figs. Compressors and vane compressors, etc.
  • a rotary compressor includes: a sealed casing 2, a motor M, and a compression device P And winding cover 30.
  • an exhaust pipe 3 is disposed on the sealed casing 2, and a lower portion of the casing 2 has an oil reservoir F in which lubricating oil is stored.
  • the motor M is disposed in the casing 2, and the motor M includes a stator 11 having a motor winding 15 and a rotor 20 sleeved inside the stator 11.
  • the outer peripheral wall of the stator 11 has a gap with the inner wall of the casing 2, and the casing 2 is located therein.
  • the compression device is disposed on the lower side of the motor cymbal and includes a crankshaft 60, a main bearing 53, a sub-bearing 57, and a cylinder 51 between the main bearing 53 and the sub-bearing 57, between the main bearing 53, the sub-bearing 57 and the cylinder 51
  • a compression chamber 52 is defined.
  • the winding cover 30 is disposed between the stator 11 and the compression device ⁇ and the winding cover 30 surrounds the lower end of the motor winding, wherein the oil-containing high-pressure refrigerant discharged from the compression chamber 52 is turbulent from the winding cover 30 through the motor to the oil separation chamber. .
  • the outer side of the winding cover 30 has an oil passage S that communicates with the oil reservoir F and the oil separation chamber.
  • the winding cover 30 is made of a non-conductive material or a non-conductive material.
  • the winding cover 30 is provided between the main bearing 53 and the stator 11, the exhaust hole 54 provided with the main bearing 53, and the winding end portion of the stator 11 are the winding cover 30. Encircled. Therefore, the oil-containing high-pressure refrigerant discharged from the main bearing 53 flows from the winding cover 30 through the motor winding 15 to the oil separation chamber T.
  • the high pressure refrigerant exchanges heat directly with the motor windings 15, cooling the entire motor winding 15, and also heating the high pressure refrigerant on the other side.
  • the oil and the refrigerant are separated, and the refrigerant flows from the exhaust pipe 3 to the refrigeration cycle device.
  • the oil on the other side, through several oil passages s, can be returned to the oil reservoir F at the same pressure as the oil separation chamber T without resistance.
  • the motor winding 15 is directly cooled by the discharged refrigerant, so that the reliability of the motor and the efficiency of the motor can be improved.
  • the oil reservoir chamber F includes a gap between the outer circumference of the winding cover 30 and the casing 2, the capacity of the oil reservoir chamber F is sufficient.
  • the exhaust pipe 3 is connected to the casing 2 at the oil separation chamber T (as shown in Fig. 1) or to the casing 2 at the oil passage S, as shown in Fig. 7. .
  • the oil passage S is defined by the outer side of the winding cover 30 and the gap between the stator 11 and the housing 2, as shown in Fig. 1, Fig. 4, Fig. 7-8, Fig. 10-Fig. 15 is shown.
  • the oil passage S is formed by a pipe provided outside the casing 2, two of the pipes The ends are connected to the oil reservoir F and the oil separation chamber T, respectively, as shown in FIG.
  • the winding cover 30 includes: a first column section 301, a second column section 302, and a connecting section 303.
  • the upper end of the first column section 301 is sleeved outside the stator 11
  • the second column section 302 is disposed below the first column section 301
  • the inner diameter of the second column section 302 is smaller than the inner diameter of the first column section 301, the second column
  • the segment 302 is sleeved outside the upper end of the main bearing 53 of the compression device.
  • the connecting section 303 has an inverted truncated cone and is connected between the first column section 301 and the second column section 302.
  • a plurality of core cutouts 13 are formed on the outer peripheral wall of the stator 11, and each of the core cutouts 13 is formed by cutting a part of the outer circumference of the stator 11. Formed, a plurality of core cuts 13 penetrate the axial direction of the stator 11, and a peripheral wall of the stator 11 forms a gap between the outer wall of the stator 11 and the inner wall of the casing 2 through the core cut 13 .
  • the plurality of core cutouts 13 of the stator 11 are respectively recessed inwardly to form a core groove 13a, the core groove 13a penetrates the axial direction of the stator 11 and the upper end of the first column section 301 of the winding cover 30 is outside.
  • a plurality of protrusions 35 are extended upward, the number of protrusions being less than the number of core slots 13a, each of which is embedded in the lower end of the corresponding core groove 13a to engage the upper end of the winding cover 30 with the stator 11.
  • the core slit 13 includes four and is evenly distributed in the circumferential direction, and the projections are two opposite.
  • the rotary compressor further includes a spring 40, the two ends of the spring 40 respectively abut against the lower surface of the flange 304 and the upper surface of the cylinder to stop the upper end surface of the first column section 301 against the stator 11 On the surface.
  • the rotary compressor RC further includes: an auxiliary winding cover 44, as shown in FIG. 13, the auxiliary winding cover 30 is disposed above the motor M and surrounds the upper end of the motor winding, the auxiliary winding
  • the peripheral wall of the cover 30 has a plurality of outer peripheral holes 44a, and a vent hole 44b is formed in the center.
  • the auxiliary winding cover 44 is formed as an inverted bowl-shaped structure, and the lower end of the auxiliary winding cover 44 extends downwardly from the two auxiliary protrusions 35b, and the two auxiliary protrusions 35b are embedded in the upper end of the corresponding core groove 13a to assist The lower end of the winding cover 44 is engaged with the stator 11.
  • the casing 2 includes an upper casing 2a and a lower casing 2b.
  • the upper casing 2 is connected to the exhaust pipe 3, and the lower casing of the upper casing 2 is provided with coils arranged in the up and down direction.
  • the lower casing 2 is connected below the upper casing 2, wherein the motor ⁇ compression device?
  • the winding cover 30 and the auxiliary winding cover 44 are both disposed in the lower casing 2, wherein the lower end of the coil spring abuts on the upper surface of the auxiliary winding cover 44 at a position corresponding to the vent hole 44b.
  • the upper end of the crankshaft 60 is provided with a circular plate 70 disposed coaxially therewith.
  • the circular plate 70 fixed to the upper end of the crankshaft 60 rotates and mixes the refrigerant, so that heavy oil is splashed on the inner wall side of the casing 2 due to the centrifugal force, and therefore, the circular plate 70 has the function of promoting oil separation and returning to the oil reservoir.
  • the upper side wall of the winding cover 30 is provided with a bypass hole 33 therethrough.
  • the winding cover 30 is further provided with a differential pressure valve 37, and the differential pressure valve is disposed corresponding to the bypass hole 33 to open or close the bypass hole 33 according to the pressure difference between the inner side and the outer side of the winding cover 30.
  • the differential pressure valve 37 is a reed valve and includes a main valve 37a and an auxiliary valve 37b fixed to the outer side wall of the winding cover 30.
  • the motor M adopts a motor winding 15 as a centralized winding type inverter motor.
  • the rotary compressor RC further includes: an exhaust gas between the motor M and the main bearing 53.
  • the muffler 55, the exhaust muffler 55 has a muffler exhaust port 56, and the muffler exhaust port 56 is sleeved on the hub of the main bearing 53.
  • the compression device P has a double cylinder therein, and the outer diameter of the flange of the main bearing 53 is fixed on the inner wall of the casing 2, wherein the winding cover 30 is formed into a bowl-like structure and a circular hole is formed in the center, and a circular hole It is fitted to the outer diameter of the muffler exhaust port 56.
  • the motor M has a winding insulating frame 17 disposed outside the winding, wherein the inner diameter of the winding cover 30 is fitted to the winding insulating frame 17 so that the lower end of the motor winding is covered by the winding cover 30.
  • the rotary compressor further includes a second spring 41 that abuts between the lower surface of the winding cover 30 and the upper surface of the exhaust muffler 55 such that the winding cover 30 faces the stator core 12 The direction is pressed to prevent vibration of the winding cover 30.
  • the second spring 41 can be omitted.
  • Fig. 1 is a view showing the basic configuration of a rotary compressor RC of the first embodiment and an outline of a refrigeration cycle device connected thereto.
  • the vertical rotary compressor RC is composed of a compression member P attached to the inner circumference of the sealed cylindrical casing 2, and a motor M disposed on the upper side thereof, and an oil reservoir F provided in the casing 2 The oil is sealed in the middle 6.
  • the motor M is a stator 11 fixed to the housing 2 and a motor rotor fixed to the crankshaft 60 of the compression member P
  • the stator 11 is composed of a stator core 12 made of an electromagnetic steel sheet and a motor winding 15 wound around the inner diameter side thereof.
  • the winding end face 15a and the winding end face 15b are disposed at the upper end and the lower end of the motor winding 15, respectively.
  • the winding cover 30 is composed of a combination of a cylindrical shape and a conical shape in which the upper opening portion 31b and the lower opening portion 31a are disposed, and two projections 35 are provided on the upper opening portion 31b.
  • the inner circumference of the lower opening portion 31a of the winding cover 30 is the outer circumference of the flange of the main bearing 53 in which the compression member P is fitted, and there is a gap between the inner circumference of the upper opening portion 31b and the outer circumference of the winding end surface 15a.
  • the inner diameter of the coil-shaped spring 40 is slightly larger than the outer circumference of the flange of the main bearing 53, and the upper opening portion 31b of the winding cover 30 is pressed against the lower surface of the stator core 12 due to the elastic force. Therefore, the winding cover 30 can be reliably mounted between the upper portion of the compression member P and the lower end of the stator core 12.
  • the winding cover 30 can be fixed at the correct position.
  • the winding cover 30 The design shape of the spring 40 and the shape of the spring 40 can be appropriately changed in accordance with the gist of the present invention.
  • the action body D indicated by "D" in Fig. 1 can be completed by the communication between the compression member P and the winding cover 30 and the motor M.
  • the operating body D is composed of a compression member P, a winding cover 30, and a motor M, and also includes a circular plate 70 fixed to the upper ends of the motor rotor 20 and the crankshaft 60.
  • the operation body D described is an oil-containing high-pressure refrigerant that is discharged from the compression member P that performs the compression activity and that is discharged from the compression member P, flows from the winding cover 30 through the inside of the motor M, and flows from the upper opening portion of the motor M to the upper portion of the motor M.
  • An assembly of oil separation chambers T is an oil-containing high-pressure refrigerant that is discharged from the compression member P that performs the compression activity and that is discharged from the compression member P, flows from the winding cover 30 through the inside of the motor M, and flows from the upper opening portion of the motor M to the upper portion of the motor M.
  • Fig. 3 is an X-X cross section of Fig. 1, showing the details of the lower side portion of the motor M, the arrangement of the winding cover 30, and the relationship between the four core cutouts 13 provided on the outer circumference of the stator core 12 and the casing 2.
  • the core cutout 13 has a core groove 13a at the center, and a projection 35 of the winding cover 30 is fitted to the opposite core slots 13a. Therefore, the upper opening portion 31b of the winding cover 30, which is tightly connected to the lower side plane of the stator 1, and the outer circumference of the holding winding cover 15a are fixed to the stator 11 with a certain gap therebetween. Therefore, efforts are made to prevent it from becoming loose due to vibration through the compressor and refrigerant flow inside the winding cover 30.
  • the four gaps formed between the four core cuts 13 and the inner circumference of the casing 2 are referred to as oil passages S.
  • the four oil passages S are passages through which the oil flows from the separation chamber T.
  • the stator is directly fixed to the rotary compressor inside the casing.
  • iron core cuts of the same shape which serve as passages for the refrigerant and the oil.
  • the motor efficiency is reduced in proportion to the size of the cross section of the core cut.
  • the oil passage S of the present invention does not become a refrigerant passage, it is advantageous in that the cross-sectional area can be reduced to improve the efficiency of the motor.
  • Fig. 4 shows the operating body D and the space cavity formed inside the casing 2.
  • the space cavity can be divided into three chambers as follows. That is, the junction from the bottom surface of the casing 2 to the winding cover 30 and the stator core 12 is a range of the oil reservoir chamber F in which oil can be stored. Further, from the upper surface of the stator core 12 to the ceiling surface of the casing 2, the oil separation chamber T separates the mixed refrigerant flowing out of the operating body D, and is a chamber for separating the refrigerant and the oil. Next, the four core cuts 13 connecting the oil separation chamber ⁇ and the stator core 12 of the oil reservoir F are the oil passages S, and the oil separated from the refrigerant in the oil separation chamber T is dropped to the oil reservoir F. aisle. Further, the exhaust pipe 3 is disposed in the oil separation chamber T in the first embodiment.
  • the oil storage chamber F Since the oil flowing out of the oil separation chamber T can be secured in the oil reservoir F, the oil level of the oil reservoir F rises. Therefore, if the oil storage amount of the oil reservoir F is increased, the oil can also be stored in a part of the oil passage S. In the operation, the maximum oil level of the conventional rotary compressor is near the joint between the cylinder and the main bearing. Therefore, in the first embodiment, the oil storage chamber F has a larger oil retention amount than in the prior art. 10 to 20%, in addition, the oil surface can be increased to more than 20%. Further, due to the effect of increasing the capacity of the oil reservoir F, when the capacity of the refrigeration cycle apparatus is increased, the amount of oil enclosed in the compressor can be easily added.
  • the mixed refrigerant discharged from the compression member P does not pass through the oil reservoir F and the oil passage S, it does not matter the size of the oil passage S.
  • the pressure of the oil separation chamber T is the same as the pressure of the oil reservoir F. . Therefore, the oil channel S If there is an area of oil drop, it is possible to reduce the number of core cuts 13 or the cross-sectional area compared with the prior art, and it is possible to improve the efficiency of the motor M.
  • the above-mentioned mixed refrigerant is compressed in the compression chamber 52 and discharged from the exhaust hole 54 into the winding cover 30, and mixed with the oil which completes the lubrication of the main bearing 53.
  • the mixed refrigerant which adds more oil in the winding cover 30, the gap through the motor winding 15, and a portion flows through the air gap 25 into the oil separation chamber T.
  • the temperature of the mixed refrigerant discharged by the adiabatic compression of the compression chamber 52 is the gas of the casing 2.
  • the heated mixed refrigerant although the quality of the refrigerant is lowered, but the dispersed oil increases the mass and flows to the oil separation chamber T, and the mixed refrigerant can be easily separated into a refrigerant and an oil.
  • the refrigerant after separation of the oil is discharged from the exhaust pipe 3 to the condenser C, and is returned from the intake pipe 9 to the compression chamber 52 through the expansion valve V, the evaporator E, and the accumulator A.
  • the refrigerant circulation device including the compressor repeats the circulation of the refrigerant and the oil.
  • the circular plate 70 fixed to the upper end of the crankshaft 60 rotates and mixes the refrigerant, so that heavy oil may splash on the inner wall side of the casing 2 due to the centrifugal force, and therefore, the circular plate 70 has the function of promoting oil separation and returning to the oil reservoir F. The role.
  • the oil of the oil separation chamber T can fall into the oil reservoir F without resistance, the amount of oil discharged from the exhaust pipe 3 can be greatly reduced.
  • the oil in the oil reservoir F because the rotating refrigerant in the rotating rotor 20 and the compression chamber 52 is not stirred, can ensure high oil storage and oil level. Therefore, not only the margin of reliability of the compressor is increased, but also since all the sliding parts of the compression member P are immersed in the oil, the efficiency of the compressor can be improved by the sealing effect of the oil.
  • Fig. 5 shows a rotary compressor mounted in a split type air conditioner for cooling and heating, and compares the temperature distribution inside the compressor when the winding cover 30 is present during the heating operation. Further, in order to reduce the heat loss during the heating operation, the outer circumference of the casing 2 is covered with a heat insulating material. 5, the muffler vent hole of the exhaust muffler 55 that communicates with the vent hole 54 of the compression member P is bored in the winding cover 30.
  • the TS of the horizontal axis is the temperature of the suction refrigerant of the cylinder 51
  • Tdl is the temperature of the refrigerant discharged from the exhaust muffler 55
  • Tml and Tm2 are the temperatures of the winding end portion 15a and the winding end portion 15b, respectively
  • Td2 is the exhaust pipe 3
  • the temperature of the discharged refrigerant, Toi l is the oil temperature of the oil reservoir F.
  • the vertical axis shows the temperature (°C) of the above components.
  • the winding end face temperature is compared by the presence or absence of a winding cover. Due to the cooling effect of the discharge refrigerant (Tdl), the temperature of the winding end portion 15a (Tml) and the winding end portion 15b (Tm2) is lower when there is a winding cover, and the maximum temperature of the winding end portion 15b (Tm2) is about 10 The difference between °C. On the other hand, when the discharge temperature (Td2) has a winding cover, the temperature becomes high, and the temperature difference from the winding-free cover is about 12 °C.
  • the oil temperature (Toi l ) of the oil reservoir F also produces a significant difference. When there is a winding cover, it is about 14 °C higher than the windingless cover. The reason for this is that there is no heat exchange with the discharge refrigerant (Tdl) when there is a winding cover; the principle that the oil in the oil reservoir is directly cooled by the discharge refrigerant (Tdl) when there is no winding cover. In the state with the winding cover, the oil temperature of the oil reservoir F is probably determined by the oil falling from the oil separation chamber T.
  • the rotary compression member P is composed of a cylinder 51, a main bearing bearing 53 and a sub-bearing 57 assembled on the upper and lower surfaces, a piston 63 and a sliding plate 64 provided on the compression chamber 52, and an eccentric operating piston 63.
  • the main bearing 53 and the sub-bearing 57 are configured by a crankshaft 60 that slidably supports.
  • the slider chamber 67 is semi-closed by blocking the upper cover 68a and the lower cover 68b at the upper and lower opening portions of the slider chamber 67 formed at the back of the slider 64 of the air cylinder 51, respectively.
  • the upper cover 68a and the lower cover 68b are intended to prevent oil agitation of the oil reservoir F caused by the reciprocating motion of the slider 64, thereby achieving the effect of stabilizing the oil level.
  • the oil supply hole 69 in the lower cover 68b supplies oil to the slider chamber 67. Further, in the state where the oil reservoir chamber F is opened, the opening portion of the slider spring hole 65 can be blocked by a plate including the upper cover 68a and the lower cover 68b.
  • the upper end of the oil groove 60a of the crankshaft 60 is designed to be not open in the winding cover 30.
  • Fig. 7 shows an application design example of the first embodiment, even if the exhaust pipe 3 is disposed to open to the oil passage S.
  • the refrigerant separated in the oil in the oil separation chamber T flows from the upper end of the oil passage S in which the exhaust pipe 3 is disposed to the opening of the exhaust pipe 3.
  • most of the oil separated in the oil separation chamber T is dropped from the three oil passages S of the exhaust pipe 3 to the oil reservoir F.
  • the amount of oil discharged is greatly reduced.
  • FIGs 8 and 9 are alternative designs of the oil passage S.
  • a plurality of stator through holes 14 penetrating the upper and lower sides of the stator core 12 are provided between the outer circumference of the stator core 12 and the motor winding 15.
  • the stator through hole 14 serves as an alternative means for the oil drop passage S.
  • Figure 9. A bypass pipe 90 opening in the oil separation chamber T and the oil reservoir F is provided outside the casing 2. This bypass pipe 90 serves as an alternative to the oil passage S.
  • the winding cover 30 is formed of a synthetic resin material which can achieve electrical insulation, refrigerant resistance, oil resistance, heat resistance and the like.
  • a synthetic resin material which can achieve electrical insulation, refrigerant resistance, oil resistance, heat resistance and the like.
  • PBT thermoplastic saturated polyester
  • This material allows contact with the motor windings 15.
  • a metal material such as a steel plate can be used if the motor winding is insulated or a certain gap is ensured between the motor winding and the motor winding.
  • the embodiment 2 shown in Fig. 10 is for miniaturizing the winding cover 30 employed in the first embodiment, and further, it is intended to increase the volume of the oil reservoir F.
  • the compression member P in the second embodiment is a rotation type composed of a double cylinder. Further, the outer diameter of the flange of the main bearing 53 is fixed to the inner wall of the casing 2.
  • the motor M uses a variable frequency motor in which the motor winding 15 is a concentrated winding method.
  • a circular hole formed in the center of the bowl-shaped winding cover 30 having a small upper and lower width is fitted to the outer diameter of the muffler exhaust port 56 which is opened along the hub of the main bearing 53. Further, since the inner diameter of the outer peripheral frame of the winding cover 30 is fitted to the outer diameter of the winding insulating frame 17 of the motor M, the winding end face 15a is covered with the winding cover 30.
  • the high-pressure refrigerant discharged from the twin cylinders merges in the exhaust muffler 55, passes through the muffler exhaust port 56, and flows into the inside of the winding cover 30. Thereafter, as in the first embodiment, after the high-pressure refrigerant is heat-exchanged with the motor winding 15, Flow to the oil separation chamber ⁇ .
  • the winding cover 30 is applicable to a multi-cylinder rotary compressor and a variable frequency motor.
  • the slider chamber (not shown) disposed in the double cylinder is semi-closed, and oil agitation due to the slider to the oil reservoir F can be prevented.
  • the balance block (not shown) fixed to the rotor 20 of the motor is small and the winding end portion 15 of the concentrated winding type is small, the miniaturization of the winding cover 30 is facilitated.
  • it is characterized by a concentrated winding method that expands the refrigerant passage inside the motor.
  • the embodiment 2 shown in Fig. 1 is an application design example of Fig. 10, and the exhaust muffler is connected through the communication pipe 32.
  • the high-pressure refrigerant discharged from the compression member ⁇ to the exhaust muffler 55 flows from the communication pipe 32 through the winding cover 30 to the oil separation chamber ⁇ from the inside of the motor ⁇ .
  • the oil discharged from the upper end of the oil groove 53a of the main bearing 53 directly merges with the oil of the oil reservoir F. Therefore, it is found that the oil amount of the oil storage chamber F changes little, and the discharge amount of the exhaust pipe 3 is less. As shown in the second embodiment, a new effect can be obtained by the exhaust passage and the winding cover 30 which are connected to the compression member P in the communication pipe 32.
  • Fig. 11 shows the details of the winding cover 30 and the connecting pipe 32 connecting the winding cover 30.
  • the shaft hole 62 provided in the center of the winding cover 30 has a hole penetrating the crankshaft 60 and a slight gap between the outer diameter of the crankshaft 60 for sliding. Further, even if the connecting pipe 32 and the winding cover 30 are integrally formed, it is possible to easily connect with the exhaust muffler 55 if there is another elastic pipe member.
  • Embodiment 3 is another elastic pipe member.
  • the housing is used as a rotary compressor RC on the high pressure side, because there is a reservoir A on the suction circuit, usually, the compression chamber
  • the bypass hole 33 is added to the upper portion of the winding cover 30, and a part of the discharge refrigerant escapes to the outside of the winding cover 30, thereby reducing the winding cover 30 to the motor M.
  • the refrigerant that has flowed out of the outside of the winding cover 30 passes through the oil passage S, flows to the oil separation chamber T, and merges with the refrigerant passing through the inner diameter surface of the motor bore. During this period, the amount of oil falling from the oil separation chamber to the oil reservoir F is reduced, and the amount of oil discharged from the exhaust pipe 3 is increased.
  • the ratio of the amount of refrigerant flowing from the winding 30 to the oil separation chamber T after passing through the inside of the motor M and the amount of refrigerant flowing from the bypass hole 33 through the oil passage S into the oil separation chamber is 8:2.
  • the refrigerant flowing from the oil passage S into the oil separation chamber is affected by the presence or absence of the winding cover 30.
  • the ratio of the quantity is Q . 25: 1. 5 0 or 1: 6.
  • the amount of refrigerant flowing from the oil passage S into the oil separation chamber is less overwhelming, and thus it is advantageous to increase the amount of oil discharged.
  • it is allowed to increase the number and area of the bypass holes 33 if necessary. That is to say, the cavity formed by the winding cover 30 is not closed, even a semi-closed cavity.
  • the bypass hole 33 can be opened only when the amount of discharged refrigerant is excessively large. Therefore, when the amount of the discharged refrigerant is exceeded, the bypass hole 33 is opened, and when the set value or lower is reached, the bypass hole 33 is closed, which is convenient.
  • a simple differential pressure valve 37 is added, and a pressure difference between the internal pressure of the winding cover 30 and the outer pressure of the winding cover 30 (same as the oil reservoir F) is passed, and the differential pressure valve is passed.
  • 37 means for opening and closing the through hole 33 to achieve the above purpose. Since the internal pressure of the winding cover 30 is increased because the amount of discharged refrigerant is excessively large, the differential pressure valve 37 is opened to discharge excess refrigerant. However, if the internal pressure is reduced, since the differential pressure valve 37 is closed, the discharge is stopped. Further, in the third embodiment, the differential pressure valve 37 is a reed valve composed of the main valve 37a and the auxiliary valve 37b, and is fixed to the side wall of the winding cover 30. Embodiment 4,
  • the embodiment 3 shown in Fig. 13 is characterized in that an additional auxiliary winding cover 44 surrounds the winding end face 15b.
  • the right side of Figure 13 shows the details of the auxiliary winding cover 44.
  • the auxiliary winding cover 44 is a bowl-shaped cover, and the outer circumference is provided with a plurality of outer peripheral holes 4 and two auxiliary projections 35b, and a vent hole 44b provided in the center portion.
  • the auxiliary winding cover 44 may use a material similar to the winding cover 30.
  • the housing 2 comprises: an upper housing 2£1 and a lower housing 2b, the upper housing 2a being connected to the exhaust pipe 3, the upper housing
  • a coil spring 45 provided in the vertical direction is provided on the lower surface of 2a.
  • the lower casing 2b is connected below the upper casing 2a, wherein the motor ⁇ compression means?
  • the winding cover 30 and the auxiliary winding cover 44 are both disposed in the lower casing 2b, wherein the lower end of the coil spring 45 abuts against the upper surface of the auxiliary winding cover 44) and is positioned corresponding to the vent hole 44b.
  • the upper casing 2a in which the coil spring 45 has been previously disposed, is inserted into the lower casing 2b, and the auxiliary winding cover 44 is pressed against the coil spring 45 to be fixed to the upper surface of the stator 11.
  • all of the winding end faces 15b are covered by the auxiliary winding cover 44.
  • the plurality of outer peripheral holes 44a are oil vent holes, and are opened on the outer circumference of the winding end surface 15b.
  • the exhaust hole 44b corresponds to the inner diameter of the coil spring 45.
  • the mixed refrigerant including the oil discharged from the exhaust port 54 of the compression member flows out of the auxiliary winding cover 44 while cooling the motor winding 15 through the winding cover 30.
  • the refrigerant having a small mass passes through the gap between the upper surface of the circular plate 70 and the auxiliary winding cover 44, and is discharged from the exhaust hole 44b to the exhaust pipe 3, and then discharged to the condenser C.
  • the oil remaining in the discharge refrigerant first slides over the auxiliary winding cover 44 to the oil passage S before flowing into the exhaust pipe 3.
  • the auxiliary winding cover 44 can not only further increase the oil separation effect, reduce the amount of oil discharged to the refrigerant circulation device, but also reduce the temperature of the winding portion 15b which is most susceptible to heat.
  • the present invention can be widely applied to rotary compressors such as vertical rotary compressors and scroll compressors, and applications such as air conditioners, refrigeration equipment, and CO2 water heaters in which the compressors are mounted.
  • the greenhouse gasification coefficient (GWP) is low, and it is planned that the new refrigerant, such as an air conditioner, will be included in the planned refrigerant R32, and the operating temperature is higher than that of the conventional refrigerant.
  • the application of the present invention makes it easier to solve the problem. .
  • a refrigeration cycle apparatus comprising: a rotary compressor, a condenser (:, an evaporator E, an expansion device V, and a reservoir according to an embodiment of the first aspect of the present invention.
  • the condenser C is connected to the exhaust pipe 3 in the rotary compressor, and the evaporator is connected to the condenser through the expansion device V.
  • the expansion device V is an expansion valve.
  • the reservoir A is connected to the evaporation.
  • the device E is between the suction pipe 9 and the compression chamber 52.
  • the refrigeration cycle apparatus further includes: a refrigerant injection pipe 80 having one end connected to the connection passage of the condenser C and the expansion device V and the other end connected to the flange side of the sub-bearing 57 and It is in communication with the compression chamber 52.
  • a flow regulating valve 86 is disposed on the refrigerant injection pipe 80.
  • the refrigeration cycle device further includes: a temperature sensor 85 and a control device 87. As shown in Fig. 14, the temperature sensor 85 is connected to the exhaust pipe 3, and the control device 87 is connected to the temperature sensor 85.
  • the compression load of the rotary compressor fluctuates with changes in the ambient temperature.
  • the motor winding temperature exceeds the safety limit.
  • the motor winding is directly cooled by the discharge refrigerant in the compression member by the features of the present invention.
  • the liquid refrigerant injection system It is applied to the rotary compressor RC to improve the motor winding cooling efficiency and motor temperature control.
  • Embodiment 5 shown in Fig. 14 shows a method of connecting both ends of the refrigerant injection pipe 80 between the condenser C and the expansion valve V, and the sub-bearing 57 in the refrigeration cycle apparatus including the rotary compressor RC. Lan side.
  • a flow rate adjusting valve 86 and a temperature sensor 85 fixed to the exhaust pipe 3 are connected to the control unit 87 in the middle of the refrigerant injection pipe 80. Further, the refrigerant injection hole 81 provided in the sub-bearing 57 is opened in the compression chamber 52.
  • the temperature-reducing refrigerant can directly cool the motor winding 15 through the winding cover 30. That is, the liquid refrigerant injected into the compression chamber 52, the oil 6 that does not cool the reservoir T, and the stator core 12 are used for cooling the motor winding 15. Therefore, compared with the conventional compressor, a high-efficiency cooling effect can be achieved with a small amount of liquid refrigerant. In other words, it is possible to prevent an increase in electrical consumption due to excessive injection of refrigerant. In addition, since there is no cooling oil 6, there is no problem that the degree of superheat of the oil is lowered.
  • the present embodiment is characterized in that the discharge refrigerant temperature is close to the maximum temperature of the motor winding. Therefore, the temperature of the exhaust pipe 3 is monitored by the temperature sensor 85, thereby adjusting the opening degree of the flow regulating valve 86, and the temperature of the motor winding 15 can be appropriately controlled. Further, the same action and effect can be obtained by the gas refrigerant injection technique of the fifth embodiment for the purpose of improving the efficiency of the refrigeration cycle apparatus. Further, the flow rate adjusting valve 86 and the temperature sensor 85 can be omitted in a state where the motor winding 15 is not required to be closely controlled.
  • Embodiment 6 Embodiment 6,
  • JP-A-1997-217692 JP-A-1997-217692
  • Compressor-Coiled Scroll Compressor the internal scroll pressure as a high-pressure side vertical scroll compressor and rotary pressure
  • the embodiment 6 shown in Fig. 15 solves the problems of the scroll compressor by applying the techniques disclosed in the first to the fifth embodiments.
  • the vertical scroll compressor SC of the sixth embodiment is assembled by a compression member P assembled on the inner circumference of the sealed cylindrical casing 2, a motor M disposed on the upper side, and a lower end of the stator 11.
  • the winding cover 30 and the like are configured to enclose the oil 6 in the oil reservoir F of the casing 2.
  • the low-pressure refrigerant sucked into the suction pipe 9 of the stationary plate 95 is compressed by the movable plate (not shown) which is eccentrically operated in the stationary plate 95, and is compressed to become an oil-containing high-pressure mixed refrigerant, which is discharged into the winding cover 30. Since the flow of the mixed refrigerant thereafter is the same as that of the first embodiment, the winding cover 30 brings about the same action and effect, and therefore the description thereof will be omitted. Therefore, the present invention is not limited to the rotary compressor and the scroll compressor, and may be applied to a vertical rotary compressor in which the internal pressure of the casing is used as the high pressure side.

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

Abstract

L'invention concerne un compresseur rotatif et un appareil de circulation frigorifique pourvu de ce compresseur. Le compresseur rotatif selon l'invention comprend : un logement de joint (2), une partie inférieure du logement (2) étant pourvue d'une chambre de stockage d'huile (F) ; un moteur (M) disposé dans le logement (2) et comprenant un stator (11) pourvu d'un bobinage de moteur (15) et un rotor (20), un écart étant formé entre une paroi périphérique externe du stator (11) et une paroi interne du logement (2), une chambre de déshuilage (T) étant disposée dans le logement (2) au-dessus du moteur (M) ; un appareil de compression (P) disposé au niveau de la partie inférieure du moteur (M) et limitant une chambre de compression (52) ; ainsi qu'un couvercle de bobinage (30) disposé entre le stator (11) et l'appareil de compression (P), ledit couvercle(30) englobant l'extrémité inférieure du bobinage de moteur (15). Un réfrigérant haute pression contenant de l'huile, évacué par la chambre de compression (52), s'écoule à travers le couvercle de bobinage (30) et le moteur (M) dans la chambre de déshuilage (T). Un côté externe du couvercle de bobinage (30) comporte un passage d'huile (S) reliant la chambre de stockage d'huile (F) et la chambre de déshuilage (T).
PCT/CN2013/079932 2013-07-23 2013-07-23 Compresseur rotatif et appareil de circulation frigorifique pourvu de ce compresseur WO2015010260A1 (fr)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104883004A (zh) * 2015-06-11 2015-09-02 广东美的暖通设备有限公司 电机散热结构、空调器和电机散热方法
CN104896699A (zh) * 2015-06-11 2015-09-09 广东美的暖通设备有限公司 电机散热结构、空调器和电机散热方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10318169A (ja) * 1997-05-21 1998-12-02 Matsushita Refrig Co Ltd 縦型ロータリ圧縮機
JP2005002868A (ja) * 2003-06-11 2005-01-06 Daikin Ind Ltd 圧縮機
CN101713405A (zh) * 2009-08-22 2010-05-26 广东美芝制冷设备有限公司 卧式旋转压缩机的内部气体导向机构
CN201650740U (zh) * 2010-03-29 2010-11-24 广东美芝制冷设备有限公司 卧式旋转压缩机的内部气体导向机构
CN202833180U (zh) * 2012-06-27 2013-03-27 广东美芝制冷设备有限公司 旋转压缩机

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10318169A (ja) * 1997-05-21 1998-12-02 Matsushita Refrig Co Ltd 縦型ロータリ圧縮機
JP2005002868A (ja) * 2003-06-11 2005-01-06 Daikin Ind Ltd 圧縮機
CN101713405A (zh) * 2009-08-22 2010-05-26 广东美芝制冷设备有限公司 卧式旋转压缩机的内部气体导向机构
CN201650740U (zh) * 2010-03-29 2010-11-24 广东美芝制冷设备有限公司 卧式旋转压缩机的内部气体导向机构
CN202833180U (zh) * 2012-06-27 2013-03-27 广东美芝制冷设备有限公司 旋转压缩机

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104883004A (zh) * 2015-06-11 2015-09-02 广东美的暖通设备有限公司 电机散热结构、空调器和电机散热方法
CN104896699A (zh) * 2015-06-11 2015-09-09 广东美的暖通设备有限公司 电机散热结构、空调器和电机散热方法

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