WO2009059488A1 - A rotary compressor with low pressure in its shell and methods for controlling its cold media and oil and application thereof - Google Patents

A rotary compressor with low pressure in its shell and methods for controlling its cold media and oil and application thereof Download PDF

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Publication number
WO2009059488A1
WO2009059488A1 PCT/CN2008/000244 CN2008000244W WO2009059488A1 WO 2009059488 A1 WO2009059488 A1 WO 2009059488A1 CN 2008000244 W CN2008000244 W CN 2008000244W WO 2009059488 A1 WO2009059488 A1 WO 2009059488A1
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WO
WIPO (PCT)
Prior art keywords
oil
cylinder
refrigerant
hole
disposed
Prior art date
Application number
PCT/CN2008/000244
Other languages
French (fr)
Chinese (zh)
Inventor
Zhenhua Chen
Zhengxiong Xiaojin
Ziqiang Liang
Chunxian Long
Qiang Gao
Original Assignee
Guang Dong Mei Zhi Refrigeration Equipment Co., Ltd
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 Guang Dong Mei Zhi Refrigeration Equipment Co., Ltd filed Critical Guang Dong Mei Zhi Refrigeration Equipment Co., Ltd
Publication of WO2009059488A1 publication Critical patent/WO2009059488A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00Compression machines, plants or systems with non-reversible cycle
    • F25B1/04Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30Rotary-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
    • F04C18/34Rotary-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
    • F04C18/356Rotary-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
    • F04C18/3562Rotary-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
    • F04C18/3564Rotary-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04Heating; Cooling; Heat insulation
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06Silencing
    • F04C29/065Noise dampening volumes, e.g. muffler chambers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06Silencing
    • F04C29/068Silencing the silencing means being arranged inside the pump housing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F04C29/128Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves

Definitions

  • the present invention relates to a rotary compressor, and more particularly to a low-pressure rotary compressor of a housing, a refrigerant control method and an application thereof.
  • 100% of the common rotary compressors are the high pressure side of the housing.
  • the main reasons are: 1) When the internal pressure of the housing is the high pressure side, due to the pressure difference between the internal pressure of the housing and the internal pressure of the cylinder, the slide and The lubrication of the piston is very easy, that is, it is advantageous in terms of lubrication; 2) In order to compress the front end of the sliding piece against the piston, it is necessary to set the back pressure of the sliding piece to high pressure, that is, the necessity of working principle; 3) The lubricating oil discharged from the cylinder compression chamber can be separated in the casing, which is advantageous in terms of oil discharge processing; 4) The direct connection of the suction pipe to the cylinder can improve the cylinder volumetric efficiency, that is, the compressor efficiency is advantageous.
  • the object of the present invention is to provide a low-pressure rotary compressor with a simple and reasonable structure, high safety, low production cost, flexible operation, good lubrication performance, low oil discharge, high compression efficiency and long service life.
  • a low-pressure rotary compressor designed according to the purpose includes a compression assembly and a motor assembly disposed in the housing, the compression assembly including one or more cylinders, a piston disposed in the cylinder, and a cylinder slide groove
  • the motor assembly comprises a motor rotor and a motor stator
  • the structural feature is that a cooling device is arranged on the housing, and the refrigerant flow dividing device is arranged in the housing
  • the top or side of the refrigerant shunt device includes a shunt tube in which a spring tube that adjusts the split ratio is disposed.
  • An air suction muffler is disposed between the motor assembly and the compression assembly, a circumferential gap is disposed between the suction muffler and the main bearing, and/or a motor rotor or an eccentric crankshaft or an upper bearing is disposed
  • a circular plate covers the suction hole provided in the suction muffler, and/or a small gap is provided between the motor rotor and the motor stator, and/or a gap provided between the motor stator and the casing is connected to the upper space portion of the motor
  • a third suction hole is provided in the upper bearing, the third suction hole is in communication with the suction muffler and the hoop clearance; and/or two suction holes are provided in the cylinder, respectively, which are disposed in the upper bearing vertical
  • the first suction hole in the direction and the second suction hole in the horizontal direction of the cylinder side surface, the first suction hole and the third suction hole communicate with each other, and the first suction hole and the second suction hole communicate with each other.
  • the high pressure side of the cylinder is provided with a venting hole communicating with an exhaust muffling cavity provided in the casing, the exhaust muffler cavity being disposed at the cylinder venting hole and the exhaust pipe disposed on the casing
  • the exhaust muffler chamber is provided with an exhaust valve and an exhaust ⁇ limit plate, and the exhaust valve and/or the exhaust limit plate are U-shaped or V-shaped, and / or the sliding chamber of the cylinder is connected to the exhaust pipe,
  • the balance body is provided with a balance hole disposed on the upper bearing and/or the lower bearing and/or the intermediate partition plate, communicating with the inside of the piston, and/or the upper bearing and the lower bearing are provided with an annular groove,
  • the annular groove communicates with the inside of the piston
  • the balance hole communicates with the annular groove
  • the oil separator is disposed outside the compressor, and the oil separator is sequentially connected to the cylinder through the oil injection pipe outside the casing and the oil supply pipe in the casing;
  • the oil supply pipe communicates with the cylinder through an oil injection hole provided on the upper bearing or the lower bearing, or the oil supply pipe passes through the first oil supply hole and the second oil supply hole respectively disposed on the intermediate partition plate between the two cylinders.
  • the first cylinder and the second cylinder are in communication.
  • the end ring of the motor rotor is provided with an upper circular plate and/or a lower circular plate, and the upper circular plate and/or the lower circular plate are provided with a circular hole, and a gap is formed between the circular hole of the lower circular plate and the main bearing.
  • the end ring, the eccentric crankshaft and the upper circular plate enclose a space portion, and the eccentric crankshaft is provided with a transverse hole communicating with the space portion, and the top end of the central hole disposed on the eccentric crankshaft communicates with the transverse hole, and the bottom end of the eccentric crankshaft is provided with an oil pump
  • the bottom end of the oil pump is open in the oil pool at the bottom of the casing, the central hole is connected with the oil pump, and/or the inner surface of the main bearing is provided with a spiral oil groove, the top end of the oil groove is open to the space portion, and/or the upper bearing and the lower portion
  • the bearing is disposed on the moving surface of the piston with a first opening slot and a second opening slot, respectively.
  • a refrigerant control method for a low-pressure rotary compressor of a casing characterized in that a low-pressure refrigerant entering a compressor is branched into two branches and above, one of which passes through the inside of the casing for heat exchange and then enters the cylinder, and One road enters the cylinder directly, and the refrigerant in the two branches merges before being compressed.
  • Another refrigerant control method for a low-pressure rotary compressor of a casing characterized in that two or more cylinders are arranged in the compressor, and the low-pressure refrigerant entering the compressor is divided into two branches and above, wherein One road enters one cylinder directly, and the other branch exchanges heat through the inside of the casing before entering another cylinder.
  • the compressor is provided with a low-pressure refrigerant flow dividing device, and the branches are adjusted by the device The flow ratio of low pressure refrigerant.
  • the liquid and gaseous portions are separated by the vapor-liquid separation device, and the liquid refrigerant first enters the inside of the casing for heat exchange and then enters the cylinder, and the gaseous refrigerant directly enters the cylinder.
  • a returning oil control method for a low-pressure rotary compressor of a casing characterized in that oil is directly returned from the oil separator outside the compressor to the cylinder compression chamber, or indirectly through two partitions disposed between the two cylinders Returning oil to the cylinder, or supplying oil to the low pressure part of the cylinder or the suction circuit from the oil pool in the compressor or through a hole or groove penetrating the inside of the piston.
  • HCFC refrigerant For the application of a low-pressure rotary compressor of a casing, HCFC refrigerant, HFC refrigerant, HC refrigerant and C0 2 refrigerant can be used.
  • the present invention solves the basic problem in the above technical background by setting the internal pressure of the casing of the rotary compressor to the low pressure side, and realizes the safe use of the HC refrigerant, the refrigerant such as C0 2, and the purpose of protecting the global environment, and also solves the problem.
  • the internal pressure of the casing has long been a problem faced by the low pressure side: that is, the compressor has poor lubricity, low efficiency, and large oil discharge, and provides a concrete and feasible method.
  • the present invention provides a control method for diverting the low-pressure suction refrigerant so as to be sucked into the cylinder and prevent the compressor from being reduced in efficiency, and also provides a seal row in the arrangement for controlling the superheat of the suction refrigerant to a minimum.
  • a control method for preventing overheating of the housing refrigerant is avoided.
  • the present invention provides a lubricating oil control method which not only lubricates all moving parts in the compressor, but also reduces the amount of oil discharged from the inside of the compressor and reduces energy consumption.
  • the present invention Compared with the current high-pressure rotary compressor of the casing, the present invention also has a great advantage in terms of manufacturing cost.
  • the invention not only facilitates the use of HC-type refrigerants and C0 2 refrigerants which meet the needs of the international community, but also can be applied to the current Freon-type refrigerants, and has a wide application range.
  • FIG. 1 is a schematic diagram of a system loop structure according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional structural view of an embodiment of the present invention.
  • Figure 3 is a schematic cross-sectional view of the X-X of Figure 2;
  • FIG. 4 is a schematic enlarged perspective view of the exhaust valve.
  • Fig. 5 is a schematic enlarged plan view showing the T-S of Fig. 3;
  • Figure 6 is a partial cross-sectional structural view of Figure 2.
  • FIG. 7 is a partial cross-sectional structural view of another embodiment of FIG. 6.
  • FIG. W is a partial cross-sectional structural view of another embodiment of FIG. 6.
  • Figure 8 is a cross-sectional structural view showing another embodiment of the present invention.
  • Figure 9 is a schematic cross-sectional enlarged view of the vapor-liquid separation device.
  • FIG. 10 is a cross-sectional structural view showing still another embodiment of the present invention.
  • 1 is the compressor
  • 2 is the exhaust pipe
  • 3 is the exhaust muffler
  • 4 is the oil separator
  • 5 is the condenser
  • 6 is the expansion valve
  • 7 is the evaporator
  • 8 is the low pressure circuit
  • 9 is the shunt pipe 10 is a bifurcation circuit
  • 11 is a suction pipe
  • 12 is a vent hole
  • 13 is an exhaust muffler cavity
  • 14 is a fuel injection pipe
  • 20 is a casing
  • 21 is a compression assembly
  • 22 is a motor
  • 23 is a cylinder
  • 24 is The upper bearing, 25 is the lower bearing
  • 26 is the eccentric crankshaft
  • 27 is the motor rotor
  • 28 is the motor stator
  • 31 is the first suction hole
  • 32 is the second suction hole
  • 34 is the third suction hole
  • 35 is the suction muffler.
  • 36 is the main bearing
  • 37 is the circumferential clearance
  • 38 is the end ring
  • 39 is the lower circular plate
  • 40 is the spring tube
  • 41 is the upper circular plate
  • 42. 1 is the upper motor coil
  • 42. 2 is the lower motor coil
  • 44 is the oil pool
  • 45 is the center hole
  • 46 is the transverse hole
  • 47 is the space part
  • 48 is the spiral oil groove
  • 49 is the liquid refrigerant
  • 50 is the gas refrigerant
  • 51 is the oil hole
  • 51. 1 is the first Oil injection hole
  • 51. 2 is the second oil hole
  • 52 is the oil supply pipe
  • 53 is the cylinder compression cavity
  • 54. 1 is the first Open slot, 54.
  • 2 is the second open slot
  • 55 is the cylinder low pressure chamber
  • 61 is the piston
  • 62 is the sliding vane
  • 63 is the sliding vane cavity
  • 64 is the vane spring
  • 71 is the exhaust valve
  • 72 is the exhaust limit Position plate
  • 73 is the communication groove
  • 81 is the balance hole
  • 82 is the groove
  • 83 is the oil drain hole
  • -84 is the motor stator outer circumference gap
  • 85 is the stator core
  • 86 is the small gap
  • 87 is the partition
  • 88 is the lower space
  • 91. 1 is the upper cylinder
  • 91. 2 is the lower cylinder
  • 93 is the balance block
  • 98 is the gas-liquid separation device.
  • the high-pressure refrigerant compressed by the compressor 1 passes through the exhaust muffler 3 and the oil separator 4 through the exhaust pipe 2 to reach the condenser 5, and the refrigerant condensed by the condenser sequentially passes through the expansion valve 6 and evaporates. After the device 7, it becomes a low pressure refrigerant.
  • the low pressure refrigerant enters the shunt tube 9 from the low pressure circuit 8, and the shunt tube 9 is provided with two circuits: one of the circuits directly enters the inside of the compressor casing and is then drawn into the cylinder; the other circuit is passed along the bifurcation circuit 10 to the suction pipe. 11.
  • the suction pipe is directly connected to the cylinder.
  • the casing pressure is the low pressure side. Then, the low-pressure refrigerant flowing into the inside of the casing and the low-pressure refrigerant directly flowing into the cylinder from the branching circuit 10 are merged before the cylinder is compressed, and the high-pressure refrigerant compressed inside the cylinder passes through the exhaust muffler inside the compressor and the exhaust pipe. 2 Vent directly to the outside of the housing.
  • the high-pressure refrigerant containing lubricating oil (hereinafter referred to as oil) passes through the external exhaust muffler 3 and the oil separator 4, and reaches the condenser 5 again, thereby forming a cycle in which the compressor functions to construct a circulation system.
  • oil lubricating oil
  • the low-pressure rotary compressor of the casing directly discharges the high-pressure refrigerant to the outside of the casing, the oil contained in the refrigerant discharged from the refrigerant cannot be separated in the casing, and therefore, the oil separator is provided in the design provided by the oil.
  • the oil separated by the separator will flow through the oil filler pipe 14 to the compression chamber in the cylinder.
  • the pressure on the low pressure side is an important part of the present invention, and the system can be widely applied to air conditioners and refrigeration equipment.
  • a compression assembly 21 and a motor assembly 22 are disposed within the housing 20.
  • the compression assembly includes a cylinder 23, an upper bearing 24, a lower bearing 25, and an eccentric crankshaft 26 supported by the bearings.
  • the motor assembly includes a motor rotor 27 and a motor stator 28, and the motor rotor 27 fixed by the eccentric crankshaft 26 is fixed in the housing.
  • the motor stator 28 is driven.
  • the cylinder 23 is provided with two suction holes, that is, a first suction hole 31 disposed in the vertical direction of the upper bearing 24 and a second suction hole 32 in the horizontal direction of the cylinder side, the first suction hole 31 and the upper bearing 24
  • the third suction hole 34 communicates, and the second suction hole 32 communicates with the first suction hole 31.
  • the shunt tube 9 mounted on the upper portion of the casing divides the refrigerant of the low pressure circuit in two directions, i.e., directions indicated by arrows A and B.
  • the function of the branch pipe 9 is to mainly cause the liquid refrigerant to flow in the direction of the arrow A and the gas refrigerant in the direction of the arrow B when the mixed refrigerant of the liquid and the gas flows in.
  • the spring tube 40 is press-fitted into the shunt tube 9, which functions to adjust the split ratio and further exert the gas-liquid separation function. When the actual operation is performed, the installation height h of the spring tube can be adjusted.
  • the third suction hole 34 is open to the suction muffler 35 installed in the upper bearing, and the suction muffler can not only reduce the noise caused by the suction pulsation of the cylinder, because the circular gap 37 between the outer sides of the main bearing 36 is the inlet of the suction muffler. This gap also serves to absorb all of the refrigerant flowing into the casing.
  • a lower circular plate 39 is mounted on the end ring 38 of the motor rotor 27, and a circular hole is provided in the middle of the lower circular plate, and a small gap is provided between the circular hole and the main bearing 36, so that the lower circular plate can be combined with the motor rotor Rotate together.
  • the lower circular plate 39 has a function of reducing the amount of oil discharged from the compressor and improving the oil absorption effect of the eccentric crankshaft, and the same upper circular plate 41 is attached to the upper portion of the rotor of the motor.
  • the balance block is omitted in Fig. 1.
  • a front end of the oil pump 43 mounted at the lower end of the eccentric crankshaft 26 is provided with a hole at the oil pool 44.
  • a center hole 45 provided at a central portion of the eccentric crankshaft communicates with the lateral hole 46 near the lower end of the motor rotor.
  • the lateral hole defines a space portion 47 formed between the end ring 38 and the lower circular plate 39. Further, the spiral oil groove 48 provided on the inner moving surface of the main bearing 36 is also opened at the space portion 47.
  • the lower bearing 25 is provided with an oil filling hole 51 which communicates with the oil supply pipe 52 and communicates with the oil separator 4 so that the oil separated by the oil separator can be returned to the cylinder compression chamber 53 .
  • the oil hole opens and closes in the lower plane of the piston.
  • the oil can be returned to the compressed refrigerant only by opening the hole in the cylinder compression chamber, the hole cannot be opened on the low pressure side of the cylinder, so the oil cannot return to the cylinder.
  • Low pressure side Movement in the upper bearing surface of the piston cylinder and the lower bearing is provided with a first opening and a second opening groove 54.1 54.2 groove, which groove is open to the low pressure oil supplied to the cylinder chamber 61 in the piston oil passage 55.
  • the piston 61 inside the cylinder 23 is driven by the eccentric crankshaft to perform an eccentric rotation motion, and a vane 62 is disposed in the vane groove, and a space portion of the back portion is a vane chamber 63.
  • the rotary compressor needs to make the front end of the sliding plate follow and press on the outer wall of the piston. Therefore, in the low-pressure rotary compressor of the casing of the present invention, the sliding chamber is also required to be on the high pressure side, and therefore, the sliding chamber is sealed. The refrigerant does not leak into the inside of the housing on the low pressure side.
  • the vane cavity has a built-in vane spring 64.
  • the high pressure side of the cylinder is provided with an exhaust hole 12 communicating with the nearly quadrangular exhaust muffler chamber 13.
  • the exhaust muffler chamber is internally provided with an exhaust valve 71 and an exhaust limit for restricting the operation of the exhaust valve. Board 72.
  • the exhaust valve 71 and the exhaust limit plate are U-shaped or V-shaped and can be extended in a limited-volume exhaust muffler chamber. For small exhaust muffler chambers, the action of the exhaust valve can also be designed to be more than adequate.
  • the U-shaped stopper is a resilient leaf spring which is positioned on the inner wall of the quadrangular exhaust muffler chamber and the cylinder mounting surface of the upper and lower bearings, and the exhaust valve is fixed by the elastic exhaust stopper.
  • a communication groove 73 is provided at the exhaust muffler chamber 13, and the refrigerant in the exhaust muffler chamber can flow into the vane chamber 63 through the communication groove. .
  • the figure shows the specific mounting position of the vane chamber 63 and the exhaust pipe 2.
  • a slider spring is disposed on the back of the slider chamber sealed by the upper bearing 24 and the lower bearing 25.
  • the machining hole of the slider spring is provided with an exhaust pipe connection.
  • the oil separator 4 is disposed between the exhaust muffler and the condenser, and the oil separator 4 has the function of the external exhaust muffler 3, and the external exhaust muffler can be omitted by installing the oil separator 4 at the position of the external exhaust muffler.
  • the exhaust pipe 2 can be connected by a slide spring machining hole, which has the advantage of sealing the slide chamber with an exhaust pipe. The improvement of motor cooling and compressor efficiency is briefly described below.
  • the compression assembly 21 begins to draw in the low pressure refrigerant.
  • the refrigerant of the evaporator 7 flows from the low-pressure refrigerant circuit 8 to the branch pipe 9, where it is branched into two circuits, first along the arrow
  • the refrigerant shunted in the direction of the head A flows into the upper space portion 89 in the casing, is rectified by the upper circular plate 41, and is dispersed in the inner circumference of the upper motor coil 42. 1 to effectively cool the motor coil.
  • the low pressure refrigerant is moved mainly through the inside of the motor or the small gap 86 to the lower space portion 88 formed between the motor assembly 22 and the compression assembly 21.
  • the low-pressure refrigerant cools the coil inside the motor and the oil attached to the motor or the casing in the middle.
  • the low-pressure refrigerant cools the lower motor line ⁇ 42. 2 and draws it from the circular gap 37 to the suction muffler 35.
  • the refrigerant in the suction muffler flows from the first suction hole 34 through the second suction hole 32 into the cylinder, and the low-pressure gas that has branched through the branch pipe 9 in the direction of the arrow B flows directly into the second suction hole 32, and flows into the first suction hole.
  • the refrigerant reaching the second suction hole 32 merges and is sucked into the cylinder to be compressed.
  • the refrigerant flows from the upper coil of the motor 42. 1 to the lower coil of the motor 42. 2, the refrigerant flows, that is, the refrigerant flows to the center of the inner diameter of the motor. Good plan. It is an optimum design to arrange the suction muffler on the inner side of the lower motor coil 42.2 and to place the gap 37 in the center of the suction muffler to make a circular hole.
  • the invention not only guides the flow of the refrigerant from the upper coil of the motor to the lower coil of the motor, but also adjusts the arrangement and shape of the gap to form a uniform flow of the refrigerant to reduce the temperature dispersion of the motor coil.
  • the action of the low-pressure refrigerant flowing into the casing from the direction of the arrow A will be described here. If the motor coil and oil are not cooled by the refrigerant, the temperature will rise above 150 °C, which will cause 'coil burning and oil aging problems.
  • the temperature of the low-pressure refrigerant flowing into the casing is usually around 5 ⁇ 20 °C. By cooling the motor and oil, they are kept at a suitable temperature range of 50 ⁇ 110 °C. Due to heat exchange, the temperature of the low-pressure refrigerant will rise. When the temperature of the low-pressure refrigerant rises, the refrigerant suction efficiency of the compressor will decrease.
  • the reduced efficiency will be proportional to the temperature rise rate of the suction refrigerant.
  • the refrigeration capacity is the largest. Will be about 10% lower. Since the low-pressure gas branched in the direction of the arrow B flows into the second suction port without substantially changing the temperature, the problem that the compressor refrigeration capacity is reduced does not occur.
  • the low-pressure refrigerant branched along the arrow A merges with the refrigerant in the direction of the arrow B before flowing into the cylinder, so the temperature of the refrigerant sucked in the cylinder is determined by the split ratio, the compressor operating conditions, and the like.
  • the splitting can reduce the temperature of the refrigerant sucked by the cylinder without causing a problem that the compressor refrigeration capacity is drastically reduced, the compressor efficiency can be prevented from being lowered.
  • the position of the split is not limited to the position in the drawing.
  • the liquid refrigerant that has flowed in the direction A and the high temperature portion such as the motor unit are heat-exchanged and then vaporized, it is possible to prevent the liquid refrigerant from flowing into the cylinder from the first suction hole 31.
  • a large amount of oil in the liquid refrigerant is vaporized by the refrigerant itself, so that it is easily separated from the refrigerant, and the oil is easily recovered into the oil pool 44 in the casing.
  • the spring tube not only has to adjust the split ratio of the arrow A direction and the arrow B direction, but also plays an important role in separating the gas refrigerant and the liquid refrigerant.
  • the low-pressure refrigerant sucked into the cylinder is compressed by the piston to become a high pressure.
  • the refrigerant enters the exhaust muffler chamber 13 from the exhaust hole 12, and is discharged from the communication passage 73 through the vane chamber 63 through the exhaust pipe 2. Since the vane chamber is on the high pressure side, the front end of the vane can be pressed against the outer circumference of the piston to start the process of compressing the gas.
  • the temperature of the exhaust circuit of the exhaust muffler chamber and the vane chamber of the low-pressure rotary compressor of the casing is relatively high, and usually reaches about 110 °C in order to make the exhaust circuit and the low-pressure refrigerant in the casing. Heat exchange is minimized, thereby preventing the compressor from drawing in overheated refrigerant and increasing compressor efficiency.
  • the technique provided herein allows the exhaust muffler chamber volume to be the minimum required, not only to seal the exhaust muffler chamber and the vane chamber from the upper and lower bearings to prevent direct contact with the low pressure refrigerant in the housing.
  • the volume of the exhaust muffler chamber is small, the noise due to the exhaust pulsation is increased, and the countermeasure is to add an external exhaust muffler 3 to enlarge the total volume of the muffler to reduce compressor noise.
  • Fifth. Fig. 8 is a design in which the shunt tube 9' is moved from the upper portion of the casing to the side of the casing to reduce the length of the branching circuit 10'.
  • the shunt tube in the design is connected to the outer circumferential gap 84 of the motor stator. Since the lower opening end of the peripheral gap connecting the shunt tubes is closed by the end plate mounted on the stator core 85, the low-pressure gas branched in the direction of the arrow ⁇ ' flows from the outer peripheral space to the upper space of the casing, and another portion of the low-pressure gas Then, the arrow B' flows into the cylinder, so that the same effect as the shunt tube 9 shown in Fig. 2 can be obtained.
  • This design example has the effect of reducing the length of the split circuit 10 and reducing the compressor torque.
  • Fig. 9 shows the separation of gas and liquid.
  • the device 98 is mounted in the vicinity of the system's low pressure refrigerant circuit, or compressor suction circuit.
  • the gas-liquid mixed refrigerant from the evaporator 7 is separated into a liquid refrigerant 49 and a gas refrigerant 50 in the gas-liquid separation device, and the liquid flows in the direction of the arrow A" and the gas in the direction of the arrow.
  • the result is shown in Fig. 2.
  • the shunt tube 9 shown in Fig. 2 has the same effect.
  • Figure 10 shows the design of a splitter for a two-cylinder rotary compressor application that uses a separate suction of the suction refrigerant into two cylinders.
  • the low-pressure refrigerant in the direction of the arrow A'" is cooled by the motor or the like, and is sucked into the cylinder from the third suction hole 34 and the second suction hole 32 of the upper cylinder 911.1 by the suction muffler 35, along the arrow
  • the low pressure refrigerant in the direction is directly sucked into the lower cylinder 91.2.
  • the two cylinders independently perform refrigerant compression, and the high-pressure refrigerant discharged from the respective cylinders merges from the vane chamber to the intermediate partition plate 87, and then is discharged from the exhaust pipe connected to the intermediate partition to the system side.
  • the technique provided in this paper is not only to minimize the amount of refrigerant sucked in the casing, but also to specify that the temperature rise of the motor is within the allowable range.
  • the remaining residual refrigerant it is directly sucked into the cylinder to lower the temperature of the refrigerant sucked by the cylinder, and as a result, the problem of excessive rise in the temperature of the low-pressure refrigerant or the problem that the density of the refrigerant is too small can be prevented. Therefore, the compressor refrigeration capacity reduction and efficiency reduction can be greatly improved.
  • the technology provided herein diverts the low pressure refrigerant circuit into two intake cylinders.
  • the heat exchange between the high-pressure refrigerant circuit such as the exhaust muffler chamber and the low-pressure refrigerant in the casing can be prevented, and the temperature rise of the low-pressure refrigerant in the casing can be controlled to prevent the refrigeration capacity and efficiency of the compressor from being lowered.
  • a high-pressure refrigerant circuit is used to seal the exhaust muffler chamber with upper and lower bearings, and a method for effectively designing the valve device with a exhaust muffler chamber in a limited volume is proposed.
  • the following is a brief description of the amount of oil discharged. Improved lubrication.
  • the high-pressure rotary compressor of the casing can automatically supply oil from the oil pool to the center hole 45 by the eccentricity of the oil, and the oil of the center hole is set through the oil hole and the bearing provided in the eccentric crankshaft. Oil holes for lubrication of eccentric crankshafts and bearings.
  • a low-pressure rotary compressor housing because the center crank eccentrically hole pressure is a low pressure side, the pressure and the same housing, so that rotation of the eccentric crankshaft by automatic supply from the oil sump through the central bore 43 to the lower end of the inlet pump.
  • the biggest problem of lubrication technology is the lubrication of moving parts required for cylinder compression and the amount of oil discharged to the system side to be below the specification value. That is, while supplying oil to the inside of the cylinder and lubricating the parts required for compression, the gap of the compression unit is filled with oil to prevent gas leakage. Since the oil supplied to the cylinder is not recovered into the inside of the casing, but is completely discharged from the exhaust pipe together with the high-pressure refrigerant, the amount of oil discharged to the system side tends to exceed the specification value. Therefore, in order to prevent and avoid these problems, the oil supply amount of the cylinder is optimized and stabilized, and the oil discharged from the compressor exhaust pipe is prevented from draining to the system side.
  • the technical solution provided by the present invention is as follows: First, oil is not designed to flow into the suction muffler 35. 2, the oil discharged from the oil groove 48 provided in the main bearing 36 flows into the space portion 47 composed of the lower circular plate 39 and the end ring 38, and then from the outer peripheral space of the space portion to the inner motor coil 42. 2 Zhou Fei San. The scattered oil is sucked into the motor coil and dropped onto the upper bearing 24, and finally dripped from a plurality of holes provided near the outer periphery thereof to be recovered into the oil pool 44. Therefore, the lower circular plate prevents oil from dripping into the circular gap 37 of the suction muffler, and the suction muffler itself does not absorb oil.
  • the pressure of the rotating space portion 47 of the lower circular plate is lowered, the pressure of the eccentric crankshaft transverse hole 46 communicating with the space portion is also lowered, and the upward oil absorbing ability of the eccentric crankshaft center hole 45 is further increased, and the oil of the center hole of the eccentric crankshaft may also be Discharge from the transverse hole can effectively prevent the suction muffler 35 from sucking in oil due to the blocking action of the lower circular plate.
  • the lower circular plate allows the suction muffler to suck only the refrigerant, preventing it from sucking in oil, and improving the ability to absorb oil upward.
  • Figure 2 shows the installation of the lower circular plate at the end ring of the rotor.
  • the same effect can be obtained by mounting the lower circular plate on the eccentric crankshaft.
  • the lower circular plate can also be mounted on the main bearing 36. At this time, the lower circular plate does not rotate, but the effect is substantially the same as that at the end ring of the rotor.
  • the function of the first opening groove 54.1A and the second opening groove 54.2 are arranged from the inside of the piston to the cylinder suction chamber.
  • the pressure of the cylinder low pressure chamber 55 is lower due to the low pressure refrigerant suction caused by the piston than the internal pressure of the piston (equivalent to the housing pressure).
  • the piston is filled with oil supplied from the center hole 45 of the eccentric crankshaft.
  • the oil in the piston can be supplied to the low pressure chamber of the cylinder through a pressure difference between the piston and the low pressure chamber of the cylinder.
  • Slot break The area and the number of tanks are determined, that is, the oil supply can be adjusted to the minimum required, and the amount of oil discharged from the compressor to the system side is also minimized, and the cylinder compression assembly can be lubricated.
  • the oil discharge hole 83 is opened in the lower bearing, and the oil discharge hole is opened in the cylinder low pressure chamber 55, which utilizes the cylinder low pressure chamber
  • the pressure is slightly lower than the oil pressure of the oil pool, and a certain amount of oil is supplied from the oil pool to the low pressure chamber of the cylinder. Therefore, the same effect as the first opening groove 54.1A and the second opening groove 54.2 of Fig. 2 can be exerted.
  • the oil supplied to the cylinder in this way can not only lubricate the moving parts, but also prevent gas leakage of the moving parts gap to improve the compression efficiency of the compressor.
  • an oil separator 4 may be added between the exhaust pipe 2 and the condenser 5, and the pressure of the oil separator is a high pressure side, The purpose is to return the separated oil to the compressor, and the amount of oil circulating in the system should be as small as possible, but the position of the return oil needs to be considered.
  • the technique provided herein is as follows: The oil is returned to the cylinder compression chamber 53.
  • the cylinder compression chamber has an oil filling hole 51 as shown in Fig. 3.
  • the oil filling hole and the lower bearing are provided with a fuel supply pipe 52, and a casing external oil filler pipe 14 connected thereto. Pay attention to the positioning of the oil hole. It is possible to switch on the moving surface of the piston 61.
  • the hole can be opened only when the cylinder pressure is higher than the suction pressure and lower than the exhaust pressure. Therefore, the oil on the high pressure side separated by the oil separator can be returned to the cylinder compression chamber.
  • the oil returning to the cylinder is exhausted from the cylinder after being lubricated inside the cylinder, and is discharged from the cylinder together with the exhaust refrigerant, reaching the sliding surface of the sliding chamber 63 to lubricate the sliding surface, and then discharged from the exhaust pipe to the outside of the casing to reach the oil separator.
  • the oil is again separated from the high-pressure refrigerant and returned to the cylinder compression chamber, thus forming a circulation system.
  • the oil recovery efficiency of the oil separator is about 90%, about 10% of the oil will be lost on the system side, which is the amount of circulating oil flowing to the system side.
  • the oil flowing into the system side is returned from the compressor suction pipe 11 to the casing, and substantially all of it can be recovered. Therefore, the oil recovery efficiency of the oil separator is about 90%, and the amount of oil supplied by the first opening groove 54.1 and the second opening groove 54.2 or the oil drain hole 83 is only equivalent to the amount of oil discharged to the system side. 10% is ok.
  • the oil separator ensures that the oil returns to the cylinder compression chamber 53 without substantially reducing the refrigeration capacity of the compressor to adequately lubricate the necessary compression components. In addition, it is possible to greatly reduce the amount of oil discharged in the system (10% in the above description).
  • a two-cylinder rotary compressor can be provided with a fuel supply pipe in the intermediate partition 87. 52.
  • the first oil hole 51. 1 and the second oil hole 51.2 are respectively opened for the two cylinders, so that the oil from the oil separator can be distributed in the two cylinders, so that the two cylinder compression chambers can be simultaneously performed. lubricating.
  • the balance hole 81 provided in the cylinder mounting portion of the lower bearing 25 penetrates from the annular (or circular) groove 82 of the lower bearing of the oil pool 44, and the balance is connected to the inside of the piston 61, so that the balance The hole also communicates with the interior of the piston. Due to the severe compressor operating conditions, when the refrigerant in the cylinder compression chamber 53 is abnormally high pressure, the high-pressure refrigerant leaks from the gap above and below the piston into the piston, and the pressure in the piston rises in a short time. If this happens, the pressure on the low-pressure side eccentric crankshaft center hole 45 will also become high, and the oil in the oil pool cannot rise to the center hole, which directly causes the eccentric crankshaft to be worn.
  • the high-pressure refrigerant leaking in the piston can be introduced into the oil pool through the balance hole 81 to prevent the above problem from occurring. It is also possible to arrange the balance hole in the upper bearing or to be disposed on both sides of the upper and lower bearings, and the two-cylinder rotary compressor can also be provided with the balance hole 81 in the intermediate partition 87.
  • the lower circular plate is to prevent oil from flowing into the muffler
  • the oil can be stably supplied through an open groove or an oil drain hole communicating with the low pressure chamber of the cylinder;
  • the oil separator also functions as an external exhaust muffler.
  • the external exhaust muffler can be omitted.

Abstract

A rotary compressor (1) with low pressure in its shell (20) comprises a compressing assembly (21) and an electric motor assembly (22) which are provided in the shell (20); the compressing assembly (21) comprises a cylinder (23), a piston (61) which is provided in the cylinder (23), a sliding vane (62) which is provided in a sliding vane chamber (63) of the cylinder (23), an eccentric crankshaft (26) which drives the piston (61), and an upper bearing (24) and a lower bearing (25) which support the eccentric crankshaft (26); the electric motor assembly (22) comprises a motor rotor (27) and a motor stator (28); the shell (20) is provided with acold media shunt device, which is provided on the top or side of the shell (20), and the cold media shunt device comprises a shunt pipe (9), which is provided with a spring pipe (40) used to adjust the shunting ratio. A suction muffler (35) is provided between the electric motor assembly (22) and the compressing assembly (21), and an annular clearance is provided between the suction muffler (35) and a main bearing (36).

Description

壳体低压的旋转式压缩机及其冷媒、 回油的控制方式和应用 技术领域  Low-pressure rotary compressor with housing and its refrigerant, oil return control method and application
本发明涉及一种旋转式压缩机, 特别是壳体低压的旋转式压缩机及其 冷媒、 回油的控制方式和应用。  The present invention relates to a rotary compressor, and more particularly to a low-pressure rotary compressor of a housing, a refrigerant control method and an application thereof.
背景技术  Background technique
常见的旋转式压缩机 100%都是壳体内压为高压侧, 其原因主要在于: 1 ) 当壳体内压为高压侧时, 由于壳体内压和气缸内压之间的压力差对滑片 和活塞的润滑非常容易, 也就是润滑方面有利; 2 )为将滑片前端紧压住活 塞进行压缩^动, 需要将滑片背压设定为高压, 也就是工作原理的必要性; 3 )从气缸压缩腔排出的润滑油可以在壳体内分离,排油量处理方面有利; 4 ) 吸入管直接连接气缸可以提高气缸容积效率,也就是压缩机效率方面有利等 等。 但是近几年来, 从地球环保、 防止温室效应的观点来看, 使用强可燃性 HC冷媒(碳化氢类冷媒, 比如丙烷), 或者自然冷媒, 比如 0)2的必要性 急剧增加。 如果旋转式压缩机的壳体内压依旧为高压侧, 那么, 从原理上讲 冷媒封入量会增加,对于强可燃性冷媒则由于火灾安全性的原因而不能满足 冷媒封入量的标准, 至于 co2则由于壳体压力明显增加所以存在不符合高 压安全标准等大课题。 发明内容 100% of the common rotary compressors are the high pressure side of the housing. The main reasons are: 1) When the internal pressure of the housing is the high pressure side, due to the pressure difference between the internal pressure of the housing and the internal pressure of the cylinder, the slide and The lubrication of the piston is very easy, that is, it is advantageous in terms of lubrication; 2) In order to compress the front end of the sliding piece against the piston, it is necessary to set the back pressure of the sliding piece to high pressure, that is, the necessity of working principle; 3) The lubricating oil discharged from the cylinder compression chamber can be separated in the casing, which is advantageous in terms of oil discharge processing; 4) The direct connection of the suction pipe to the cylinder can improve the cylinder volumetric efficiency, that is, the compressor efficiency is advantageous. However, in recent years, the necessity of using a strong flammable HC refrigerant (hydrocarbon refrigerant such as propane) or a natural refrigerant such as 0) 2 has increased sharply from the viewpoint of environmental protection and prevention of the greenhouse effect. If the internal pressure of the housing of the rotary compressor is still on the high pressure side, the refrigerant sealing amount will increase in principle, and the strong flammable refrigerant cannot meet the standard of the refrigerant sealing amount due to the safety of the fire, as for the co 2 Since the pressure of the casing is significantly increased, there are major problems such as not meeting the high-pressure safety standards. Summary of the invention
本发明的目的在于提供一种结构简单合理、 安全程度高、 制作成本低、 操作灵活、 润滑性能好、 吐油量少、 压缩效率高、 使用寿命长的壳体低压的 旋转式压缩机及其冷媒、 回油的控制方式和应用, 以克服现有技术中的不足 之处。  The object of the present invention is to provide a low-pressure rotary compressor with a simple and reasonable structure, high safety, low production cost, flexible operation, good lubrication performance, low oil discharge, high compression efficiency and long service life. The control method and application of refrigerant and oil return to overcome the deficiencies in the prior art.
按此目的设计的一种壳体低压的旋转式压缩机, 包括设置在壳体内的 压缩组件和电机组件,压缩组件包括一个及以上的气缸,设置在气缸内的活 塞,设置在气缸滑片槽内的滑片,驱动活塞的偏心曲轴以及支撑偏心曲轴的 上部、 下部轴承, 电机组件包括电机转子和电机定子, 其结构特征是壳体上 设置有冷媒分流装置,该冷媒分流装置设置在壳体的顶部或者侧面,冷媒分 流装置包括分流管, 分流管中设置有调整分流比率的弹簧管。  A low-pressure rotary compressor designed according to the purpose includes a compression assembly and a motor assembly disposed in the housing, the compression assembly including one or more cylinders, a piston disposed in the cylinder, and a cylinder slide groove The inner slide, the eccentric crankshaft driving the piston and the upper and lower bearings supporting the eccentric crankshaft, the motor assembly comprises a motor rotor and a motor stator, and the structural feature is that a cooling device is arranged on the housing, and the refrigerant flow dividing device is arranged in the housing The top or side of the refrigerant shunt device includes a shunt tube in which a spring tube that adjusts the split ratio is disposed.
所述的电机组件与压缩组件之间设置有吸气消声器, 吸气消声器和主 轴承之间设置有环向间隙, 和 /或电机转子或偏心曲轴或上部轴承上设置有  An air suction muffler is disposed between the motor assembly and the compression assembly, a circumferential gap is disposed between the suction muffler and the main bearing, and/or a motor rotor or an eccentric crankshaft or an upper bearing is disposed
确认本 圆板, 圆板覆盖吸气消声器中设置的吸入孔, 和 /或电机转子和电机定子之 间设置有小间隙, 和 /或电机定子和壳体之间设置的间隙与电机上部空间部 相连通; 和 /或上部轴承中设置有第三吸入孔, 该第三吸入孔与吸气消声器 和环向间隙相连通; 和 /或气缸中设置有两个吸入孔, 分别为设置在上部轴 承竖直方向上的第一吸入孔和气缸侧面水平方向上的第二吸入孔,第一吸入 孔和第三吸入孔相连通, 第一吸入孔和第二吸入孔相连通。 Confirmation a circular plate, the circular plate covers the suction hole provided in the suction muffler, and/or a small gap is provided between the motor rotor and the motor stator, and/or a gap provided between the motor stator and the casing is connected to the upper space portion of the motor And/or a third suction hole is provided in the upper bearing, the third suction hole is in communication with the suction muffler and the hoop clearance; and/or two suction holes are provided in the cylinder, respectively, which are disposed in the upper bearing vertical The first suction hole in the direction and the second suction hole in the horizontal direction of the cylinder side surface, the first suction hole and the third suction hole communicate with each other, and the first suction hole and the second suction hole communicate with each other.
所述的气缸的高压侧设置有排气孔, 该排气孔与设置在壳体内的排气 消声腔相连通,排气消声器腔设置在气缸排气孔和设置在壳体上的排气管之 间, 排气消声器腔由上部、 下部轴承和 /或气缸共同围成, 排气消声器腔中 设置有排气阀和排气罔限位板,排气阀和 /或排气限位板为 U字形或 V字形, 和 /或气缸的滑片腔与排气管相连通,  The high pressure side of the cylinder is provided with a venting hole communicating with an exhaust muffling cavity provided in the casing, the exhaust muffler cavity being disposed at the cylinder venting hole and the exhaust pipe disposed on the casing Between the exhaust muffler chamber and the upper and lower bearings and/or the cylinder, the exhaust muffler chamber is provided with an exhaust valve and an exhaust 罔 limit plate, and the exhaust valve and/or the exhaust limit plate are U-shaped or V-shaped, and / or the sliding chamber of the cylinder is connected to the exhaust pipe,
所述的売体内设置有平衡孔, 该平衡孔设置在上部轴承和 /或下部轴承 和 /或中间隔板上, 与活塞内部相连通, 和 /或上部轴承和下部轴承上设置有 环形槽, 环形槽与活塞内部相连通, 平衡孔与环形槽相连通, 和 /或压缩机 外设置有油分离器,油分离器依次通过壳体外的注油管和壳体内的供油管与 气缸相连通;供油管通过设置在上部轴承或下部轴承上的注油孔与气缸相连 通,或供油管分别通过设置在两气缸之间的中间隔板上的第一供油孔和第二 供油孔与第一气缸和第二气缸相连通。  The balance body is provided with a balance hole disposed on the upper bearing and/or the lower bearing and/or the intermediate partition plate, communicating with the inside of the piston, and/or the upper bearing and the lower bearing are provided with an annular groove, The annular groove communicates with the inside of the piston, the balance hole communicates with the annular groove, and/or the oil separator is disposed outside the compressor, and the oil separator is sequentially connected to the cylinder through the oil injection pipe outside the casing and the oil supply pipe in the casing; The oil supply pipe communicates with the cylinder through an oil injection hole provided on the upper bearing or the lower bearing, or the oil supply pipe passes through the first oil supply hole and the second oil supply hole respectively disposed on the intermediate partition plate between the two cylinders. The first cylinder and the second cylinder are in communication.
所述的电机转子的端环上设置有上部圆板和 /或下部圆板,上部圆板和 / 或下部圆板上设置有圆孔,下部圆板的圆孔与主轴承之间设置有间隙,端环、 偏心曲轴和上部圆板围成空间部, 偏心曲轴上设置有横孔与空间部相连通, 设置在偏心曲轴上的中心孔顶端与横孔相连通, 偏心曲轴底端设置有油泵, 油泵底端开口于壳体底部的油池内, 中心孔与油泵相连通, 和 /或主轴承的 内侧面上设置有螺旋形油槽, 该油槽顶端开口于空间部, 和 /或上部轴承和 下部轴承位于活塞运动面上分别设置有第一开口槽和第二开口槽。  The end ring of the motor rotor is provided with an upper circular plate and/or a lower circular plate, and the upper circular plate and/or the lower circular plate are provided with a circular hole, and a gap is formed between the circular hole of the lower circular plate and the main bearing. The end ring, the eccentric crankshaft and the upper circular plate enclose a space portion, and the eccentric crankshaft is provided with a transverse hole communicating with the space portion, and the top end of the central hole disposed on the eccentric crankshaft communicates with the transverse hole, and the bottom end of the eccentric crankshaft is provided with an oil pump The bottom end of the oil pump is open in the oil pool at the bottom of the casing, the central hole is connected with the oil pump, and/or the inner surface of the main bearing is provided with a spiral oil groove, the top end of the oil groove is open to the space portion, and/or the upper bearing and the lower portion The bearing is disposed on the moving surface of the piston with a first opening slot and a second opening slot, respectively.
一种壳体低压的旋转式压缩机的冷媒控制方式, 其特征是将进入压缩 机的低压冷媒分流为两支路及以上,其中一支路通过壳体内部进行热交换后 再进入气缸, 另一支路直接进入气缸, 两支路中的冷媒被压缩前合流。  A refrigerant control method for a low-pressure rotary compressor of a casing, characterized in that a low-pressure refrigerant entering a compressor is branched into two branches and above, one of which passes through the inside of the casing for heat exchange and then enters the cylinder, and One road enters the cylinder directly, and the refrigerant in the two branches merges before being compressed.
另一种壳体低压的旋转式压缩机的冷媒控制方式, 其特征是所述的压 缩机内设置有两个及以上的气缸,将进入压缩机的低压冷媒分流为两支路及 以上,其中一支路直接进入一个气缸,另一支路通过壳体内部进行热交换后 再进入到另一个气缸。  Another refrigerant control method for a low-pressure rotary compressor of a casing, characterized in that two or more cylinders are arranged in the compressor, and the low-pressure refrigerant entering the compressor is divided into two branches and above, wherein One road enters one cylinder directly, and the other branch exchanges heat through the inside of the casing before entering another cylinder.
所述的压缩机上设置有低压冷媒分流装置, 通过该装置调整各支路中 低压冷媒的流量比例。 The compressor is provided with a low-pressure refrigerant flow dividing device, and the branches are adjusted by the device The flow ratio of low pressure refrigerant.
所述的冷媒为汽液两态时, 通过汽液分离装置分离出液态和气态部分, 液态冷媒先进入壳体内部进行热交换后再进入气缸,气态冷媒则直接进入气 缸。  When the refrigerant is in vapor-liquid two-state, the liquid and gaseous portions are separated by the vapor-liquid separation device, and the liquid refrigerant first enters the inside of the casing for heat exchange and then enters the cylinder, and the gaseous refrigerant directly enters the cylinder.
一种壳体低压的旋转式压缩机的回油控制方式, 其特征是从压缩机外 部的油分离器直接向气缸压缩腔回油,或者通过设置在两气缸之间的隔板间 接向两个气缸内回油,或者从压缩机内的油池或经过贯通活塞内部的孔或槽 向气缸低压部分或吸入回路供油,  A returning oil control method for a low-pressure rotary compressor of a casing, characterized in that oil is directly returned from the oil separator outside the compressor to the cylinder compression chamber, or indirectly through two partitions disposed between the two cylinders Returning oil to the cylinder, or supplying oil to the low pressure part of the cylinder or the suction circuit from the oil pool in the compressor or through a hole or groove penetrating the inside of the piston.
一种壳体低压的旋转式压缩机的应用, 可采用 HCFC冷媒、 HFC冷媒、 HC冷媒及 C02冷媒。 For the application of a low-pressure rotary compressor of a casing, HCFC refrigerant, HFC refrigerant, HC refrigerant and C0 2 refrigerant can be used.
本发明通过将旋转式压缩机的壳体内部压力设置为低压侧而解决了上 述技术背景中的基本课题, 实现 HC冷媒, C02等冷媒的安全使用, 达到保 护地球环境的目的,也解决了长期以来将壳体内部压力作为低压侧所面临的 课题: 即压缩机的润滑性差、 效率低、 吐油量大, 还提供了具体可行且成本 低廉的方法。 The present invention solves the basic problem in the above technical background by setting the internal pressure of the casing of the rotary compressor to the low pressure side, and realizes the safe use of the HC refrigerant, the refrigerant such as C0 2, and the purpose of protecting the global environment, and also solves the problem. The internal pressure of the casing has long been a problem faced by the low pressure side: that is, the compressor has poor lubricity, low efficiency, and large oil discharge, and provides a concrete and feasible method.
本发明为将吸入冷媒的过热控制为最小限, 提供了分流低压吸入冷媒 的控制方法, 使其既能被吸入气缸中, 又能防止压缩机效率降低, 并且也提 供了如何在设置有密封排气消声腔的壳体内,避免发生壳体冷媒的过热的控 制方法。  The present invention provides a control method for diverting the low-pressure suction refrigerant so as to be sucked into the cylinder and prevent the compressor from being reduced in efficiency, and also provides a seal row in the arrangement for controlling the superheat of the suction refrigerant to a minimum. In the housing of the air anechoic chamber, a control method for preventing overheating of the housing refrigerant is avoided.
本发明提供润滑油控制方法不仅可润滑压缩机内的全部运动零部件, 还减少了从压缩机内向外排出的吐油量, 降低了能耗。  The present invention provides a lubricating oil control method which not only lubricates all moving parts in the compressor, but also reduces the amount of oil discharged from the inside of the compressor and reduces energy consumption.
本发明与目前的壳体高压的旋转式压缩机进行比较, 在制造成本方面 也有较大优势。  Compared with the current high-pressure rotary compressor of the casing, the present invention also has a great advantage in terms of manufacturing cost.
本发明不仅仅有利于使用符合国际社会需要的 HC类冷媒和 C02冷媒 等, 也可以运用于目前的氟里昂类冷媒中, 其适用范围比较广。 The invention not only facilitates the use of HC-type refrigerants and C0 2 refrigerants which meet the needs of the international community, but also can be applied to the current Freon-type refrigerants, and has a wide application range.
附图说明  DRAWINGS
图 1为本发明一实施例的系统循环结构示意图。  FIG. 1 is a schematic diagram of a system loop structure according to an embodiment of the present invention.
图 2为本发明一实施例的剖视结构示意图。  2 is a cross-sectional structural view of an embodiment of the present invention.
图 3为图 2的 X- X剖视结构示意图。  Figure 3 is a schematic cross-sectional view of the X-X of Figure 2;
图 4为排气阀的放大立体结构示意图。  4 is a schematic enlarged perspective view of the exhaust valve.
图 5为图 3的 T-S剖视放大结构示意图。  Fig. 5 is a schematic enlarged plan view showing the T-S of Fig. 3;
图 6为图 2的局部剖视结构示意图。  Figure 6 is a partial cross-sectional structural view of Figure 2.
图 7为图 6的另一实施例局部剖视结构示意图。 W FIG. 7 is a partial cross-sectional structural view of another embodiment of FIG. 6. FIG. W
图 8为本发明另一实施例的剖视结构示意图。 Figure 8 is a cross-sectional structural view showing another embodiment of the present invention.
图 9为汽液分离装置的剖视放大结构示意图。  Figure 9 is a schematic cross-sectional enlarged view of the vapor-liquid separation device.
图 10为本发明又一实施例的剖视结构示意图。  FIG. 10 is a cross-sectional structural view showing still another embodiment of the present invention.
具体实施方式  detailed description
下面结合附图及实施例对本发明作进一步描述。  The invention is further described below in conjunction with the drawings and embodiments.
图中: 1为压缩机, 2为排气管, 3为排气消声器, 4为油分离器, 5为 冷凝器, 6为膨胀阀, 7为蒸发器, 8为低压回路, 9为分流管, 10为分叉 回路, 11为吸入管, 12为排气孔, 13为排气消声器腔, 14为注油管, 20 为壳体, 21为压缩组件, 22为电机, 23为气缸, 24为上部轴承, 25为下 部轴承, 26为偏心曲轴, 27为电机转子, 28为电机定子, 31为第一吸入孔, 32为第二吸入孔, 34为第三吸入孔, 35为吸气消声器, 36为主轴承, 37 为环向间隙, 38为端环, 39为下部圆板, 40为弹簧管, 41为上部圆板, 42. 1 为上部电机线圈, 42. 2为下部电机线圈, 43为油泵, 44为油池, 45为中心 孔, 46为横孔, 47为空间部, 48为螺旋形油槽, 49为液态冷媒, 50为气 体冷媒, 51为注油孔, 51. 1为第一注油孔, 51. 2为第二注油孔, 52为供油 管, 53为气缸压缩腔, 54. 1为第一开口槽, 54. 2为第二开口槽, 55为气缸 低压腔, 61为活塞, 62为滑片, 63为滑片腔, 64为滑片弹簧, 71为排气 阀, 72为排气限位板, 73为连通槽, 81为平衡孔, 82为槽, 83为排油孔,- 84为电机定子外周间隙, 85为定子铁心, 86为小间隙, 87为隔板, 88为 下部空间部, 89为上部空间部, 91. 1为上部气缸, 91. 2为下部气缸, 93 为平衡块, 98为气液分离装置。  In the figure: 1 is the compressor, 2 is the exhaust pipe, 3 is the exhaust muffler, 4 is the oil separator, 5 is the condenser, 6 is the expansion valve, 7 is the evaporator, 8 is the low pressure circuit, 9 is the shunt pipe 10 is a bifurcation circuit, 11 is a suction pipe, 12 is a vent hole, 13 is an exhaust muffler cavity, 14 is a fuel injection pipe, 20 is a casing, 21 is a compression assembly, 22 is a motor, 23 is a cylinder, 24 is The upper bearing, 25 is the lower bearing, 26 is the eccentric crankshaft, 27 is the motor rotor, 28 is the motor stator, 31 is the first suction hole, 32 is the second suction hole, 34 is the third suction hole, and 35 is the suction muffler. 36 is the main bearing, 37 is the circumferential clearance, 38 is the end ring, 39 is the lower circular plate, 40 is the spring tube, 41 is the upper circular plate, 42. 1 is the upper motor coil, 42. 2 is the lower motor coil, 43 For the oil pump, 44 is the oil pool, 45 is the center hole, 46 is the transverse hole, 47 is the space part, 48 is the spiral oil groove, 49 is the liquid refrigerant, 50 is the gas refrigerant, 51 is the oil hole, 51. 1 is the first Oil injection hole, 51. 2 is the second oil hole, 52 is the oil supply pipe, 53 is the cylinder compression cavity, 54. 1 is the first Open slot, 54. 2 is the second open slot, 55 is the cylinder low pressure chamber, 61 is the piston, 62 is the sliding vane, 63 is the sliding vane cavity, 64 is the vane spring, 71 is the exhaust valve, 72 is the exhaust limit Position plate, 73 is the communication groove, 81 is the balance hole, 82 is the groove, 83 is the oil drain hole, -84 is the motor stator outer circumference gap, 85 is the stator core, 86 is the small gap, 87 is the partition, 88 is the lower space For the upper space part, 91. 1 is the upper cylinder, 91. 2 is the lower cylinder, 93 is the balance block, and 98 is the gas-liquid separation device.
参见图 1 ,经压缩机 1压缩的高压冷媒通过排气管 2依次经过外部的排 气消声器 3和油分离器 4后到达冷凝器 5, 经冷凝器冷凝后的冷媒依次经过 膨胀阀 6和蒸发器 7后,成为低压冷媒。低压冷媒从低压回路 8进入分流管 9 ,分流管 9上设置有两个回路: 其中一个回路是直接进入压缩机壳体内部, 然后被吸入气缸; 另一个回路是沿分叉回路 10到达吸入管 11, 吸入管直接 与气缸相通, 由于被吸入冷媒中的一部分是先被吸入売体内部, 而后被吸入 进气缸中, 所以壳体压力为低压侧。 接着, 流入壳体内部的低压冷媒和从分 叉回路 10直接流入气缸的低压冷媒在进入气缸被压缩前合流, 在气缸内部 被压缩的高压冷媒通过压缩机内部的排气消声器、从排气管 2直接向壳体外 部排气。含润滑油(以下简称油)的高压冷媒通过外部的排气消声器 3和油 分离器 4后, 再次到达冷凝器 5 , 于是就形成一个循环, 此时的压缩机起到 了构建循环系统的作用。 由于这种壳体低压的旋转式压缩机直接将高压冷媒向壳体外部排出, 其排出冷媒中含的油在壳体内不能分离,故此,本提供的设计方案中设置了 油分离器, 通过油分离器分离出来的油将通过注油管 14流向气缸内的压缩 壳体压力为低压侧是本发明中的重要组成部分, 这种系统可广泛应用 于空调、 冷冻设备。 Referring to Fig. 1, the high-pressure refrigerant compressed by the compressor 1 passes through the exhaust muffler 3 and the oil separator 4 through the exhaust pipe 2 to reach the condenser 5, and the refrigerant condensed by the condenser sequentially passes through the expansion valve 6 and evaporates. After the device 7, it becomes a low pressure refrigerant. The low pressure refrigerant enters the shunt tube 9 from the low pressure circuit 8, and the shunt tube 9 is provided with two circuits: one of the circuits directly enters the inside of the compressor casing and is then drawn into the cylinder; the other circuit is passed along the bifurcation circuit 10 to the suction pipe. 11. The suction pipe is directly connected to the cylinder. Since a part of the sucked refrigerant is first sucked into the inside of the body and then sucked into the cylinder, the casing pressure is the low pressure side. Then, the low-pressure refrigerant flowing into the inside of the casing and the low-pressure refrigerant directly flowing into the cylinder from the branching circuit 10 are merged before the cylinder is compressed, and the high-pressure refrigerant compressed inside the cylinder passes through the exhaust muffler inside the compressor and the exhaust pipe. 2 Vent directly to the outside of the housing. The high-pressure refrigerant containing lubricating oil (hereinafter referred to as oil) passes through the external exhaust muffler 3 and the oil separator 4, and reaches the condenser 5 again, thereby forming a cycle in which the compressor functions to construct a circulation system. Since the low-pressure rotary compressor of the casing directly discharges the high-pressure refrigerant to the outside of the casing, the oil contained in the refrigerant discharged from the refrigerant cannot be separated in the casing, and therefore, the oil separator is provided in the design provided by the oil. The oil separated by the separator will flow through the oil filler pipe 14 to the compression chamber in the cylinder. The pressure on the low pressure side is an important part of the present invention, and the system can be widely applied to air conditioners and refrigeration equipment.
参见图 2,该图可以清楚了解吸入管 11、排气孔 12和排气消声器腔 13 的具体情况。 壳体 20内设置有压缩组件 21和电机组件 22。 压缩组件包括 气缸 23、 上部轴承 24、 下部轴承 25以及被这些轴承支撑的偏心曲轴 26..; 电机组件包括电机转子 27和电机定子 28, 被偏心曲轴 26固定的电机转子 27由固定在壳体内的电机定子 28驱动。  Referring to Figure 2, the specifics of the suction pipe 11, the venting opening 12 and the exhaust muffler chamber 13 can be clearly understood. A compression assembly 21 and a motor assembly 22 are disposed within the housing 20. The compression assembly includes a cylinder 23, an upper bearing 24, a lower bearing 25, and an eccentric crankshaft 26 supported by the bearings. The motor assembly includes a motor rotor 27 and a motor stator 28, and the motor rotor 27 fixed by the eccentric crankshaft 26 is fixed in the housing. The motor stator 28 is driven.
气缸 23中设置有 2个吸入孔, 即设置在上部轴承 24中竖直方向上的 第一吸入孔 31和气缸侧面水平方向上的第二吸入孔 32 , 第一吸入孔 31和 上部轴承 24的第三吸入孔 34连通,第二吸入孔 32与第一吸入孔 31相连通。  The cylinder 23 is provided with two suction holes, that is, a first suction hole 31 disposed in the vertical direction of the upper bearing 24 and a second suction hole 32 in the horizontal direction of the cylinder side, the first suction hole 31 and the upper bearing 24 The third suction hole 34 communicates, and the second suction hole 32 communicates with the first suction hole 31.
另一方面, 壳体上部安装的分流管 9使低压回路的冷媒按两个方向, 即箭头 A和 B指示的方向分流。分流管 9的功能是在液体和气体的混合冷媒 流入时, 主要使液体冷媒沿箭头 A方向、 气体冷媒沿箭头 B方向分流。 分流 管 9中压入弹簧管 40, 该弹簧管将起到调整分流比率和进一步发挥气液分 离功能的作用, 实际搡作时, 可调整弹簧管的安装高度 h。  On the other hand, the shunt tube 9 mounted on the upper portion of the casing divides the refrigerant of the low pressure circuit in two directions, i.e., directions indicated by arrows A and B. The function of the branch pipe 9 is to mainly cause the liquid refrigerant to flow in the direction of the arrow A and the gas refrigerant in the direction of the arrow B when the mixed refrigerant of the liquid and the gas flows in. The spring tube 40 is press-fitted into the shunt tube 9, which functions to adjust the split ratio and further exert the gas-liquid separation function. When the actual operation is performed, the installation height h of the spring tube can be adjusted.
第三吸入孔 34开口于上部轴承中安装的吸气消声器 35 ,吸气消声器不 光可以降低气缸吸气脉动引起的噪音, 因为主轴承 36外侧之间的圆形间隙 37是吸气消声器的入口, 该间隙还起到吸入流入到壳体中全部冷媒的作用。  The third suction hole 34 is open to the suction muffler 35 installed in the upper bearing, and the suction muffler can not only reduce the noise caused by the suction pulsation of the cylinder, because the circular gap 37 between the outer sides of the main bearing 36 is the inlet of the suction muffler. This gap also serves to absorb all of the refrigerant flowing into the casing.
电机转子 27的端环 38上安装了下部圆板 39, 下部圆板'的中间设置有 圆形孔, 该圆形孔和主轴承 36之间设置有小间隙, 所以下部圆板可以和电 机转子一起旋转。 该下部圆板 39具有减小压缩机吐油量、 提高偏心曲轴吸 油效果的作用, 电机转子的上部也安装了同样的上部圆板 41。 为了消除活 塞 61的不平衡质量, 通常需要在端环 38上安装平衡块, 图 1中省略了平衡 块。 实际的设计中如图 7中所示在端环 38平衡块 83之间, 推荐使用铆钉固 定, 使平衡块同时和下部圆板 39—起和端环实现一体化的方式。  A lower circular plate 39 is mounted on the end ring 38 of the motor rotor 27, and a circular hole is provided in the middle of the lower circular plate, and a small gap is provided between the circular hole and the main bearing 36, so that the lower circular plate can be combined with the motor rotor Rotate together. The lower circular plate 39 has a function of reducing the amount of oil discharged from the compressor and improving the oil absorption effect of the eccentric crankshaft, and the same upper circular plate 41 is attached to the upper portion of the rotor of the motor. In order to eliminate the unbalanced mass of the piston 61, it is usually necessary to mount a weight on the end ring 38, and the balance block is omitted in Fig. 1. In the actual design, as shown in Fig. 7, between the end ring 38 balance blocks 83, it is recommended to use a rivet fixing to integrate the balance block with the lower circular plate 39 and the end ring at the same time.
偏心曲轴 26下端安装的油泵 43前端在油池 44处开设有孔。 在偏心曲 轴中心部设置的中心孔 45在电机转子的下端附近与横孔 46连通。横孔在端 环 38和下部圆板 39之间形成的空间部 47开孔。另外, 主轴承 36的内侧运 动面上设置的螺旋性油槽 48也同样在空间部位 47开孔。 N2008/000244 A front end of the oil pump 43 mounted at the lower end of the eccentric crankshaft 26 is provided with a hole at the oil pool 44. A center hole 45 provided at a central portion of the eccentric crankshaft communicates with the lateral hole 46 near the lower end of the motor rotor. The lateral hole defines a space portion 47 formed between the end ring 38 and the lower circular plate 39. Further, the spiral oil groove 48 provided on the inner moving surface of the main bearing 36 is also opened at the space portion 47. N2008/000244
下部轴承 25上设置有注油孔 51 , 该注油孔和供油管 52连通, 而且和 油分离器 4连通所以可以将油分离器分离出的油返回气缸压缩腔 53中。 The lower bearing 25 is provided with an oil filling hole 51 which communicates with the oil supply pipe 52 and communicates with the oil separator 4 so that the oil separated by the oil separator can be returned to the cylinder compression chamber 53 .
注油孔在活塞旋转的时候, 在活塞下部平面打开和关闭, 虽然只在气 缸压缩腔中开孔就可以将油返回压缩中的冷媒中, 但不能在气缸低压侧开 孔,所以油不能返回气缸低压侧。气缸位于上部轴承和下部轴承的活塞运动 面上设置有第一开口槽 54. 1和第二开口槽 54. 2 , 该开口槽是将活塞 61内 的油供给气缸低压腔 55的油通道。 When the piston rotates, the oil hole opens and closes in the lower plane of the piston. Although the oil can be returned to the compressed refrigerant only by opening the hole in the cylinder compression chamber, the hole cannot be opened on the low pressure side of the cylinder, so the oil cannot return to the cylinder. Low pressure side. Movement in the upper bearing surface of the piston cylinder and the lower bearing is provided with a first opening and a second opening groove 54.1 54.2 groove, which groove is open to the low pressure oil supplied to the cylinder chamber 61 in the piston oil passage 55.
参见图 3, 气缸 23内部的活塞 61被偏心曲轴驱动进行偏心旋转运动, 滑片槽中设置有滑片 62 , 其背部的空间部为滑片腔 63。 旋转式压缩机需要 使滑片前端追随并压紧在活塞外壁上,所以本发明中的壳体低压的旋转式压 缩机中也需要使滑片腔为高压侧, 因此, 滑片腔被密封, 冷媒不会泄漏到低 压侧的壳体内部。 滑片腔内置滑片弹簧 64。  Referring to Fig. 3, the piston 61 inside the cylinder 23 is driven by the eccentric crankshaft to perform an eccentric rotation motion, and a vane 62 is disposed in the vane groove, and a space portion of the back portion is a vane chamber 63. The rotary compressor needs to make the front end of the sliding plate follow and press on the outer wall of the piston. Therefore, in the low-pressure rotary compressor of the casing of the present invention, the sliding chamber is also required to be on the high pressure side, and therefore, the sliding chamber is sealed. The refrigerant does not leak into the inside of the housing on the low pressure side. The vane cavity has a built-in vane spring 64.
参见图 3和图 4 , 气缸的高压侧设置有排气孔 12, 连通近四角形的排 气消声器腔 13, 排气消声器腔内部设置有排气阀 71和限制排气阀动作的排 气限位板 72。 排气阀 71和排气限位板为 U字形或 V字形, 在有限容积的排 气消声器腔内也可以将其延长。对于小的排气消声器腔中, 排气阀的动作也 可以设计得较富余。 另外, U字形限位板是有弹力的板簧, 在四角形的排气 消声器腔内壁和上下轴承的气缸安装面定位,并且排气阀被有弹力的排气限 位板固定。 在排气消声器腔 13处设置有连通槽 73, 排气消声器室中的冷媒 可以通过连通槽流到滑片腔 63中。 .  Referring to FIG. 3 and FIG. 4, the high pressure side of the cylinder is provided with an exhaust hole 12 communicating with the nearly quadrangular exhaust muffler chamber 13. The exhaust muffler chamber is internally provided with an exhaust valve 71 and an exhaust limit for restricting the operation of the exhaust valve. Board 72. The exhaust valve 71 and the exhaust limit plate are U-shaped or V-shaped and can be extended in a limited-volume exhaust muffler chamber. For small exhaust muffler chambers, the action of the exhaust valve can also be designed to be more than adequate. Further, the U-shaped stopper is a resilient leaf spring which is positioned on the inner wall of the quadrangular exhaust muffler chamber and the cylinder mounting surface of the upper and lower bearings, and the exhaust valve is fixed by the elastic exhaust stopper. A communication groove 73 is provided at the exhaust muffler chamber 13, and the refrigerant in the exhaust muffler chamber can flow into the vane chamber 63 through the communication groove. .
参见图 5 , 该图为滑片腔 63和排气管 2的具体安装位置。 上部轴承 24 和下部轴承 25密封的滑片腔背部设置有滑片弹簧, 该滑片弹簧的加工孔设 置有排气管连接。 通过以上的方法, 被气缸压缩后排入排气消声器腔 13内 的高压冷媒通过连通槽 73流入滑片腔 63, 从排气管 开始到达压缩机外部 配置的外部排气消声器 3。 外部排气消声器为圆简状的容器, 尽量安装在接 近排气管的位置, 排气消声器内的高压冷媒移至系统的冷凝器 5。 油分离器 4配置在排气消声器和冷凝器之间, 油分离器 4具有外部排气消声器 3的功 能, 在外部排气消声器的位置安装油分离器 4则可以省去外部排气消声器。 可以利用滑片弹簧加工孔连接排气管 2, 具有用排气管密封滑片室的优点。 下面简述电机冷却和压缩机效率的改善。  Referring to Figure 5, the figure shows the specific mounting position of the vane chamber 63 and the exhaust pipe 2. A slider spring is disposed on the back of the slider chamber sealed by the upper bearing 24 and the lower bearing 25. The machining hole of the slider spring is provided with an exhaust pipe connection. According to the above method, the high-pressure refrigerant discharged into the exhaust muffler chamber 13 after being compressed by the cylinder flows into the vane chamber 63 through the communication groove 73, and from the exhaust pipe to the external exhaust muffler 3 disposed outside the compressor. The external exhaust muffler is a round-shaped container, installed as close as possible to the exhaust pipe, and the high-pressure refrigerant in the exhaust muffler is moved to the condenser 5 of the system. The oil separator 4 is disposed between the exhaust muffler and the condenser, and the oil separator 4 has the function of the external exhaust muffler 3, and the external exhaust muffler can be omitted by installing the oil separator 4 at the position of the external exhaust muffler. The exhaust pipe 2 can be connected by a slide spring machining hole, which has the advantage of sealing the slide chamber with an exhaust pipe. The improvement of motor cooling and compressor efficiency is briefly described below.
第一. 压缩机一启动, 压缩组件 21就开始吸入低压冷媒。 蒸发器 7的 冷媒从低压冷媒回路 8向分流管 9流动,在这里分流为 2个回路, 首先沿箭 头 A方向分流的冷媒流入壳体内的上部空间部 89 , 由上部圆板 41整流后向 上部电机线圏 42. 1的内周分散, 并有效地冷却电机线圏。 之后、 低压冷媒 主要通过电机内部或小间隙 86移至电机组件 22和压缩组件 21间形成的下 部空间部 88。低压冷媒中途冷却电机内部的线圈和电机或壳体上附着的油。 接着, 低压冷媒冷却下部电机线圏 42. 2 , 从圆形间隙 37向吸气消声器 35 吸入。 吸气消声器内的冷媒从第一吸入孔 34通过第二吸入孔 32流入气缸, 经过分流管 9沿箭头 B方'向分流的低压气体直接流入第二吸入孔 32 , 和前 述流入第一吸入孔到达第二吸入孔 32的冷媒合流后被吸入气缸进行压缩。 First, as soon as the compressor is started, the compression assembly 21 begins to draw in the low pressure refrigerant. The refrigerant of the evaporator 7 flows from the low-pressure refrigerant circuit 8 to the branch pipe 9, where it is branched into two circuits, first along the arrow The refrigerant shunted in the direction of the head A flows into the upper space portion 89 in the casing, is rectified by the upper circular plate 41, and is dispersed in the inner circumference of the upper motor coil 42. 1 to effectively cool the motor coil. Thereafter, the low pressure refrigerant is moved mainly through the inside of the motor or the small gap 86 to the lower space portion 88 formed between the motor assembly 22 and the compression assembly 21. The low-pressure refrigerant cools the coil inside the motor and the oil attached to the motor or the casing in the middle. Next, the low-pressure refrigerant cools the lower motor line 圏42. 2 and draws it from the circular gap 37 to the suction muffler 35. The refrigerant in the suction muffler flows from the first suction hole 34 through the second suction hole 32 into the cylinder, and the low-pressure gas that has branched through the branch pipe 9 in the direction of the arrow B flows directly into the second suction hole 32, and flows into the first suction hole. The refrigerant reaching the second suction hole 32 merges and is sucked into the cylinder to be compressed.
为了将低压冷媒分流至壳体内尽可能均匀地冷却温度最高的电机整个 线圈,要使冷媒从电机上部线圈 42. 1向电机下部线圈 42. 2冷媒流动, 即冷 媒向电机内径中心部流动是最佳方案。 在下部电机线圈 42. 2的内侧配置吸 气消声器, 并将间隙 37置于吸气消声器中央部做成圆孔是最佳的设计。  In order to distribute the low-pressure refrigerant to the entire coil of the motor with the highest temperature as uniformly as possible, the refrigerant flows from the upper coil of the motor 42. 1 to the lower coil of the motor 42. 2, the refrigerant flows, that is, the refrigerant flows to the center of the inner diameter of the motor. Good plan. It is an optimum design to arrange the suction muffler on the inner side of the lower motor coil 42.2 and to place the gap 37 in the center of the suction muffler to make a circular hole.
本发明不仅仅是引导冷媒从电机上部线圈向电机下部线圈流动, 还可 以通过调整间隙的配置和形状,形成均匀的冷媒流动, 以减少电机线圈的温 度离散性。  The invention not only guides the flow of the refrigerant from the upper coil of the motor to the lower coil of the motor, but also adjusts the arrangement and shape of the gap to form a uniform flow of the refrigerant to reduce the temperature dispersion of the motor coil.
第二. 在这里说明从箭头 A方向向壳体内流入的低压冷媒的作用。 如 果电机线圈和油得不到冷媒冷却, 那么其温度会上升到 150°C以上、 会产生' 线圈烧损和油老化的问题。流入壳体内的低压冷媒的温度通常是 5 ~ 20°C左 右, 通过冷却电机和油, 使它们保持合适的温度范围 50 ~ 110°C。 由于热交 换, 低压冷媒温度会上升, 当低压冷媒温度上升时, 压缩机冷媒吸入效率会 就降低, 降低的效率和吸入冷媒的温度上升率呈一定比率, 当吸入冷媒异常 过热时, 冷冻能力最大会低 10%左右。 由于沿箭头 B方向分流的低压气体流 入第二吸入孔时基本上不改变温度,因此不会发生压缩机冷冻能力减少的问 题。沿箭头 A分流的低压冷媒在流入气缸之前和沿箭头 B方向来的冷媒合流, 故气缸中吸入的冷媒温度由分流比率和压缩机运行条件等决定。  Second, the action of the low-pressure refrigerant flowing into the casing from the direction of the arrow A will be described here. If the motor coil and oil are not cooled by the refrigerant, the temperature will rise above 150 °C, which will cause 'coil burning and oil aging problems. The temperature of the low-pressure refrigerant flowing into the casing is usually around 5 ~ 20 °C. By cooling the motor and oil, they are kept at a suitable temperature range of 50 ~ 110 °C. Due to heat exchange, the temperature of the low-pressure refrigerant will rise. When the temperature of the low-pressure refrigerant rises, the refrigerant suction efficiency of the compressor will decrease. The reduced efficiency will be proportional to the temperature rise rate of the suction refrigerant. When the suction refrigerant is abnormally overheated, the refrigeration capacity is the largest. Will be about 10% lower. Since the low-pressure gas branched in the direction of the arrow B flows into the second suction port without substantially changing the temperature, the problem that the compressor refrigeration capacity is reduced does not occur. The low-pressure refrigerant branched along the arrow A merges with the refrigerant in the direction of the arrow B before flowing into the cylinder, so the temperature of the refrigerant sucked in the cylinder is determined by the split ratio, the compressor operating conditions, and the like.
由于分流可以降低气缸吸入的冷媒温度, 而不会产生压缩机冷冻能力 大幅减少的问题,还可以防止压缩机效率降低。但是为了不过度冷却电机温 度,最大地发挥压缩机冷冻能力和效率,最好象本文提供技术那样向间接吸 入(箭头 A方向)和直接吸入(箭头 B方向)进行分流。 为了实现从蒸发器 出来的冷媒分流后可以被吸入压缩机气缸中,所以分流的位置并不仅仅局限 于附图中的位置。  Since the splitting can reduce the temperature of the refrigerant sucked by the cylinder without causing a problem that the compressor refrigeration capacity is drastically reduced, the compressor efficiency can be prevented from being lowered. However, in order not to excessively cool the motor temperature and maximize compressor refrigeration capacity and efficiency, it is preferred to split the indirect suction (arrow A direction) and direct suction (arrow B direction) as provided herein. In order to allow the refrigerant from the evaporator to be diverted into the compressor cylinder, the position of the split is not limited to the position in the drawing.
第三. 通过调整弹簧管 40的压入尺寸, 即改变 h的长度, 从而轻松地 改变沿箭头 A方向和沿箭头 B方向流动冷媒的分流比率。另外,低压气体中 混入液体冷媒的条件下, 因为液体冷媒的惯性力大,所以向箭头 A方向流动 的比率增加,而向箭头 B方向的液体冷媒则流动相对困难,所以可以事先防 止从箭头 B方向直接侵入的液体冷媒在气缸内发生液体压缩的问题。由于向 A方向流入的液体冷媒和电机组件等高温部进行热交换后被气化, 故可以防 止从笫一吸入孔 31向气缸内流入液体冷媒。 通常情况下液体冷媒中所合大 量的油由于冷媒本身气化, 故很容易和冷媒分离, 油很容易回收到壳体内的 油池 44中。 Third. By adjusting the press-in size of the spring tube 40, that is, changing the length of h, the split ratio of the flow of the refrigerant in the direction of the arrow A and the direction of the arrow B is easily changed. In addition, in low pressure gas In the case where the liquid refrigerant is mixed, since the inertial force of the liquid refrigerant is large, the ratio of the flow in the direction of the arrow A increases, and the flow of the liquid refrigerant in the direction of the arrow B is relatively difficult. Therefore, the liquid directly invading from the direction of the arrow B can be prevented in advance. The problem of liquid compression in the cylinder occurs in the refrigerant. Since the liquid refrigerant that has flowed in the direction A and the high temperature portion such as the motor unit are heat-exchanged and then vaporized, it is possible to prevent the liquid refrigerant from flowing into the cylinder from the first suction hole 31. Usually, a large amount of oil in the liquid refrigerant is vaporized by the refrigerant itself, so that it is easily separated from the refrigerant, and the oil is easily recovered into the oil pool 44 in the casing.
于是, 弹簧管不仅仅要调整箭头 A方向和箭头 B方向的分流比率, 而 且还担负着分离气体冷媒和液态冷媒的重要作用。 为了更好地实现弾簧管 40的功能, 推荐设置一个可以根据压缩机电机温度或系统环境温度自动调 整分流比率的自动阀。  Therefore, the spring tube not only has to adjust the split ratio of the arrow A direction and the arrow B direction, but also plays an important role in separating the gas refrigerant and the liquid refrigerant. In order to better realize the function of the clarinet 40, it is recommended to set an automatic valve that can automatically adjust the split ratio according to the compressor motor temperature or the system ambient temperature.
第四. 接下来说明压缩机内部的排气回路和壳体内低压冷媒进行热交 换后吸入冷媒过热问题的对策。气缸里吸入的低压冷媒被活塞压缩变成高压 冷媒从排气孔 12进入排气消声器腔 13, 从连通槽 73经过滑片腔 63由排气 管 2排出。 由于滑片腔为高压侧, 故滑片前端可以压紧在活塞外周, 开始压 缩气体的进程。壳体低压的旋转式压缩机的排气消声器腔和滑片腔等排气回 路的温度较高, 通常状况下会达到 110 °C左右, 为了使排气回路和壳体内的 低压冷媒之间的热交换达到最小化, 从而防止压缩机吸入过热的冷媒,提高 压缩机效率。  Fourth, the countermeasures for the problem of overheating of the refrigerant in the exhaust circuit inside the compressor and the low-pressure refrigerant in the casing after heat exchange are explained. The low-pressure refrigerant sucked into the cylinder is compressed by the piston to become a high pressure. The refrigerant enters the exhaust muffler chamber 13 from the exhaust hole 12, and is discharged from the communication passage 73 through the vane chamber 63 through the exhaust pipe 2. Since the vane chamber is on the high pressure side, the front end of the vane can be pressed against the outer circumference of the piston to start the process of compressing the gas. The temperature of the exhaust circuit of the exhaust muffler chamber and the vane chamber of the low-pressure rotary compressor of the casing is relatively high, and usually reaches about 110 °C in order to make the exhaust circuit and the low-pressure refrigerant in the casing. Heat exchange is minimized, thereby preventing the compressor from drawing in overheated refrigerant and increasing compressor efficiency.
本文提供的技术使排气消声器腔容积为所需的最小量, 不光使排气消 声器腔、滑片腔也由上部、下部轴承密封来防止和壳体内低压冷媒的直接接 触。 但是, 当排气消声器腔室容积比较小时, 由于排气脉动引起的噪音会增 加, 其对策是追加外部排气消声器 3扩大消声器总容积以减小压缩机噪音。 另外, 在重视制热的系统设计中, 推荐对外部排气消声器进行隔热处理, 使 对外气 (空气) 的热量损失减少到最小。  The technique provided herein allows the exhaust muffler chamber volume to be the minimum required, not only to seal the exhaust muffler chamber and the vane chamber from the upper and lower bearings to prevent direct contact with the low pressure refrigerant in the housing. However, when the volume of the exhaust muffler chamber is small, the noise due to the exhaust pulsation is increased, and the countermeasure is to add an external exhaust muffler 3 to enlarge the total volume of the muffler to reduce compressor noise. In addition, in the design of systems that emphasize heating, it is recommended to insulate the external exhaust muffler to minimize heat loss from the outside air (air).
第五. 图 8是将分流管 9' 从壳体上部移向壳体侧面, 以减短分叉回路 10' 长度的设计, 该设计中的分流管连接了电机定子外周间隙 84。 由于连 接分流管的外周间隙的下部开孔端被定子铁心 85上安装的端板所关闭, 故 沿箭头 Λ' 方向分流的低压气体从外周间隙向壳体的上部空间流动, 而另一 部分低压气体则沿箭头 B' 流动进入气缸, 所以可以得到和图 2所示分流管 9同等的效果。 这个设计例子中有减短分叉回路 10长度、 降低压缩机髙度 的效果。  Fifth. Fig. 8 is a design in which the shunt tube 9' is moved from the upper portion of the casing to the side of the casing to reduce the length of the branching circuit 10'. The shunt tube in the design is connected to the outer circumferential gap 84 of the motor stator. Since the lower opening end of the peripheral gap connecting the shunt tubes is closed by the end plate mounted on the stator core 85, the low-pressure gas branched in the direction of the arrow Λ' flows from the outer peripheral space to the upper space of the casing, and another portion of the low-pressure gas Then, the arrow B' flows into the cylinder, so that the same effect as the shunt tube 9 shown in Fig. 2 can be obtained. This design example has the effect of reducing the length of the split circuit 10 and reducing the compressor torque.
另外, 作为图 2说明的分流管 9的替代设计, 图 9表示了将气液分离 装置 98安装在系统的低压冷媒回路、 或压缩机吸入回路附近的方法。 从蒸 发器 7出来的气液混合冷媒在气液分离装置中分离为液态冷媒 49和气体冷 媒 50、 液体向箭头 A" 方向、 气体向箭头 方向流动。 其结果如图 2所示 可以得到和图 2所示分流管 9同等的效果。 In addition, as an alternative design of the shunt tube 9 illustrated in Fig. 2, Fig. 9 shows the separation of gas and liquid. The device 98 is mounted in the vicinity of the system's low pressure refrigerant circuit, or compressor suction circuit. The gas-liquid mixed refrigerant from the evaporator 7 is separated into a liquid refrigerant 49 and a gas refrigerant 50 in the gas-liquid separation device, and the liquid flows in the direction of the arrow A" and the gas in the direction of the arrow. The result is shown in Fig. 2. The shunt tube 9 shown in Fig. 2 has the same effect.
笫六. 图 10是在两气缸旋转式压缩机应用分流装置的设计, 该设计采 用将吸入冷媒分流到两个气缸独立吸入的方法。 在图 10中沿箭头 A' " 方 向的低压冷媒在冷却了电机等之后, 通过吸气消声器 35从第三吸入孔 34、 上部气缸 91. 1的第二吸入孔 32向气缸内吸入, 沿箭头 " 方向的低压冷 媒直接吸入下部气缸 91. 2中。 两个气缸独立进行冷媒压缩, 从各自的气缸 排出的高压冷媒从滑片腔到达中隔板 87合流之后, 从连接中隔板的排气管 向系统侧排出。  Figure 6. Figure 10 shows the design of a splitter for a two-cylinder rotary compressor application that uses a separate suction of the suction refrigerant into two cylinders. In Fig. 10, the low-pressure refrigerant in the direction of the arrow A'" is cooled by the motor or the like, and is sucked into the cylinder from the third suction hole 34 and the second suction hole 32 of the upper cylinder 911.1 by the suction muffler 35, along the arrow The low pressure refrigerant in the direction is directly sucked into the lower cylinder 91.2. The two cylinders independently perform refrigerant compression, and the high-pressure refrigerant discharged from the respective cylinders merges from the vane chamber to the intermediate partition plate 87, and then is discharged from the exhaust pipe connected to the intermediate partition to the system side.
通过使两气缸以上的多气筒旋转式压缩机中分流的低压冷媒有选择性 地吸入气缸, 可以同时满足电机冷却和压缩效率提高的要求。  By selectively sucking the low-pressure refrigerant branched in the multi-cylinder rotary compressor of two or more cylinders into the cylinder, the requirements for motor cooling and compression efficiency can be improved at the same time.
现将以上的技术要点归纳如下: 如果压缩机壳体中吸入了所有的低压 冷媒, 那么电机组件温度降低对电机冷却是有利的,但是通过和电机的热交 ^ 换吸入气缸的冷媒温度会升高,冷媒密度会变小, 因此压缩机冷冻能力将会 下降, 即导致压缩机效率降低。  The above technical points are summarized as follows: If all the low-pressure refrigerant is sucked into the compressor casing, the temperature drop of the motor component is beneficial to the cooling of the motor, but the temperature of the refrigerant sucked into the cylinder is increased by the heat exchange with the motor. High, the density of the refrigerant will become smaller, so the compressor refrigeration capacity will be reduced, which will lead to a decrease in compressor efficiency.
针对这一点, 本文提供的技术不光是尽量减小壳体内吸入的冷媒量, 还规定电机温度上升要在允许范围内。至于其余的剩余冷媒则直接吸入气缸 内, 降低气缸吸入的冷媒温度,其结果可以防止低压冷媒温度过度上升问题 或者是冷媒密度过小的问题。因此可以大幅度地改善压缩机冷冻能力降低和 效率降低的状况,为达到该目的本文提供的技术将低压冷媒回路分流为两路 吸入气缸。既可以通过防止排气消声器腔等的高压冷媒回路直接和壳体内的 低压冷媒相接触进行热交换,也可以控制壳体内低压冷媒温度的上升, 防止 压缩机冷冻能力和效率降低的效果。  In response to this, the technique provided in this paper is not only to minimize the amount of refrigerant sucked in the casing, but also to specify that the temperature rise of the motor is within the allowable range. As for the remaining residual refrigerant, it is directly sucked into the cylinder to lower the temperature of the refrigerant sucked by the cylinder, and as a result, the problem of excessive rise in the temperature of the low-pressure refrigerant or the problem that the density of the refrigerant is too small can be prevented. Therefore, the compressor refrigeration capacity reduction and efficiency reduction can be greatly improved. To achieve this goal, the technology provided herein diverts the low pressure refrigerant circuit into two intake cylinders. The heat exchange between the high-pressure refrigerant circuit such as the exhaust muffler chamber and the low-pressure refrigerant in the casing can be prevented, and the temperature rise of the low-pressure refrigerant in the casing can be controlled to prevent the refrigeration capacity and efficiency of the compressor from being lowered.
为达到该目的本文提供了采用上部、 下部轴承密封排气消声器室等高 压冷媒回路,并提出了在有限的容积内用排气消声器室有效地设计阀装置的 方法. 下面简述吐油量和润滑的改善。  In order to achieve this goal, a high-pressure refrigerant circuit is used to seal the exhaust muffler chamber with upper and lower bearings, and a method for effectively designing the valve device with a exhaust muffler chamber in a limited volume is proposed. The following is a brief description of the amount of oil discharged. Improved lubrication.
第一. 壳体高压的旋转式压缩机通过偏心曲轴的旋转, 可以利用油的 粘性从油池向中心孔 45自动供油, 中心孔的油通过偏心曲轴中设置的油孔 和轴承中设置的油孔, 可以润滑偏心曲轴和轴承。 壳体低压的旋转式压缩机, 因为偏心曲轴的中心孔压力是低压侧, 和 壳体压力相同, 故可以通过偏心曲轴的旋转从油池通过油泵 43下端的入口 向中心孔自动供油。 当偏心曲轴和轴承的润滑完成后, 油因为自重下落回收 入油池 44,但是,该油在被回收进油池 44的途中必须要避免被吸入消声器。 另外, 高压冷媒从气缸压缩腔 53向活塞内泄漏,如果中心孔 45的内部压力 比壳体压力高, 就不能向中心孔供油, 所以要采取设置平衡孔 81等对策。 First, the high-pressure rotary compressor of the casing can automatically supply oil from the oil pool to the center hole 45 by the eccentricity of the oil, and the oil of the center hole is set through the oil hole and the bearing provided in the eccentric crankshaft. Oil holes for lubrication of eccentric crankshafts and bearings. A low-pressure rotary compressor housing, because the center crank eccentrically hole pressure is a low pressure side, the pressure and the same housing, so that rotation of the eccentric crankshaft by automatic supply from the oil sump through the central bore 43 to the lower end of the inlet pump. When the lubrication of the eccentric crankshaft and the bearing is completed, the oil falls back to the income oil pool 44 due to its own weight, but the oil must be prevented from being sucked into the muffler on the way to be recovered into the oil pool 44. Further, the high-pressure refrigerant leaks from the cylinder compression chamber 53 into the piston. If the internal pressure of the center hole 45 is higher than the case pressure, the center hole cannot be supplied with oil. Therefore, countermeasures such as the provision of the balance hole 81 are taken.
对壳体低压的旋转式压缩机来说, 润滑技术的最大课题是气缸压缩中 所需要的运动部件的润滑、 以及对系统侧的吐油量都要控制在规格值以下。 即向气缸内部供油、对压缩所需的部品进行润滑的同时,在压缩组件的间隙 内填满油, 以防止气体泄漏。 由于供给气缸的油不是回收进壳体内部, 而是 全部从排气管和高压冷媒一起排出,所以向系统侧排出的吐油量有超过规格 值的趋势。因此为防止和避免这些问题,对气缸的供油量要进行优化并稳^, 而且从压缩机排气管排出的油回收后还要防止向系统侧的排油。  For rotary compressors with low casing pressure, the biggest problem of lubrication technology is the lubrication of moving parts required for cylinder compression and the amount of oil discharged to the system side to be below the specification value. That is, while supplying oil to the inside of the cylinder and lubricating the parts required for compression, the gap of the compression unit is filled with oil to prevent gas leakage. Since the oil supplied to the cylinder is not recovered into the inside of the casing, but is completely discharged from the exhaust pipe together with the high-pressure refrigerant, the amount of oil discharged to the system side tends to exceed the specification value. Therefore, in order to prevent and avoid these problems, the oil supply amount of the cylinder is optimized and stabilized, and the oil discharged from the compressor exhaust pipe is prevented from draining to the system side.
为解决该课题, 本发明提供的技术说明如下: 首先设计成油不流入吸 气消声器 35中。 在图 2中, 从主轴承 36内设置的油槽 48排出的油流入到 下部圆板 39和端环 38组成的空间部 47, 其后从空间部的外周间隙向下部 电机线圈 42. 2的内周飞散。 飞散的油被吸入到电机线圈中, 并滴落到上部 轴承 24上,最后从其外周附近设置的多个孔滴落下来回收至油池 44。故此, 下部圆板可以防止油滴进吸气消声器的圆形间隙 37中, 吸气消声器本身不 吸油。 由于下部圆板的旋转空间部 47的压力会下降, 与空间部连通的偏心 曲轴横孔 46的压力也下降,偏心曲轴中心孔 45的向上吸油能力进一步加大, 偏心曲轴中心孔的油也可能从横孔排出,由于下部圆板的阻挡作用可有效阻 止吸气消声器 35吸入油。 于是, 下部圆板可使吸气消声器只吸入冷媒, 而 防止其吸入油, 并且可以提高向上吸油的能力。  In order to solve this problem, the technical solution provided by the present invention is as follows: First, oil is not designed to flow into the suction muffler 35. 2, the oil discharged from the oil groove 48 provided in the main bearing 36 flows into the space portion 47 composed of the lower circular plate 39 and the end ring 38, and then from the outer peripheral space of the space portion to the inner motor coil 42. 2 Zhou Fei San. The scattered oil is sucked into the motor coil and dropped onto the upper bearing 24, and finally dripped from a plurality of holes provided near the outer periphery thereof to be recovered into the oil pool 44. Therefore, the lower circular plate prevents oil from dripping into the circular gap 37 of the suction muffler, and the suction muffler itself does not absorb oil. Since the pressure of the rotating space portion 47 of the lower circular plate is lowered, the pressure of the eccentric crankshaft transverse hole 46 communicating with the space portion is also lowered, and the upward oil absorbing ability of the eccentric crankshaft center hole 45 is further increased, and the oil of the center hole of the eccentric crankshaft may also be Discharge from the transverse hole can effectively prevent the suction muffler 35 from sucking in oil due to the blocking action of the lower circular plate. Thus, the lower circular plate allows the suction muffler to suck only the refrigerant, preventing it from sucking in oil, and improving the ability to absorb oil upward.
图 2是将下部圆板安装在转子的端环处, 作为其替代设计, 将下部圆 板安装在偏心曲轴上也可以得到相同的效果。另外, 如图 6所示也可以将下 部圆板安装在主轴承 36上, 此时, 下部圆板不旋转, 但和安装在转子的端 环处的效果基本相当。  Figure 2 shows the installation of the lower circular plate at the end ring of the rotor. As an alternative design, the same effect can be obtained by mounting the lower circular plate on the eccentric crankshaft. Further, as shown in Fig. 6, the lower circular plate can also be mounted on the main bearing 36. At this time, the lower circular plate does not rotate, but the effect is substantially the same as that at the end ring of the rotor.
笫二. 在图 2中说明了从活塞内侧向气缸吸入室内配置的第一开口槽 54. 1A和第二开口槽 54. 2的功能。 气缸低压腔 55的压力由于活塞引起的低 压冷媒吸入效果比活塞内压力(等同壳体压力 )仅低一点。 活塞内充满了从 偏心曲轴的中心孔 45供给的油, 压缩机运行中, 通过活塞和气缸低压腔之 间的压力差可以将活塞内的油供给到气缸低压腔中,该供油量由开口槽的断 面积和槽的数量来决定, 也就是说,供油量可以调整到所需的最下限, 从压 缩机向系统侧的吐油量也为最少, 同时可以对气缸压缩组件进行润滑。 The function of the first opening groove 54.1A and the second opening groove 54.2 are arranged from the inside of the piston to the cylinder suction chamber. The pressure of the cylinder low pressure chamber 55 is lower due to the low pressure refrigerant suction caused by the piston than the internal pressure of the piston (equivalent to the housing pressure). The piston is filled with oil supplied from the center hole 45 of the eccentric crankshaft. During the operation of the compressor, the oil in the piston can be supplied to the low pressure chamber of the cylinder through a pressure difference between the piston and the low pressure chamber of the cylinder. Slot break The area and the number of tanks are determined, that is, the oil supply can be adjusted to the minimum required, and the amount of oil discharged from the compressor to the system side is also minimized, and the cylinder compression assembly can be lubricated.
作为第一开口槽 54. 1A和第二开口槽 54. 2的替代方案, 如图 7所示在 下部轴承开排油孔 83, 该排油孔开口于气缸低压腔 55 , 其利用气缸低压腔 的压力比油池油压稍低的特点,从油池向气缸低压腔供给一定量的油。 因此 可以和图 2的第一开口槽 54. 1A和第二开口槽 54. 2一样, 发挥出同等的效 果。就这样供给气缸的油不光是可以润滑运动部件,还可以防止运动部件间 隙的气体泄漏, 以提高压缩机的压缩效率。  As an alternative to the first opening groove 54.1A and the second opening groove 54.2, as shown in FIG. 7, the oil discharge hole 83 is opened in the lower bearing, and the oil discharge hole is opened in the cylinder low pressure chamber 55, which utilizes the cylinder low pressure chamber The pressure is slightly lower than the oil pressure of the oil pool, and a certain amount of oil is supplied from the oil pool to the low pressure chamber of the cylinder. Therefore, the same effect as the first opening groove 54.1A and the second opening groove 54.2 of Fig. 2 can be exerted. The oil supplied to the cylinder in this way can not only lubricate the moving parts, but also prevent gas leakage of the moving parts gap to improve the compression efficiency of the compressor.
第三. 当从压缩机排出的吐油量过多影响到系统性能的时候, 可以在 排气管 2和冷凝器 5之间追加油分离器 4, 该油分离器的压力为高压侧, 其 目的是将分离出的油返回到压缩机,在系统中循环的油量要尽可能减小、但 需要考虑回油的位置。  Third, when the excessive amount of oil discharged from the compressor affects the performance of the system, an oil separator 4 may be added between the exhaust pipe 2 and the condenser 5, and the pressure of the oil separator is a high pressure side, The purpose is to return the separated oil to the compressor, and the amount of oil circulating in the system should be as small as possible, but the position of the return oil needs to be considered.
众所周知, 向压缩机低压侧的壳体内部回油, 油可以很容易地回收到 壳体内。但是,高压气体和油一起会回到壳体内的低压侧就会造成压缩机冷 冻能力降低。 为解决该课题, 本文提供的技术如下: 将油返回到气缸压缩腔 53内。 气缸压缩腔中有如图 3所示的注油孔 51 , 如图 2所示, 该注油孔和 下部轴承设置的供油管 52, 以及与其相连的壳体外部注油管 14相通。 注油 孔定位时要注意可在活塞 61运动面进行开关, 所以仅在气缸压力比吸入压 力高、 比排气压力低的旋转角度之间可以开孔。 因此, 油分离器分离出的高 压侧的油可以回到气缸压缩腔中, 采用该种设计方法, 油不回到低压侧, 因 此也不会发生压缩机冷冻能力降低的问题。回到气缸的油在气缸内部润滑后 和排气冷媒一起从气缸被排出, 到达滑片腔 63润滑滑片的运动面, 之后, 从排气管向壳体外部被排出,到达油分离器的油在这里再次从高压冷媒中被 分离, 而回到气缸压缩腔, 于是构成了循环系统。  It is well known that oil is returned to the inside of the casing on the low pressure side of the compressor, and the oil can be easily recovered into the casing. However, the high pressure gas and oil will return to the low pressure side of the housing together, resulting in a decrease in the compressor's ability to freeze. To solve this problem, the technique provided herein is as follows: The oil is returned to the cylinder compression chamber 53. The cylinder compression chamber has an oil filling hole 51 as shown in Fig. 3. As shown in Fig. 2, the oil filling hole and the lower bearing are provided with a fuel supply pipe 52, and a casing external oil filler pipe 14 connected thereto. Pay attention to the positioning of the oil hole. It is possible to switch on the moving surface of the piston 61. Therefore, the hole can be opened only when the cylinder pressure is higher than the suction pressure and lower than the exhaust pressure. Therefore, the oil on the high pressure side separated by the oil separator can be returned to the cylinder compression chamber. With this design method, the oil does not return to the low pressure side, and therefore the problem that the compressor refrigeration capacity is lowered does not occur. The oil returning to the cylinder is exhausted from the cylinder after being lubricated inside the cylinder, and is discharged from the cylinder together with the exhaust refrigerant, reaching the sliding surface of the sliding chamber 63 to lubricate the sliding surface, and then discharged from the exhaust pipe to the outside of the casing to reach the oil separator. Here, the oil is again separated from the high-pressure refrigerant and returned to the cylinder compression chamber, thus forming a circulation system.
如果油分离器的油回收效率约为 90%左右, 那么约 10%左右的油会流失 在系统侧,这就是流向系统侧的循环吐油量。流入系统侧的油从压缩机吸入 管 11回到壳体, 基本上全部可以回收。 故此油分离器的油回收效率在 90% 左右, 那么第一开口槽 54. 1和第二开口槽 54. 2或者排油孔 83供给的油量 只要补充相当于流失到系统侧循环吐油量的 10%就可以了。 油分离器在不降 低压缩机冷冻能力的情况下, 可确保油返回到气缸压缩腔 53中, 以充分对 必要的压缩组件进行润滑。 另外, 可起到大幅度(上述说明中为 10% )降低 系统中循环的吐油量的作用。  If the oil recovery efficiency of the oil separator is about 90%, about 10% of the oil will be lost on the system side, which is the amount of circulating oil flowing to the system side. The oil flowing into the system side is returned from the compressor suction pipe 11 to the casing, and substantially all of it can be recovered. Therefore, the oil recovery efficiency of the oil separator is about 90%, and the amount of oil supplied by the first opening groove 54.1 and the second opening groove 54.2 or the oil drain hole 83 is only equivalent to the amount of oil discharged to the system side. 10% is ok. The oil separator ensures that the oil returns to the cylinder compression chamber 53 without substantially reducing the refrigeration capacity of the compressor to adequately lubricate the necessary compression components. In addition, it is possible to greatly reduce the amount of oil discharged in the system (10% in the above description).
如图 10所示, 两气缸旋转式压缩机时可以在中隔板 87中设置供油管 52。将第一注油孔 51. 1和第二注油孔 51. 2对两个气缸分别开孔,这样从油 分离器出来的油可以分配在两个气缸中,故可以同时进行两个气缸压缩腔的 润滑。 As shown in FIG. 10, a two-cylinder rotary compressor can be provided with a fuel supply pipe in the intermediate partition 87. 52. The first oil hole 51. 1 and the second oil hole 51.2 are respectively opened for the two cylinders, so that the oil from the oil separator can be distributed in the two cylinders, so that the two cylinder compression chambers can be simultaneously performed. lubricating.
第四. 在图 6中, 下部轴承 25的气缸安装部位设置的平衡孔 81从油 池 44向下部轴承的环形 (或圆形)槽 82贯通, 由于环形槽和活塞 61内部 相连通, 故平衡孔也就和活塞内部连通。 由于严苛的压缩机运行条件, 当气 缸压缩腔 53的冷媒异常高压时, 高压冷媒就从活塞上下的间隙向活塞内泄 漏, 活塞内的压力短时间内会升高。 如果发生这种现象, 低压侧的偏心曲轴 中心孔 45的压力也会变高、 油池的油不能上升至中心孔, 故直接导致偏心 曲轴被磨损。 在这种异常状态下, 通过平衡孔 81可将泄漏在活塞内的高压 冷媒导入到油池中, 以防止上述问题的发生。将平衡孔配置在上部轴承中也 可有同等的效果,或者配置在上下轴承的两侧,并且两气缸的旋转式压缩机 也可以在中隔板 87中配置平衡孔 81。  Fourth, in Fig. 6, the balance hole 81 provided in the cylinder mounting portion of the lower bearing 25 penetrates from the annular (or circular) groove 82 of the lower bearing of the oil pool 44, and the balance is connected to the inside of the piston 61, so that the balance The hole also communicates with the interior of the piston. Due to the severe compressor operating conditions, when the refrigerant in the cylinder compression chamber 53 is abnormally high pressure, the high-pressure refrigerant leaks from the gap above and below the piston into the piston, and the pressure in the piston rises in a short time. If this happens, the pressure on the low-pressure side eccentric crankshaft center hole 45 will also become high, and the oil in the oil pool cannot rise to the center hole, which directly causes the eccentric crankshaft to be worn. In this abnormal state, the high-pressure refrigerant leaking in the piston can be introduced into the oil pool through the balance hole 81 to prevent the above problem from occurring. It is also possible to arrange the balance hole in the upper bearing or to be disposed on both sides of the upper and lower bearings, and the two-cylinder rotary compressor can also be provided with the balance hole 81 in the intermediate partition 87.
现将以上的技术要点归纳如下: 壳体低压的旋转式压缩机中要想降低 对系统侧的吐油量到允许范围以下,就必须要将对气缸的供油量减少到所需 的最小量, 而且必须使其稳定。 因此,  The above technical points are summarized as follows: In order to reduce the amount of oil discharged to the system side below the allowable range in the low-pressure rotary compressor of the casing, it is necessary to reduce the oil supply to the cylinder to the minimum required. And must be stabilized. Therefore,
( 1 ) 下部圆板要防止油流入消声器中;  (1) The lower circular plate is to prevent oil from flowing into the muffler;
( )通过和气缸低压室相通的开口槽或排油孔使油能稳定地供给; ( ) The oil can be stably supplied through an open groove or an oil drain hole communicating with the low pressure chamber of the cylinder;
( 3 )通过将油分离器设定在排气回路中, 使分离的油回到气缸压缩腔 中, 实现气缸→油分离器→气缸的油循环, 以充分润滑压缩组件中的关键部 分: 活塞和滑片; ' (3) By setting the oil separator in the exhaust circuit, the separated oil is returned to the cylinder compression chamber to realize the oil circulation from the cylinder→oil separator→cylinder to fully lubricate the key parts of the compression assembly: Piston And slides; '
( 4 )系统侧流失的油 (吐油量)可以大幅度减少;  (4) The oil (supply volume) lost on the system side can be greatly reduced;
( 5 )通过从油分离器向气缸压缩腔回油, 以保持压缩机效率; (5) maintaining compressor efficiency by returning oil from the oil separator to the cylinder compression chamber;
( 6 )油分离器也具有外部排气消声器的作用, 当设置有油分离器时, 可以省去外部排气消声器。 (6) The oil separator also functions as an external exhaust muffler. When an oil separator is provided, the external exhaust muffler can be omitted.

Claims

杈 利 要 求 书 Profit request
1、 一种壳体低压的旋转式压缩机, 包括设置在壳体(20) 内的压缩组 件(21)和电机组件(22) , 压缩组伴包括一个及以上的气缸, 设置在气缸内 的活塞, 设置在气釭滑片槽内的滑片, 驱动活塞的偏心曲轴(26) 以及支撑偏 心曲轴的上部、 下部轴承(24)和(25) , 电机组件包括电机转子和电机定子, 其特征是所述的壳体上设置有冷媒分流装置, 该冷媒分流装置设置在壳体的顶 部或者侧面, 冷媒分流装置包括分流管, 分流管中设置有调整分流比率的弹簧 管。  A low-pressure rotary compressor comprising a compression assembly (21) and a motor assembly (22) disposed in a housing (20), the compression assembly including one or more cylinders disposed in the cylinder a piston, a vane disposed in the air slide vane, an eccentric crankshaft (26) driving the piston, and upper and lower bearings (24) and (25) supporting the eccentric crankshaft, the motor assembly including the motor rotor and the motor stator, characterized The housing is provided with a refrigerant flow dividing device, and the refrigerant flow dividing device is disposed at the top or the side of the casing. The refrigerant flow dividing device includes a shunt pipe, and the shunt pipe is provided with a spring tube for adjusting the split ratio.
2、 根据杈利要求 1 所述的壳体低压的旋转式压缩机, 其特征是所述的电 机组件(22)与压缩组件(21)之间设置有吸气消声器(35) , 吸气消声器和 主轴承(3.6)之间设置有环向间隙 (37) , 和 /或电机转子或偏心曲轴或上部 轴承上设置有圆板,圆板覆盖吸气消声器中设置的吸入孔,和 /或电机转子(27) 和电机定子( 28 )之间设置有小间隙( 86 ) , 和 /或电机定子 ( 28 )和壳体( 20 ) 之间设置的间隙(84)与电机上部空间部(89)相连通; 和 /或上部轴承(24) 中设置有第三吸入孔(34) , 该第三吸入孔与吸气消声器(35)和环向间隙相 连通; 和 /或气缸 (23) 中设置有两个吸入孔, 分别为设置在上部轴承(24)'· 竖直方向上的第一吸入孔(31)和气缸侧面水平方向上的第二吸入孔(32),; 第一吸入孔和第三吸入孔(34)相连通, 第一吸入孔和第二吸入孔相连通。 2. The housing low pressure rotary compressor according to claim 1, wherein the motor assembly ( 22 ) and the compression assembly (21) are provided with an air suction muffler (35), an air suction muffler. A circumferential gap (37) is provided between the main bearing (3.6), and/or a motor or a eccentric or upper bearing is provided with a circular plate covering the suction hole provided in the suction muffler, and/or the motor clearance is provided a small gap is provided (86), and / or the stator (28) and the housing (20) between the rotor (27) and the stator (28) between (84) and the upper space of the motor unit (89 a third suction port (34) is provided in the upper bearing (24), the third suction port is in communication with the suction muffler (35) and the circumferential gap; and/or in the cylinder (23) Provided are two suction holes, respectively a first suction hole (31) disposed in the vertical direction of the upper bearing (24)' and a second suction hole (32) in the horizontal direction of the cylinder side; the first suction hole The third suction hole (34) communicates with the first suction hole and the second suction hole.
3、 根据权利要求 1所述的壳体低压的旋转式压缩机 其特征是所述的气 缸的高压侧设置有排气孔(12) , 该排气孔与设置在壳体(20) 内的排气消声 腔( 13 )相连通,排气消声器腔设置在气缸排 '气孔和设置在壳体上的排气管( 2 ) 之间, 排气消声器腔由上部、 下部轴承和 /或气缸共同围成, 排气消声器腔中 设置有排气阀 (71)和排气阀限位板(72) , 排气阀和 /或排气限位板为 U字 形或 V字形, 和 /或气缸的滑片腔与排气管相连通。  3. The housing low pressure rotary compressor according to claim 1, wherein said cylinder has a vent hole (12) disposed on a high pressure side thereof, said vent hole being disposed in said housing (20) The exhaust muffler chamber (13) is in communication, and the exhaust muffler chamber is disposed between the cylinder bore 'ventilation and the exhaust pipe (2) disposed on the casing, and the exhaust muffler cavity is shared by the upper portion, the lower bearing and/or the cylinder Enclosed, an exhaust valve (71) and an exhaust valve limit plate (72) are disposed in the exhaust muffler chamber, and the exhaust valve and/or the exhaust limit plate are U-shaped or V-shaped, and/or the cylinder The vane chamber is in communication with the exhaust pipe.
4、 根据杈利要求 1所述的壳体低压的旋转式压缩机, 其特征是所述的壳 体(20) 内设置有平衡孔(81) , 该平衡孔设置在上部轴承(24)和 /或下部 轴承(25)和 /或中间隔板(87)上, 与活塞内部相连通, 和 /或上部轴承和下 部轴承上设置有环形槽(82) , 环形槽与活塞内部相连通, 平衡孔与环形槽相 连通, 和 /或压缩机外设置有油分离器(4), 油分离器依次通过壳体外的注油 管 (14)和壳体内的供油管(52)与气缸(23)相连通; 供油管通过设置在上 部轴承 4)或下部轴承(25)上的注油孔(51)与气缸相连通, 或供油管分 别通过设置在两气缸之间的中间隔板(87)上的第一供油孔(51.1)和第二供 油孔(51· 2 )与第一气缸(91. 1 )和第二气缸(91. 2 )相连通。 4. The housing low pressure rotary compressor according to claim 1, wherein the housing (20) is provided with a balance hole (81), and the balance hole is disposed in the upper bearing (24) and / or the lower bearing (25) and / or the intermediate partition (87), communicate with the inside of the piston, and / or the upper bearing and the lower bearing are provided with an annular groove (82), the annular groove is connected with the inside of the piston, balanced The hole is connected to the annular groove, and/or the oil separator (4) is disposed outside the compressor, and the oil separator sequentially passes through the oil injection pipe (14) outside the casing and the oil supply pipe (52) and the cylinder (23) in the casing. Connected to the cylinder through the oil filling hole (51) provided on the upper bearing 4) or the lower bearing (25), or the oil supply pipe respectively passes through the intermediate partition (87) disposed between the two cylinders The first oil supply hole (51.1) and the second supply The oil hole (51·2) is in communication with the first cylinder (91. 1) and the second cylinder (91. 2).
5、 根据杈利要求 1 所述的壳体低压的旋转式压缩机, 其特征是所述的电 机转子( 27 ) 的端环上设置有上部圆板( 41 )和 /或下部圆板( 39 ) , 上部圆 板和 /或下部圆板上设置有圆孔, 下部圆板(39 ) 圆孔与主轴承(36 )之间设 置有间隙, 端环、 偏心曲轴和上部圆板围成空间部(47 ) , 偏心曲轴 (26 )上 设置有横孔(46 )与空间部相连通, 设置在偏心曲轴上的中心孔(45 )顶端与 横孔相连通, 偏心曲轴底端设置有油泵(43 ), 油泵底端开口于壳体底部的油 池 (44 ) 内, 中心孔与油泵相连通, 和 /或主轴承的内侧面上设置有螺旋形油 槽(48 ),该油槽顶端开口于空间部,和 /或上部轴承和下部轴承位于活塞(61 ) 运动面上分别设置有第一开口槽 (54. 1 )和第二开口槽 (54. 2 ) , 和 /或端环 上设置有平衡块。 5. The housing low pressure rotary compressor according to claim 1, characterized in that the end ring of the motor rotor ( 27 ) is provided with an upper circular plate (41) and/or a lower circular plate (39). ), the upper circular plate and/or the lower circular plate are provided with a circular hole, and the lower circular plate (39) is provided with a gap between the circular hole and the main bearing (36), and the end ring, the eccentric crankshaft and the upper circular plate enclose a space portion. (47), the eccentric crankshaft (26) is provided with a transverse hole (46) communicating with the space portion, and the top end of the central hole (45) disposed on the eccentric crankshaft is in communication with the transverse hole, and the bottom end of the eccentric crankshaft is provided with an oil pump (43) The bottom end of the oil pump is open in the oil pool (44) at the bottom of the casing, the central hole is in communication with the oil pump, and/or the inner surface of the main bearing is provided with a spiral oil groove (48), and the top end of the oil groove is open to the space portion. And/or the upper bearing and the lower bearing are respectively disposed on the moving surface of the piston (61) with a first opening groove (54.1) and a second opening groove (54.2), and/or a balance block is disposed on the end ring .
6、 一种如杈利要求 1 所述的壳体低压的旋转式压缩机的冷媒控制方式, 其特征是将进入压缩机的低压冷媒分流为两支路及以上, 其中一支路通过壳体 内部进行热交换后再进入气缸, 另一支路直接进入气缸, 两支路中的冷媒被压 缩前合流。  6. A refrigerant control method for a low-pressure rotary compressor of a housing as claimed in claim 1, characterized in that the low-pressure refrigerant entering the compressor is branched into two branches and above, one of which passes through the housing After the internal heat exchange, the cylinder enters the cylinder, and the other branch directly enters the cylinder. The refrigerant in the two branches merges before being compressed.
7、 一种如杈利要求 1 所述的壳体低压的旋转式压缩机的冷媒控制方式., 其特征是所述的压缩机内设置有两个及以上的气缸, 将进入压缩机的低压冷媒 分流为两支路及以上, 其中一支路直接进入一个气缸, 另一支路通过壳体内部 进行热交换后再进入到另一个气缸。  7. A refrigerant control method for a low-pressure rotary compressor of a housing as claimed in claim 1, characterized in that the compressor is provided with two or more cylinders, which will enter the low pressure of the compressor. The refrigerant is divided into two branches and above, one of which directly enters one cylinder, and the other of which passes through the inside of the casing for heat exchange and then enters another cylinder.
8、 根据权利要求 6或 7所述的壳体低压的旋转式压缩机的冷媒控制方式, 其特征是所述的压缩机上设置有低压冷媒分流装置, 通过该装置调整各支路中 低压冷媒的流量比例。  8. The refrigerant control method for a low-pressure rotary compressor of a casing according to claim 6 or 7, wherein said compressor is provided with a low-pressure refrigerant flow dividing device, and the low-pressure refrigerant in each branch is adjusted by the device. Flow ratio.
.  .
9、 根据杈利要求 8所述的壳体低压的旋转式压缩机的冷媒控制方式, 其 特征是所述的冷媒为汽液两态时, 通过汽液分离装置分离出液态和气态部分, 液态冷媒先进入壳体内部进行热交换后再进入气缸, 气态冷媒则直接进入气 缸。 9. The refrigerant control method of a low-pressure rotary compressor according to claim 8, wherein the refrigerant is in a vapor-liquid two-state, and the liquid and gaseous portions are separated by a vapor-liquid separation device. The refrigerant enters the inside of the casing for heat exchange and then enters the cylinder. The gaseous refrigerant enters the cylinder directly.
10、 一种如权利要求 1所述的壳体低压的旋转式压缩机的回油控制方式, 其特征是从压缩机外部的油分离器直接向气缸压缩腔回油, 或者通过设置在两 气缸之间的隔板间接向两个气缸内回油, 或者从压缩机内的油池或经过贯通活 塞内部的孔或槽向气缸低压部分或吸入回路供油。  10. A return oil control method for a low-pressure rotary compressor of a casing according to claim 1, wherein the oil separator from the outside of the compressor directly returns oil to the cylinder compression chamber, or is disposed in two cylinders. The separator between the two indirectly returns oil to the two cylinders, or from the oil pool in the compressor or through a hole or groove penetrating the inside of the piston to the low pressure portion of the cylinder or the suction circuit.
11、 一种如权利要求 1 所述的壳体低压的旋转式压缩机的应用, 可釆用 HCFC冷媒、 HFC冷媒、 HC冷媒及 C02冷媒。 Application of the rotary compressor 11. A housing as claimed in claim 1, said low pressure, can preclude the use of HCFC refrigerant, HFC refrigerant, HC refrigerant, and the refrigerant C0 2.
PCT/CN2008/000244 2007-11-09 2008-01-31 A rotary compressor with low pressure in its shell and methods for controlling its cold media and oil and application thereof WO2009059488A1 (en)

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