CN102251964B - Rotary compressor - Google Patents

Rotary compressor Download PDF

Info

Publication number
CN102251964B
CN102251964B CN 201010181068 CN201010181068A CN102251964B CN 102251964 B CN102251964 B CN 102251964B CN 201010181068 CN201010181068 CN 201010181068 CN 201010181068 A CN201010181068 A CN 201010181068A CN 102251964 B CN102251964 B CN 102251964B
Authority
CN
China
Prior art keywords
cylinder
gas
compression chamber
rotor
rotary compressor
Prior art date
Application number
CN 201010181068
Other languages
Chinese (zh)
Other versions
CN102251964A (en
Inventor
小津政雄
李华明
Original Assignee
广东美芝制冷设备有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 广东美芝制冷设备有限公司 filed Critical 广东美芝制冷设备有限公司
Priority to CN 201010181068 priority Critical patent/CN102251964B/en
Publication of CN102251964A publication Critical patent/CN102251964A/en
Application granted granted Critical
Publication of CN102251964B publication Critical patent/CN102251964B/en

Links

Classifications

    • 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
    • F04C23/00Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F04C23/00Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008Hermetic pumps
    • 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
    • F04C28/00Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/02Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
    • 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
    • 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

Abstract

The invention relates to a rotary compressor and a control method thereof, and the rotary compressor comprises a motor part and a two-stage compression type compression mechanism part which are arranged in a sealed housing, wherein the motor part comprises a stator and a rotor, the compression mechanism part comprises a first cylinder, a second cylinder, a crankshaft for driving a first piston and a second piston to rotate eccentrically in a first cylinder compression cavity and a second cylinder compression cavity, a main bearing and an auxiliary bearing, the main bearing and the auxiliary bearing are used for supporting the crankshaft, the end parts of a first sliding sheet and a second sliding sheet are connected with the peripheries of the first piston and the second piston respectively, and gas which is spitted from the first cylinder compression cavity into the sealed housing is sucked into the second cylinder compression cavity. A cooling medium injection device communicated with the second cylinder compression cavity is arranged on the second cylinder compression cavity. The rotary compressor has the characteristics of high air-conditioning ability, high efficiency, safety, reliability and a wide application range and can be popularized and applied to heat pump type air conditioners.

Description

Rotary compressor
Technical field
The present invention relates to a kind of rotary compressor.
Background technique
Jet-propelled air-conditioning is the gas coolant that gas-liquid separator produces to be injected into by the refrigerant infusion circuit in the cylinder compression chamber of compressor increase efficient.After sneaking into liquid coolant in the refrigerant infusion circuit, liquid coolant will condensation in the oil of compressor, and oil viscosity descends, and causes the abrasion of the component doing to slide, thereby so that compressor break down.
Patent documentation 1: Japanese Laid-Open Patent communique 2008-286037 rotary compressor and heat pump
Patent documentation 2: Japanese Laid-Open Patent communique 2006-177224 rotary compressor
Summary of the invention
Purpose of the present invention aims to provide a kind of simple and reasonable, air-conditioning ability and high, safe and reliable, the applied widely rotary compressor of efficient, to overcome deficiency of the prior art.
A kind of rotary compressor by this purpose design, comprise the motor section that is arranged in the seal casinghousing and the compression mechanical part of making two sections compression types, motor section comprises stator and rotor, compression mechanical part comprises the first cylinder and the second cylinder, drive first piston and the second piston and in the first cylinder compression chamber and the second cylinder compression chamber, make respectively the bent axle of eccentric rotary, and the main bearing and the supplementary bearing that support bent axle, the end of the first slide plate and the second slide plate joins with the periphery of first piston and the second piston respectively, it is characterized in that being inhaled into the second cylinder compression chamber from the gas that the first cylinder compression chamber spues in the seal casinghousing.
Be provided with the refrigerant injection device that communicates with it on described the second cylinder compression chamber.
Be provided with the first discharge valve and the middle baffler of pressing on the described main bearing, the first discharge valve is communicated with the first cylinder compression chamber and the middle baffler of pressing; Gas imports jacket casing and is located at outside the bent axle, the end that gas imports cylinder communicates with the middle baffler of pressing, gas imports the close rotor of opening of the other end of cylinder, be provided with more than one the rotor pore that connects along its axis on the rotor, the opening end of rotor pore is positioned at the scope at opening place that gas imports the other end of cylinder; One end opening of gas discharge pipe is in the outside of gas importing cylinder, and the other end of gas discharge pipe communicates with the middle baffler of pressing; One end opening of gas suction pipe is in baffler is pressed in the centre, and the other end of gas suction pipe communicates with the second cylinder compression chamber.
Press in the baffler in the middle of described and be provided with the first silencing cavity and the second silencing cavity, the first discharge valve communicates with the first silencing cavity, and an end opening of gas suction pipe is in the second silencing cavity, and the other end of gas discharge pipe communicates with the first silencing cavity.
Described refrigerant injection device comprises the pipe that is inserted into the second cylinder side from the outside of seal casinghousing, be arranged on first of pipe central authorities spue the hole, be arranged on the second cylinder and perforate in second of the second cylinder compression chamber spue the hole, be communicated with first spue hole and the second cylinder compression chamber expansion chamber and be positioned at expansion chamber and be used for opening and closing the first safety check that spues the hole.
Described pipe communicates with an end of coolant injection tube, and the other end of coolant injection tube communicates with the upper space of gas-liquid separator.
The upper end of described bent axle is provided with the rotor plectane, and being provided with between the upper end of rotor plectane and rotor can be by the gap of gas.
Described refrigerant injection device comprises the U-shaped pipe, and an end of this U-shaped pipe is communicated with the shell space that is positioned at the motor section top, and the other end of U-shaped pipe is communicated with the second cylinder compression chamber.
A kind of rotary compressor, comprise the motor section that is arranged in the seal casinghousing and the compression mechanical part of making two sections compression types, motor section comprises stator and rotor, compression mechanical part comprises the first cylinder and the second cylinder, drive first piston and the second piston and in the first cylinder compression chamber and the second cylinder compression chamber, make respectively the bent axle of eccentric rotary, and the main bearing and the supplementary bearing that support bent axle, the end of the first slide plate and the second slide plate joins with the periphery of first piston and the second piston respectively, it is characterized in that also comprising perforate in the refrigerant injection device of the second cylinder compression chamber, the gas that spues in the seal casinghousing from the first cylinder compression chamber is inhaled into the second cylinder compression chamber.
Described refrigerant injection device comprises the pipe that is inserted into the second cylinder side from the outside of seal casinghousing, be arranged on first of pipe central authorities spue the hole, be arranged on the second cylinder and perforate in second of the second cylinder compression chamber spue the hole, be communicated with first spue hole and the second cylinder compression chamber expansion chamber and be positioned at expansion chamber and be used for opening and closing the first safety check that spues the hole.
Described pipe communicates with an end of coolant injection tube, and the other end of coolant injection tube communicates with the upper space of gas-liquid separator.
It is two sections compression type rotary compressors of intermediate pressure that the present invention adopts housing pressure, injecting gas refrigerant in the compression process of the second cylinder compression chamber, even sneak into liquid coolant, this liquid coolant can condensation in oil yet, and controls easily refrigerant and inject.
The gas coolant that the present invention optionally produces the gas-liquid separator in the freeze cycle injects the second cylinder compression chamber of compressor, when improving air-conditioning ability and efficient, can under the state that does not carry out loaded down with trivial details freeze cycle control, prevent the decline of compressor reliability.
The present invention has the following advantages: the reliability problem can not occur even sneak into liquid coolant at the refrigerant infusion circuit in (1) yet; (2) because not needing gas coolant injected controls, so easily this compressor is applied manufacture cost and control cost all lower; (3) can supply with a large amount of gas coolants in the cylinder compression chamber, compare with mode in the past and can further improve heating capacity and efficient; (4) can reduce the oil mass of telling that comes from compressor.
That the present invention has is simple and reasonable, air-conditioning ability and high, safe and reliable, the applied widely characteristics of efficient, can be promoted the use of on the heat pump air conditioner.
Description of drawings
Fig. 1 is the first embodiment of the invention structural representation.
The broken section that Fig. 2 and Fig. 3 are respectively rotary compressor amplifies
Fig. 4 is that Y-Y among Fig. 1 is to analysing and observe amplification
Fig. 5 is P-V plotted curve of the present invention.
Fig. 6 is the second embodiment of the invention structural representation.
Among the figure: 1 is rotary compressor, and 2 is seal casinghousing, and 3 is discharge pipe, 5 is condenser, and 6 is vaporizer, and 7 is gas-liquid separator, 8a is the first capillary tube, and 8b is the second capillary tube, and 13 is liquid-storage container, 14 is suction pipe, and 16 is the refrigerant injection device, and 16a is first hole that spues, 16b is second hole that spues, and 16c is pipe, and 16d is safety check, 17 is coolant injection tube, and 18a is gas coolant, and 18b is the liquid cooling matchmaker, 21 is compression mechanical part, and 22 is motor section, and 22b is rotor, 22c is the rotor pore, and 22d is end ring, and 22e is the rotor plectane, 22f is coil, and 22g is stator iron core, and 23a is the first cylinder, 23b is the second cylinder, and 24a is the first cylinder compression chamber, and 24b is the second cylinder compression chamber, 25 is main bearing, 26 is supplementary bearing, and 27 is bent axle, and 28a is first piston, 28b is the second piston, 29a is the first slide plate, and 29b is the second slide plate, and 31 is central diaphragm, 32 are intermediate-pressure gas suction path, 33 is the middle baffler of pressing, and 33a is the first silencing cavity, and 33b is the second silencing cavity, 33c is that gas imports cylinder, 33d is the gas discharge pipe, and 33e is gas suction pipe, and 34 is the high pressure silencing cavity, 35a is the first discharge valve, 35b is the second discharge valve, and 36 is oil, and 41 is the U-shaped pipe.
Embodiment
The invention will be further described below in conjunction with drawings and Examples.
The first embodiment
Referring to Fig. 1, be the internal structure of rotary compressor 1 and the air-condition freezing circulation of carrying this rotary compressor.Fig. 2 and Fig. 3 are the details drawing of compression mechanical part 21.Fig. 4 is the Y-Y sectional view among Fig. 1.
Rotary compressor 1 is made of the compression mechanical part 21 that is installed on the two sections compression types of work on seal casinghousing 2 inwalls and the motor section 22 that is disposed at its top.
Compression mechanical part 21 comprises two cylinders: the first cylinder 23a and the second cylinder 23b, be received into first piston 28a among the first cylinder compression chamber 24a and the second cylinder compression chamber 24b and the second piston 28b, the first slide plate 29a and the second slide plate 29b, main bearing 25 and supplementary bearing 26, the bent axle 27 that supported by main bearing 25 and supplementary bearing 26 consists of.Be clipped in the central diaphragm 31 among the first cylinder 23a and the second cylinder 23b, this central diaphragm 31 is used for dividing two cylinder compression chambers.Compression mechanical part 21 is installed on the inwall of seal casinghousing 2 by the periphery of main bearing 25.
The motor section 22 that is installed on seal casinghousing 2 inwalls is made of stator 22a and rotor 22b, and stator is made of stator iron core 22g and coil 22f, is provided with more than one rotor pore 22c and end ring 22d on the rotor 22b.Rotor pore 22c arranges along its axis on rotor 22b, and connects rotor 22b.But, for variable-frequency motor, do not use the situation of end ring 22d many.Above rotor 22b, be installed on that be provided with between the rotor plectane 22e of bent axle 27 upper ends and the rotor 22b upper end can be by the gap of gas.
By the bent axle 27 that motor section 22 drives, driving first piston 28a and the second piston 28b make eccentric rotary in the first cylinder compression chamber 24a and the second cylinder compression chamber 24b respectively.The periphery of the first slide plate 29a and the second slide plate 29b and first piston 28a and the second piston 28b is joined reciprocating, with first piston 28a and the second piston 28b, play a part respectively compressed gas in the first cylinder compression chamber 24a and the second cylinder compression chamber 24b of sealing, but also play the first cylinder compression chamber 24a is divided into low-pressure cavity and hyperbaric chamber, and the effect that the first cylinder compression chamber 24a is divided into low-pressure cavity and hyperbaric chamber.
Being provided with the first discharge valve 35a and centre on the main bearing 25 presses baffler 33, the first discharge valve 35a to be communicated with the first cylinder compression chamber 24a and the middle baffler 33 of pressing; Gas imports cylinder 33 and is set in outside the bent axle 27, the end that gas imports cylinder 33 communicates with the middle baffler 33 of pressing, gas imports the opening of the other end of cylinder 33 near rotor 22b, and the opening end of rotor pore 22c is positioned at the scope at opening place that gas imports the other end of cylinder 33; The end opening of gas discharge pipe 33d is in the outside of gas importing cylinder 33, and the other end of gas discharge pipe 33d communicates with the middle baffler 33 of pressing; The end opening of gas suction pipe 33e is in baffler 33 is pressed in the centre, and the other end of gas suction pipe 33e communicates with the second cylinder compression chamber 24b.
The middle pressure in the baffler 33 is provided with the first silencing cavity 33a and the second silencing cavity 33b, the first discharge valve 35a communicates with the first silencing cavity 33a, the other end of gas discharge pipe 33d communicates with the first silencing cavity 33a, and the end opening of gas suction pipe 33e is in the second silencing cavity 33b.When the external diameter that gas is imported cylinder 33c and the gap design between the end ring 22d internal diameter get hour, the gas that spues from gas discharge pipe 33d can not enter the inside that gas imports a 33c.
The pressure that sucks from the suction pipe 14 that is installed on the first cylinder 23a side is the low-pressure gas of Ps, in the first cylinder compression chamber 24a, be compressed to the intermediate pressure gas body, the pressure of this intermediate pressure gas body is Pm, the intermediate pressure gas body is via the first discharge valve 35a that is disposed on the main bearing 25, and the first silencing cavity 33a of baffler 33 is pressed in the centre that spues.Thereafter, the intermediate pressure gas body moves to the space between motor section 22 and the main bearing 25 from gas discharge pipe 33d.Sneak into the oil of a large amount of spray forms in the intermediate pressure gas body.
The intermediate pressure gas body mainly by being rolled onto coil 22f and the gap around it on the stator 22a, moves to the space between motor section 22 tops and the seal casinghousing 2.The oil of sneaking into the spray form of intermediate pressure gas body therebetween, can be separated from body is calmed the anger in the centre relatively easily.
At this, the intermediate pressure gas body moves to the gap between the upper end of the lower end of High Rotation Speed ground rotor plectane 22e and rotor 22b.At this moment, sneak into the oil of the spray form in the intermediate pressure gas body, by the centrifugal force separate of rotor plectane 22e out after, the bottom from seal casinghousing 2 is fallen in stator 22a gap is recovered.
Intermediate pressure gas body after the separating oil, usually from upper direction to lower direction, by four rotor pore 22c, import cylinder 33c, the second silencing cavity 33b and gas suction pipe 33e via gas successively in order, the body of calming the anger from the centre sucks path 32 and sucks the second cylinder compression chamber 24b.
As shown in Figure 2, the second slide plate 29b of refrigerant injection device 16 and the second cylinder compression chamber 24b is adjacent and dispose.
Refrigerant injection device 16 comprises the pipe 16c that is inserted into the second cylinder 23b side from the outside of seal casinghousing 2, be arranged on first of pipe 16c central authorities spue hole 16a, be arranged on the upper and perforate of the second cylinder 23b in second of the second cylinder compression chamber 24b spue hole 16b, be communicated with first spue hole 16a and the second cylinder compression chamber 24b expansion chamber and be positioned at expansion chamber and be used for opening and closing the first safety check 16d that spues hole 16a.Pipe 16c in the present embodiment can be arranged on left side, right side, upside or the downside of the second cylinder 23b as required, has only provided the concrete structure that pipe 16c is arranged on the second cylinder 23b left side among the figure.
The outside of discoideus safety check 16d has several otch that become the gas passageway.Safety check 16d opens first when spuing hole 16a, and the first otch of gas coolant by safety check that spues hole 16a is injected into the second cylinder compression chamber 24b from the second hole 16b that spues.
Be injected into the gas coolant among the second cylinder compression chamber 24b, with the compression in gas mix, become the pressurized gas that pressure is Pd, these pressurized gas via the second discharge valve 35b, spuing is formed in the high pressure silencing cavity 34 of supplementary bearing 26 inside.Thereafter, pressurized gas flow to condenser 5 from discharge pipe 3.High pressure silencing cavity 34 is shaped in the cast sections of supplementary bearing 26.
Pressurized gas from discharge pipe 3 spues become liquid coolant after the condensation in condenser 5, by the first capillary tube 8a, move to gas-liquid separator 7.The gas coolant 18a that the liquid coolant that is depressurized produces hoards the upper space of gas-liquid separator 7, and overcooled liquid coolant 18b hoards lower space.After liquid coolant 18b reduces pressure by the second capillary tube 8b, evaporation in vaporizer 6.At the refrigerant of this evaporation, via liquid-storage container 13, turn back to the first cylinder compression chamber 24a from suction pipe 14.
Gas coolant 18a in the gas-liquid separator 7 moves to refrigerant injection device 16 via coolant injection tube 17.Gas coolant is injected among the second cylinder compression chamber 24b as mentioned above.So, use in the freeze cycle of jet compressor, the overcooled liquid coolant 18b of entrained gas can not improve the caloric receptivity of vaporizer, so can improve heating capacity, refrigerating capacity and efficient.
Next, the effect of the embodiment of the invention 1 public technology described.
Fig. 5 is, the P-V plotted curve of disclosed two sections compression type rotary compressors among the present invention, and be injected into the relation of the gas coolant 18a among the second cylinder compression chamber 24b.The P of the longitudinal axis is the pressure of the first cylinder compression chamber 24a and the second cylinder compression chamber 24b, and the V of transverse axis is the volume of these strokes.
At this, Pm is the pressure that spues of the first cylinder compression chamber 25a, and is the internal pressure of seal casinghousing simultaneously, and is the suction pressure of the second cylinder compression chamber 24b.Pi is for from the second gas coolant pressure that hole 16b spues that spues.Pi reduces pressure by condenser 5, the first capillary tube 8a, coolant injection tube 17, and the pressure P d that spues than the second cylinder compression chamber 24b is low usually.
Eccentric rotary along with the second piston 28b, the compression pressure of the second cylinder compression chamber 24b is at intermediate pressure Pm and spue and change between the pressure P d, when the pressure ratio second of the second cylinder compression chamber 24b spues hole 16b pressure P i when low, gas coolant is injected into the second cylinder compression chamber 24b from the second hole 16b that spues.
Thereafter, spue hole 16b pressure high moment than second at the compression pressure of the second cylinder compression chamber 24b, safety check 16d closes the first hole 16a that spues, and gas coolant injects and interrupts.The every rotation of the second piston 28b once, safety check 16d to-and-fro motion is carried out that gas coolant injects and injects interrupting.Be injected into the pressure range of injecting interruption from refrigerant, can show as the Δ p of Fig. 5, Δ p=Pi-Pm.
At this, the refrigerant injection amount relevant with air-conditioning ability increase and decrease, as mentioned above, not only the first capillary tube 8a with above-mentioned is relevant with coolant injection tube 17, and hole 16a and second the different also relevant of hole 16b size that spue that spue of first in according to the present invention.
Refrigerant injection device 16 by first spue hole 16a, second spue hole 16b, betwixt the configuration safety check 16d consist of, can adjust easily the refrigerant injection amount; If necessary, can increase considerably the refrigerant injection amount.
If when any among suction pressure Ps and the pressure P d that spues changed, Pm will change.In the operating condition of reality, Pm often changes, and varies widely in abnormal operating condition lower time especially.When employing can frequently change the variable-frequency motor of compressor rotational speed, this variation will be more obvious.But, the present invention, even under the Pi condition less than Pm, safety check 16d is the autoshutdown first hole 16a that spues still, therefore can avoid the problem of refrigerant adverse current.
Gas coolant in the second cylinder compression chamber 24b compression if occur from coolant injection tube 17 adverse currents to gas-liquid separator 7, with not only can be so that jet effect vanishing, and can cause the decrease in efficiency of compressor; Because the gas coolant of adverse current flows in the vaporizer 6, efficient that will the decrease system.
The refrigerant injected system of rotary compressor in the past, the refrigerant that injects from coolant injection tube be with the gas that spues, via seal casinghousing, again from being arranged on discharge pipe on the seal casinghousing condenser that spues.Yet in the present invention, after being injected into the refrigerant of the second cylinder compression chamber and pressure and being the gas interflow that spues of Pd, need not be via seal casinghousing, directly from the discharge pipe that communicates with the second cylinder compression chamber condenser that spues, so substantially different from technology in the past, as therefore can to prevent refrigerant condensation in seal casinghousing, cause oil viscosity to descend problem.
As the means that solve above-mentioned a plurality of problems, among in the past coolant injection tube and the first capillary tube, the second capillary tube three at least one can be replaced with flow control valve, carry out system's control according to the temperature conditions of discharge pipe, suction pipe, condensator outlet temperature etc.
The present invention is by above-mentioned feature, so that the relevant gas coolant injected system control summary of rotary compressor can easily be provided by the rotary compressor that provides.For example, can use cheaply capillary tube, replace in the past required flow control valve.But, need to optimize design capillaceous, certainly, also can use above-mentioned flow control valve.
In public technology, be illustrated centered by the injecting gas refrigerant coming by the refrigerant injection device; Use the method for mixing material refrigerant and gas coolant, have the effect that reduces the gas temperature that spues.In disclosed technology, used the safety check that is conducive to the refrigerant injection amount; Injecting refrigerant has multiplely to the means of cylinder compression chamber, be not the means that only are defined as public technology of the present invention.
The oil mass means are told in reduction disclosed by the invention, (1) as rotary compressor, the intermediate pressure gas body that spues from the first cylinder 23a flows to the upper space of motor section 22, the oil of a large amount of spray forms that contains the intermediate pressure gas body by the coil 22f of high temperature heating after, become the oil of grain refined; (2) by the rotor plectane 22e of High Rotation Speed, can prevent that the oil of grain refined from entering rotor pore 22c; (3) the intermediate pressure gas body that is separated by oil is drawn into the second cylinder 23b from rotor pore 22c.
By these three strokes, can prevent that oil from entering among the second cylinder compression chamber 24b, can significantly reduce the oil that spues from discharge pipe 3, be the oil mass of telling of systemic circulation.Consequently, can prevent that the too much compressor oil starvation that causes of antiemetic oil mass and system effectiveness descend.
As sucking the intermediate pressure gas body from rotor pore 22c to the technological scheme of the second cylinder 23b, such as public technology, by the silencing cavity that is communicated with the second cylinder compression chamber 24b is set on main bearing 25 tops, thereby solve easily.Above-mentioned public technology is compared with conventional art, can significantly reduce and tell oil mass, so also can cancel the design of rotor plectane 22e.
The present invention such the two section compression type rotary compressors of seal casinghousing as intermediate pressure in, exist the oil that enters the 2nd section the second cylinder and can not in seal casinghousing, carry out oil and separate and directly tell the problem of oil in the system.The technology that provides can be provided, solve this problem.
The oil mass means are told in disclosed reduction, are technology independent from the gas coolant injection technique, so can be widely applied on two sections compression type rotary compressors.
The present invention adopts the design of DC frequency-changing formula motor, does not need the end ring of rotor.At this moment, import the gap of cylinder 33c upper end and rotor lower end by dwindling gas, the punching press component that perhaps will be equivalent to end ring are fixed on the rotor, thereby reduce the means such as gap between punching press component and the gas importing cylinder 33c, can solve easily.
In drawing disclosed by the invention, the discharge capacity of the second cylinder designs littlely than the first cylinder; Certainly, also can suitably adjust the discharge capacity ratio of two cylinders.The first cylinder as the 1st section compression, the second cylinder as the 2nd section compression; Certainly, can also it sequentially be changed, order is changed afterwards, is compared with public technology, and its formation, effect, effect do not have too large difference.
The second embodiment
Referring to Fig. 6, suck the method for motor part 22 top intermediate pressure gas bodies by use U-shaped pipe 41, from the side of the second cylinder 23b, can obtain the effect identical with public technology.But, by the method, can not use the rotor plectane, so oil content is disembarked can significantly descend and cost uprises.
All the other are not stated part and see the first embodiment, no longer repeat.
In sum, technology disclosed by the invention, the gas jet technique that rotary compressor is relevant is applied in the system easily, and the value on the production cause is large.

Claims (7)

1. rotary compressor, comprise the motor section (22) that is arranged in the seal casinghousing (1) and the compression mechanical part (21) of making two sections compression types, motor section (22) comprises stator and rotor (22b), compression mechanical part (21) comprises the first cylinder (23a) and the second cylinder (23b), drive first piston (28a) and the second piston (28b) and in the first cylinder compression chamber (24a) and the second cylinder compression chamber (24b), make respectively the bent axle (27) of eccentric rotary, and the main bearing (25) and the supplementary bearing (26) that support bent axle (27), the end of the first slide plate (29a) and the second slide plate (29b) joins with the periphery of first piston (28a) and the second piston (28b) respectively, it is characterized in that being inhaled into the second cylinder compression chamber (24b) from the gas that the first cylinder compression chamber (24a) spues in the seal casinghousing (1); Be provided with the first discharge valve (35a) and the middle baffler (33) of pressing on the described main bearing (25), the first discharge valve (35a) is communicated with the first cylinder compression chamber (24a) and the middle baffler (33) of pressing; Gas imports cylinder (33) and is set in outside the bent axle (27), the end that gas imports cylinder (33) communicates with the middle baffler (33) of pressing, gas imports the close rotor (22b) of opening of the other end of cylinder (33), rotor (22b) is upper to be provided with the rotor pore (22c) that connects more than along its axis, and the opening end of rotor pore (22c) is positioned at the scope at opening place that gas imports the other end of cylinder (33); One end opening of gas discharge pipe (33d) is in the outside of gas importing cylinder (33), and the other end of gas discharge pipe (33d) communicates with the middle baffler (33) of pressing; One end opening of gas suction pipe (33e) is in baffler (33) is pressed in the centre, and the other end of gas suction pipe (33e) communicates with the second cylinder compression chamber (24b).
2. rotary compressor according to claim 1, it is characterized in that described middle the pressure in the baffler (33) is provided with the first silencing cavity (33a) and the second silencing cavity (33b), the first discharge valve (35a) communicates with the first silencing cavity (33a), the other end of gas discharge pipe (33d) communicates with the first silencing cavity (33a), and an end opening of gas suction pipe (33e) is in the second silencing cavity (33b).
3. rotary compressor according to claim 1 and 2 is characterized in that being provided with the refrigerant injection device (16) that communicates with it on described the second cylinder compression chamber (24b).
4. rotary compressor according to claim 3 is characterized in that described refrigerant injection device (16) comprises the pipe (16c) that is inserted into the second cylinder (23b) side from the outside of seal casinghousing (2), be arranged on first of pipe (16c) the central authorities hole (16a) that spues, be arranged on the upper and perforate of the second cylinder (23b) in second of the second cylinder compression chamber (24b) hole (16b) that spues, be communicated with first spue hole (16a) and the second cylinder compression chamber (24b) expansion chamber and be positioned at expansion chamber for the spue safety check (16d) of hole (16a) of switching first.
5. rotary compressor according to claim 4 is characterized in that described pipe (16c) communicates with an end of coolant injection tube (17), and the other end of coolant injection tube (17) communicates with the upper space of gas-liquid separator (7).
6. rotary compressor according to claim 4 is characterized in that the upper end of described bent axle (27) is provided with rotor plectane (22e), and being provided with between the upper end of rotor plectane (22e) and rotor (22b) can be by the gap of gas.
7. rotary compressor according to claim 3, it is characterized in that described refrigerant injection device comprises U-shaped pipe (41), one end of this U-shaped pipe (41) is communicated with the shell space that is positioned at motor section (22) top, and the other end of U-shaped pipe (41) is communicated with the second cylinder compression chamber (24b).
CN 201010181068 2010-05-17 2010-05-17 Rotary compressor CN102251964B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN 201010181068 CN102251964B (en) 2010-05-17 2010-05-17 Rotary compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN 201010181068 CN102251964B (en) 2010-05-17 2010-05-17 Rotary compressor
PCT/CN2010/077124 WO2011143882A1 (en) 2010-05-17 2010-09-20 Rotary compressor

Publications (2)

Publication Number Publication Date
CN102251964A CN102251964A (en) 2011-11-23
CN102251964B true CN102251964B (en) 2013-03-13

Family

ID=44979458

Family Applications (1)

Application Number Title Priority Date Filing Date
CN 201010181068 CN102251964B (en) 2010-05-17 2010-05-17 Rotary compressor

Country Status (2)

Country Link
CN (1) CN102251964B (en)
WO (1) WO2011143882A1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102588254A (en) * 2012-02-22 2012-07-18 北京工业大学 Single dual-stage hermetically sealed refrigerating compressor with external mixing chamber
KR101981096B1 (en) 2012-10-12 2019-05-22 엘지전자 주식회사 Hemetic compressor
CN103775342A (en) * 2014-01-06 2014-05-07 广东美芝制冷设备有限公司 Rotary compressor
CN103727039A (en) * 2014-01-08 2014-04-16 广东美芝制冷设备有限公司 Two-stage compression rotary compressor, pump body assembly of two-stage compression rotary compressor, and air conditioning system
EP3163084B1 (en) * 2014-06-24 2018-08-15 Panasonic Intellectual Property Management Co., Ltd. Rotary compressor having two cylinders
CN106151049A (en) * 2015-04-07 2016-11-23 珠海格力节能环保制冷技术研究中心有限公司 Compressor and air conditioning system
CN105698425B (en) * 2016-02-22 2018-06-15 广东美芝制冷设备有限公司 Refrigerating plant

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1004219B (en) * 1984-11-06 1989-05-17 株式会社东芝 Rotary compressor for refrigerant
JP3037391B2 (en) * 1989-10-12 2000-04-24 カール・ツアイス―スチフツング Coordinate measuring machine detection head
JP2005264878A (en) * 2004-03-19 2005-09-29 Sanyo Electric Co Ltd Horizontal type rotary compressor
CN1227459C (en) * 2000-03-30 2005-11-16 三洋电机株式会社 Multi-stage compressor
CN100347452C (en) * 2002-06-05 2007-11-07 三洋电机株式会社 Rotary compressor and method for manufacturing same and removal volumetric proportions setting method
CN201025261Y (en) * 2007-04-26 2008-02-20 珠海格力电器股份有限公司 Rotary compressor with gas spraying and enthalpy addition function
JP2008286037A (en) * 2007-05-16 2008-11-27 Fujitsu General Ltd Rotary compressor and heat pump system
CN101344091A (en) * 2008-08-16 2009-01-14 广东美芝制冷设备有限公司 Coolant injection device and control method of rotary compressor
CN201351607Y (en) * 2008-09-10 2009-11-25 珠海格力电器股份有限公司 Rotary compressor with air jet system
CN101684804A (en) * 2008-09-27 2010-03-31 乐金电子(天津)电器有限公司 Two-stage rotating type compressor

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2507047B2 (en) * 1989-05-09 1996-06-12 松下電器産業株式会社 Two-stage compression rotary compressor
JPH0337391A (en) * 1989-07-04 1991-02-18 Hitachi Ltd Rotary compressor

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1004219B (en) * 1984-11-06 1989-05-17 株式会社东芝 Rotary compressor for refrigerant
JP3037391B2 (en) * 1989-10-12 2000-04-24 カール・ツアイス―スチフツング Coordinate measuring machine detection head
CN1227459C (en) * 2000-03-30 2005-11-16 三洋电机株式会社 Multi-stage compressor
CN100347452C (en) * 2002-06-05 2007-11-07 三洋电机株式会社 Rotary compressor and method for manufacturing same and removal volumetric proportions setting method
JP2005264878A (en) * 2004-03-19 2005-09-29 Sanyo Electric Co Ltd Horizontal type rotary compressor
CN201025261Y (en) * 2007-04-26 2008-02-20 珠海格力电器股份有限公司 Rotary compressor with gas spraying and enthalpy addition function
JP2008286037A (en) * 2007-05-16 2008-11-27 Fujitsu General Ltd Rotary compressor and heat pump system
CN101344091A (en) * 2008-08-16 2009-01-14 广东美芝制冷设备有限公司 Coolant injection device and control method of rotary compressor
CN201351607Y (en) * 2008-09-10 2009-11-25 珠海格力电器股份有限公司 Rotary compressor with air jet system
CN101684804A (en) * 2008-09-27 2010-03-31 乐金电子(天津)电器有限公司 Two-stage rotating type compressor

Also Published As

Publication number Publication date
WO2011143882A1 (en) 2011-11-24
CN102251964A (en) 2011-11-23

Similar Documents

Publication Publication Date Title
CN101201050B (en) Rotary compressor, and car air conditioner and heat pump type water heater using the compressor
CN101892984B (en) Scroll machine
CN101205916B (en) Steam injection system of eddy compressor
CN102996445B (en) Compressor and oil cooling system
CN101235815B (en) Multistage compressor
US6350111B1 (en) Scroll machine with ported orbiting scroll member
CN1993555B (en) Capacity variable device for rotary compressor and driving method of air conditioner having the same
KR100724047B1 (en) Scroll compressor and refrigerating apparatus
CN100585186C (en) The variable capacity type rotary compressor
US6746215B2 (en) Compressor
AU2002301427B2 (en) Scroll compressor with vapor injection
EP2055956A1 (en) Multistage compressor
EP1253323A2 (en) Hermetic compressors
CN107448383B (en) Scroll compressor
US7563080B2 (en) Rotary compressor
US7229261B2 (en) Scroll compressor having an annular recess located outside an annular seal portion and another recess communicating with suction port of fixed scroll
CN104728109B (en) Air conditioning system and rotating compressor component thereof
US4781542A (en) Hermetically-sealed compressor with motor
US6264446B1 (en) Horizontal scroll compressor
JP4365729B2 (en) Rotary compressor
KR20070009958A (en) Rotary type two stage compressor
ES2670508T3 (en) Spiral compressor
CN100453813C (en) Apparatus for varying capacity in scroll compressor
CN101165350B (en) Vortex compressor
US8177522B2 (en) Mode changing apparatus for a scroll compressor

Legal Events

Date Code Title Description
PB01 Publication
C06 Publication
SE01 Entry into force of request for substantive examination
C10 Entry into substantive examination
GR01 Patent grant
C14 Grant of patent or utility model