CN104747444B - Rotary compressor and refrigerating circulatory device - Google Patents

Abstract

The invention discloses a kind of rotary compressor and refrigerating circulatory device.Rotary compressor includes：Possesses the motor of stator and rotor；Compression mechanism, compression mechanism include with rotor rotational slide and eccentric shaft with the axle mesopore to its shaft part opening, compression mechanism are provided with compression chamber, compression chamber is built-in by eccentric shaft-driven compression assembly；Torsion-bar spring, the both sides motion end of torsion-bar spring connects rotor and axle mesopore respectively.In the action of compression assembly, the difference of the anglec of rotation of eccentric shaft and the anglec of rotation of rotor is phase angle, and phase angle has increase and decrease.Rotary compressor of the invention, rotor can cause angular speed stabilization, the problem that electric efficiency will not be produced to decline by the torque buffering effect of torsion-bar spring.

Description

Rotary compressor and refrigerating circulatory device

Technical field

The present invention relates to refrigerating field, more particularly, to a kind of rotary compressor and refrigerating circulatory device.

Background technology

In order to reduce the rotary vibration of rotary compressor, the motor torque control of the Waveform composition correlation of DC variable-frequency motors Technology obtains motion in or so nineteen ninety, and thereafter, the application of the method gets along with always.Motor torque control technology, is in inspection While surveying rotor rotation position, detection axle square changes, and carries out the synthesis of motor torque waveform, makes motor torque with eccentric axle power Square (hereinafter referred to as axle square) is approximate, makes the rotor velocity stabilization in rotation.But, the shortcoming of Waveform composition be electric efficiency meeting Reduce, so being used in the limited scope such as low velocity mostly.

The content of the invention

It is contemplated that at least solving one of technical problem in correlation technique to a certain extent.

Therefore, the present invention proposes a kind of rotary compressor, rotor can be made by the torque buffering effect of torsion-bar spring Obtain angular speed stabilization, the problem that electric efficiency will not be produced to decline.

The present invention proposes a kind of refrigerating circulatory device with above-mentioned rotary compressor.

Rotary compressor according to embodiments of the present invention, including：Possesses the motor of stator and rotor；Compression mechanism, institute Stating compression mechanism includes and the rotor rotational slide and eccentric shaft, the compressor with the axle mesopore to its shaft part opening Structure is provided with compression chamber, and the compression chamber is built-in by the eccentric shaft-driven compression assembly；Torsion-bar spring, the torsion-bar spring Both sides motion end connects the rotor and the axle mesopore respectively；In the action of the compression assembly, the rotation of the eccentric shaft The difference of the anglec of rotation of angle and the rotor is phase angle, and the phase angle has increase and decrease.

Rotary compressor according to embodiments of the present invention, rotor can be caused by the torque buffering effect of torsion-bar spring Angular speed stabilization, the problem that electric efficiency will not be produced to decline, simple structure and easy to manufacture, while torsion-bar spring can be applied In various electric motors, with stronger interchangeability.

In some embodiments of the invention, it is circular or non-circular linear that the torsion-bar spring is formed as section Axle is turned round, the linear both sides motion end at least one party for turning round axle is cylinder or polygon.

In further embodiment of the present invention, rotary compressor also includes the phase of the scope at the limitation phase angle Angle limiting part.

Some embodiments of the invention, possess the pipe with the eccentric shaft rotational slide in the rotor.

Further, the motion end of described torsion-bar spring one end is connected with the pipe.

In some embodiments of the invention, in the rotor and the sliding surface of the eccentric shaft rotational slide, possess Expand the circumferential groove in the gap of the sliding surface.

Some embodiments of the invention, the torsion-bar spring is configured to increase, twisting resistance with its torsion angle Square rate or spring constant can increased non-linear torsion-bar spring.

In a particular embodiment of the present invention, the phase angle limiter assembly includes being located at the pipe and the eccentric shaft In projection on either one.

In specific example of the invention, rotary compressor possesses to perforate in the axle mesopore and the circumferential groove Intercommunicating pore.

Some specific embodiments of the invention, at least one party of the motion end of the torsion-bar spring is provided with gas and passes through Gas grooves.

In some embodiments of the invention, in the scope of the axial length of the torsion-bar spring, it is provided with for reduction and institute State the amplitude controlling component in the gap of axle mesopore.

Refrigerating circulatory device according to embodiments of the present invention, including rotary compression according to the above embodiment of the present invention Machine.

Refrigerating circulatory device according to embodiments of the present invention, by being provided with above-mentioned rotary compressor, rotor can lead to The torque buffering effect for crossing torsion-bar spring causes angular speed stabilization, the problem that electric efficiency will not be produced to decline.

Brief description of the drawings

Fig. 1 is related to embodiments of the invention 1, represents the company of the longitudinal section and kind of refrigeration cycle inside rotary compressor Connect；

Fig. 2 is related to the embodiment 1, the design drawing of torsion-bar spring；

Fig. 3 is related to the embodiment 1, represents the torsion-bar spring of insertion eccentric shaft；

Fig. 4 is related to the embodiment 1, the sectional view of rotor；

Fig. 5 is related to the embodiment 1, represents the detailed sectional view of the assembling of the composition and rotor of compression key element；

Fig. 6 is related to the embodiment 1, the plan from terms of rotor upper end；

Fig. 7 is related to the embodiment 1, represents the eccentric shaft become in moving curve and motion and the rotation position of rotor of axle square Put the concept map with phase angle；

Fig. 8 is related to the embodiment 1, represents the concept map of the nonlinear characteristic of torsion-bar spring；

Fig. 9 is related to embodiments of the invention 2, represents the assembling figure of main shaft and rotor；

Figure 10 is related to the embodiment 2, is the plan from terms of the last time of rotor, represents the limitation of phase angular region；

Figure 11 is related to the embodiment 2, represents alternate design case；

Figure 12 is related to embodiments of the invention 3, represents the assembling of eccentric shaft and rotor；

The plan that Figure 13 is related to the embodiment 3, expression is from terms of the upper end of rotor；

Figure 14 is related to embodiments of the invention 4, represents the assembling of eccentric shaft and rotor.

Reference：

1 ‥ rotary compressors, 2 ‥ housings, 3 ‥ motors, 4 ‥ stators, 5 ‥ compression mechanisms, 10 ‥ eccentric shafts, 11 ‥ masters Axle, 14 ‥ axles mesopores, 15 ‥ circumferential grooves, 30 ‥ rotors, 35 ‥ pipes, 36 ‥ pipes ends, 36a ‥ pipes projection, 40 ‥ torsion bars Spring, 41 ‥ turn round axle, 43 ‥ R torques rods, 45 ‥ R motion ends, 46 ‥ C motion ends

Specific embodiment

Embodiments of the invention are described below in detail, the example of the embodiment is shown in the drawings.Below with reference to The embodiment of Description of Drawings is exemplary, it is intended to for explaining the present invention, and be not considered as limiting the invention.

In the description of the invention, it is to be understood that term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, "front", "rear", "left", "right", " vertical ", " level ", " top ", " bottom " " interior ", " outward ", " up time The orientation or position relationship of the instruction such as pin ", " counterclockwise ", " axial direction ", " radial direction ", " circumference " be based on orientation shown in the drawings or Position relationship, is for only for ease of the description present invention and simplifies description, must rather than the device or element for indicating or imply meaning With specific orientation, with specific azimuth configuration and operation, therefore must be not considered as limiting the invention.

Additionally, term " first ", " second " are only used for describing purpose, and it is not intended that indicating or implying relative importance Or the implicit quantity for indicating indicated technical characteristic.Thus, define " first ", the feature of " second " can express or Implicitly include at least one this feature.In the description of the invention, " multiple " is meant that at least two, such as two, three It is individual etc., unless otherwise expressly limited specifically.

In the present invention, unless otherwise clearly defined and limited, term " installation ", " connected ", " connection ", " fixation " etc. Term should be interpreted broadly, for example, it may be fixedly connected, or be detachably connected, or integrally；Can be that machinery connects Connect, or electrically connect or can communicate each other；Can be joined directly together, it is also possible to be indirectly connected to by intermediary, can be with Be two element internals connection or two interaction relationships of element, unless otherwise clearly restriction.For this area For those of ordinary skill, above-mentioned term concrete meaning in the present invention can be as the case may be understood.

Rotary compressor 1 according to embodiments of the present invention is described in detail below with reference to Fig. 1-Figure 14, wherein rotary pressure Contracting machine 1 can be mounted in the refrigerating circulatory devices such as air-conditioning, refrigerator, refrigeration plant, water heater.

Rotary compressor 1 according to embodiments of the present invention, including：Motor 3, compression mechanism 5 and torsion-bar spring 40, its In, motor 3 possesses stator 4 and rotor 30.Compression mechanism 5 is included with the rotational slide of rotor 30 and with the axle to its shaft part opening The eccentric shaft 10 of mesopore 14, compression mechanism 5 are provided with compression chamber, the built-in compression assembly driven by eccentric shaft 10 of compression chamber.Can be with Understand, compression mechanism 5 includes the elements such as cylinder 50, base bearing 55 and supplementary bearing 56, compression assembly includes piston 52 and slides It is enclosed within eccentric shaft 10 and in compression chamber outside piece 53, piston 52, slide plate 53 is located in the vane slot of cylinder 50 and slide plate 53 Tip stop and being against on the periphery wall of piston 52.

The both sides motion end of torsion-bar spring 40 connects rotor 30 and axle mesopore 14 respectively, and torsion-bar spring 40 limits rotor 30 And the torque buffer unit between eccentric shaft 10.Wherein the load of rotor 30 is supported by torsion-bar spring 40.

In the action of compression assembly, the difference of the rotation angle θ 1 of eccentric shaft 10 and the rotation angle θ 2 of rotor 30 is phase angle θ 3, Phase angle θ 3 has increase and decrease.

Rotary compressor 1 according to embodiments of the present invention, rotor 30 can buffer effect by the torque of torsion-bar spring 40 Fruit causes angular speed stabilization, the problem that the efficiency of motor 3 will not be produced to decline, simple structure and easy to manufacture, while torsion-bar spring 40 can apply in various electric motors 3, with stronger interchangeability.

In a particular embodiment of the present invention, it is circular or non-circular linear torsion that torsion-bar spring 40 is formed as section Axle, the linear both sides motion end at least one party for turning round axle is cylinder or polygon.

In further embodiment of the present invention, rotary compressor 1 also includes the phase of the scope of limitation phase angle θ 3 Angle limiting part.Wherein phase angle limiting part includes being located in pipe 35 and eccentric shaft 10 projection on either one.For example exist In the example of Fig. 9, phase angle limiting part includes the pipe projection 36a being located on pipe 35 with the shaft end for being located at eccentric shaft 10 Main shaft projection 11e.So as to by being provided with phase angle limiting part, be able to be kept away with the higher limit at qualification phase angle and lower limit Exempt from the excessive motor 3 for causing in phase angle to shut down, the excessive loads to torsion-bar spring 40 can be reduced, improve reliability.

Some embodiments of the invention, possess the pipe 35 with the rotational slide of eccentric shaft 10 in rotor 30.

In specific example of the invention, the motion end of the one end of torsion-bar spring 40 is connected with pipe 35.

Some embodiments of the invention, in rotor 30 and the sliding surface of the rotational slide of eccentric shaft 10, possess expansion The circumferential groove 15 in the gap of sliding surface.Further, possess to the intercommunicating pore 11c of perforate in axle mesopore 14 and circumferential groove 15 (i.e. It is following oilhole 11c), that is to say, that it is right in circumferential groove 15 that the lubricating oil of axle mesopore 14 can be entered into by intercommunicating pore 11c Sliding surface is lubricated.

Some specific embodiments of the invention, torsion-bar spring 40 is configured to increase, torsion with its torsion angle Torque rate or spring constant can increased non-linear torsion-bar spring 40.Preferably, torsion-bar spring 40 is non-linear torsion-bar spring When, rotary compressor 1 includes phase angle limiting part.

In specific example of the invention, at least one party of the motion end of torsion-bar spring 40 is provided with the gas that gas passes through Groove.

Some embodiments of the invention, in the scope of the axial length of torsion-bar spring 40, are provided with reduction and axle The amplitude controlling component in the gap in hole 14.Wherein amplitude controlling component can be the damping ring 41a of cylinder.

Refrigerating circulatory device according to embodiments of the present invention, including rotary compressor according to the above embodiment of the present invention 1。

Refrigerating circulatory device according to embodiments of the present invention, by being provided with above-mentioned rotary compressor 1, rotor 30 can be with Angular speed stabilization, the problem that the efficiency of motor 3 will not be produced to decline are caused by the torque buffering effect of torsion-bar spring 40.

The rotary compressor according to different embodiments of the invention is described in detail below with reference to Fig. 1-Figure 14.

Embodiment 1

The present embodiment is the application examples of the single cylinder rotary compressor for using single phase induction motor.Fig. 1 represents rotary pressure The composition of contracting machine 1 and kind of refrigeration cycle.

Rotary compressor 1 is by the compression mechanism 5 being fixed on the cylindrical shell 2 of sealing, the structure of motor 3 of its top configuration Into stator 4 is fixed on housing 2.Therefore, compression mechanism 5 is driven by the turning moment of the rotor 30 produced between stator 4 It is dynamic.In addition, the bottom storage of housing 2 lubricating oil (not shown).

The present embodiment feature be in the main shaft 11 of eccentric shaft 10 set axle mesopore 14 in be equipped with torsion-bar spring 40, The C motion ends 46 and R motion ends 45 that its two ends is equipped with are connected to eccentric shaft 10 and rotor 30 and possess eccentric shaft 10 respectively The rotor 30 of main shaft 11 and pipe 35 can enter line slip and rotate by the scope of the predetermined anglec of rotation.

As conventional rotary compressor, by the rotation of eccentric shaft 10, from the lubricating oil of its lower end suction (with Under, be referred to as oil), the pump chamber 13a (Fig. 5) that possesses by the inside of eccentric shaft 10 is to fuel feeding in each slip component.

The vibration of rotary compressor 1 is made up of the resultant vibration of direction of rotation and normal direction, and rotary vibration is due to axle The variation of square, method linearly coupled is produced due to the unbalanced quality that the rotating band of eccentric shaft 10 and piston 52 comes.These vibrate into / in, rotary vibration accounts for the major part of the resultant vibration of rotary compressor 1.In addition, the vibration reduction of principle upper rotary is compared Difficulty, normal vibration reduction is easier.

Next, carrying out simple illustration to refrigeration system.Sucked to compression mechanism 5 from suction line 9 by reservoir 94 Low-pressure gas, compressed in cylinder 50, be discharged to the inside of housing 2.Therefore, the pressure of housing 2 is high pressure.

To housing 2 discharge gases at high pressure, by from blast pipe 4 to outdoor heat exchanger 91, expansion valve (or capillary) 92, The sequential flowing of indoor heat exchanger 93, reservoir 94.Air-conditioner due to outside air temperature variation with indoor heat exchanger 91 temperature The pressure change of the gases at high pressure that change is caused is big, and with the proportional pressure, the axle square of eccentric shaft 10 has fierce increase and decrease.And, The pressure of housing 2 can all produce same axle square to change either in high-pressure side or low-pressure side.

Torsion-bar spring 40 shown in Fig. 2, the cylindrical type R motion ends 45 and C of turning round axle 41 and the integration of its two ends by circle Motion end 46 is constituted.R motion ends 45 and C motion ends 46 possess gas grooves 45a and rod hole 45b, gas grooves 46a and rod hole respectively 46b.Gas grooves 45a and gas grooves 46a are the grooves that mixed oil and gas pass through.

Rod hole 45b and rod hole 46b refer to the hole of R torques rod 43 and C torques rod 44 shown in insertion Fig. 2 respectively.R motion ends 45 It is connected with rotor 30 and eccentric shaft 10 with C motion ends 46, respectively through R torques rod 43 and C torques rod 44.Torsion-bar spring 40 and this A little torque rods, it is the means being delivered to the torque of rotor 30 on eccentric shaft 10, is the trunk component of torque buffer unit.

Fig. 3 is the torsion-bar spring 40 assembled in the axle mesopore 14 of eccentric shaft 10.It is assembled below is illustrated.From axle Insert the C motion ends 46 of torsion-bar spring 40 in one side openend of mesopore 14.Here, moving the rod hole 11a possessed in main shaft 11 and C The C rods hole 46b for making end 46 is consistent, and if press-in C torques rod 44, C motion ends 46 can be fixed on main shaft 11.

At this moment, R motion ends 45 have in the open end side of axle mesopore 14, R motion ends 45 and are rotated between axle mesopore 14 The only gap slided.In addition, torsion axle 41 has the necessary gap between axle mesopore 14, so without the internal diameter with axle mesopore 14 Contact can just twist rotation.Therefore, the turning moment of R motion ends 45, be delivered on eccentric shaft 10 by turning round axle 41.In addition, The thin footpath axle 11b of main shaft 11 constitutes circumferential groove 15 between the pipe 35 of rotor described later 30.

Fig. 4 is that rotor 30 is completed figure.Rotor 30 be on possessing end ring 32 and end ring under 33 rotor core 31, Hot jacket is assembled in the pipe 35 in the centre bore, the composition of the balance weight on each end ring.In addition, also having in pipe 35 The end ring groove 32a possessed on 36,2, the pipe end axis of rod hole 36b of rod hole 36b.

Fig. 5 represents the assembling of compression mechanism 5 and rotor 30.Other Fig. 6 is the plan seen from the upside of rotor 30.Should In figure, rotor 30 rotates in the counterclockwise direction.First, external diameter insertion and the rotor 30 of the main shaft 11 of support are slided by base bearing 55 The internal diameter of the pipe 35 of integration.Possessing between them can be with the small glade plane space of rotational slide.

Secondly, in R motion ends 45, R torques rod 43 is inserted from the gap of end ring groove 32a, by rod hole 36b and rod hole After the order press-in of 45b, R motion ends 45 and pipe end 36 can combine, and complete assembling.As a result, the torque of rotor 30 passes through R Torque rod 43 turns into the turning moment of R motion ends 45, further passes through torsion-bar spring 40 from C torques rod 44 as to eccentric shaft 10 Turning moment.

In addition, C motion ends 46 fixed in the present embodiment, in axle mesopore 14 and C torques rod 44, configuration are in main shaft 11 and master The slipper of bearing 55, but as needed, can change in pump chamber 13a or be the rotational slide of rotor 30 and main shaft 11 In part.That is, the present invention is favourable in terms of the design freedom of the length direction of torsion-bar spring 40.In addition, solid on R motion ends 45 Fixed R torques rod 43, have both support rotor 30 rotary shaft above-below direction burden functional.Therefore, the rotational slide of rotor 30 The thrust loss for bringing will not be produced.

When maximum relative to the anglec of rotation of the rotor 30 of main shaft 11, i.e. phase angle below 1 turn, if it is considered that these If rotational slide part does not have big side pressure to work, preferably reduce and slide length, make the rotation of pipe 35 smooth.Main shaft 11 In constituted between the thin axle 11b that possesses and the internal diameter of pipe 35 circumferential groove 15, be reduce pipe 35 slip grow reach it is above-mentioned The means of purpose.In addition, circumferential groove 15 has the effect of the mismachining tolerances of aspect such as the linearity of permission main shaft 11 and pipe 35.

The oilhole 11c of connection shaft mesopore 14 and circumferential groove 15 is the fuel feeding means to above-mentioned sliding surface, from pump chamber 13a out To a small amount of oil for passing through of axle mesopore 14, by oilhole 11c and circumferential groove 15 to sliding surface fuel feeding.In addition, additional to above-mentioned The oil groove of the two ends perforate of sliding surface is also good.

Gas grooves 46a and gas grooves 45a, passed through from pump chamber 13a a small amount of oil out and the gas in being dissolved in oil Axle mesopore 14 is discharged into the hole of the upper end side of rotor 30, and the pressure of pump chamber 13a is uniform, with the effect for maintaining oil pump performance.

Next, by piston 52 and slide plate 53 be divided into 2 compression chambers of part 51 of low pressure chamber and high pressure chest, suck it is low Calm the anger body while, compression and low pressure gas turn into high pressure.The eccentric shaft 10 of eccentric drive is carried out to piston 52, is being compressed and is being vented The wheelbase for being generated in stroke drastically changes.

The above-mentioned axle square that Fig. 7 longitudinal axis is illustrated in 1 turn of rotor 30 changes.In addition, to rotor 30 and eccentric shaft 10 The process of the anglec of rotation has carried out conceptual diagram.Here, on the basis of the angle of the eccentric direction of eccentric shaft 10 point, as 0 degree, the inner circumferential of compression chamber 51 is 360 degree, the angle split at equal intervals is θ.

Here, with the anglec of rotation of eccentric shaft 10 (●) for θ 1, the anglec of rotation (zero) of rotor 30 for θ 2 when, it is poor θ 3=θ 2- θ 1 are their phase angles.θ 3 is also the windup-degree of torsion-bar spring 40.In addition, axle square (Tc) minimum 0 degree or During 360 degree of person, the anglec of rotation of rotor 30 is consistent with the anglec of rotation of eccentric shaft 10.

Axle square Tc starts to increase in the compression travel of the about 25 degree of beginnings in suction hole opening, for most about when 180 degree Greatly, afterwards, instroke is gone to, with the reduction of capacity, axle square can reduce, is minimum at about 360 degree or so.Inhale herein Tolerance again passes by about 25 degree and goes to compression travel for maximum, eccentric shaft 10.

The rotor anglec of rotation by 0 degree towards 90 degree rotation when, Tc can rapidly increase.But, due to the torsion of torsion-bar spring 40 Turn effect, the angular speed of eccentric shaft can reduce, but rotor 30 can maintain angular speed, so θ 3 can gradually increase.And, towards Tc When being rotated for maximum 180 degree, the angular speed of eccentric shaft can further reduce, but the rotor anglec of rotation can maintain angular speed, institute It is of about 180 degree with its anglec of rotation.Therefore, θ 3 is increased about 90 degree.

And, when Tc reaches maximum 180 degree, the rotor anglec of rotation is 240 degree, θ 3 is about expanded to 120 degree.This When, torsion-bar spring 40 reaches 120 degree of its torsion angle, puts aside rotating energy.

The anglec of rotation of eccentric shaft is by the way that after 180 degree, Tc rapidly reduces, so torsion-bar spring 40 discharges the energy of savings, Reduce windup-degree.Therefore, the eccentric shaft that the anglec of rotation has delay can increase angular speed, so θ 3 can be reduced.

Therefore, when θ is near 270 °, the anglec of rotation of eccentric shaft be about 250 degree, the rotor anglec of rotation be about 270 degree, So, θ 3 is about 20 degree.Thereafter, when eccentric shaft reaches 360 degree, θ 3 is 0 degree, the anglec of rotation one of rotor 30 and eccentric shaft 10 Cause.At this moment, the windup-degree of torsion-bar spring 40 is also 0 degree.

Like this, among 1 turn of rotor 30, the maximum of torsion-bar spring 40 can rotate to 120 degree to the present embodiment, put aside energy Amount, thereafter, discharges rotating energy.Savings and release action by the torque, rotor 30 will not be subject to the angle speed of eccentric shaft 10 The considerable influence of the change of degree, can maintain certain angular speed.Therefore, the axle square of eccentric shaft 10 changes the rotary pressure for causing The whirling vibration of contracting machine 1 can be reduced.

Here, the present embodiment remarks additionally to the advantage for selecting torsion-bar spring 40.

Even the twisting that 40 1 turns of torsion-bar spring, it is also possible to play very strong turning moment.And, because be not with its The spring of his component contact, so the answer speed in high-speed cruisings such as 120rps is fast, for projected life at 30,000 hours The Reliability of Microprocessor of longtime running is also very high.

Even that is, the windup-degree of torsion-bar spring 40 be also greatly 1 turn (360 degree) below, as the rotation for needing strength The torque buffer of the rotary compressor of torque and longtime running is most suitable.And, bar-shaped torsion-bar spring 40 is very Easily it is accommodated in inside eccentric shaft, is suitable component for the rotary compressor small to volume.In addition, torsion-bar spring 40 is very Easy to manufacture, cost is also cheap.

Embodiment 2

The maximum of phase angle θ 3 has larger fluctuation due to the difference of service condition.The rotary pressure carried in air-conditioner In the case of contracting machine, in general, θ 3 is proportional to the difference of high side pressure and low-pressure lateral pressure to become big.In general, θ 3 exists When refrigerating operaton, can become big daytime high in air conditioner load, air conditioner load small night can diminish.But, heating fortune It is opposite when row.And, in carrying the machine of the variable variable-frequency motor of rotary speed, still air conditioner load, does not consider also The inertia mass of rotor.

As described above, in the condition variations such as operating load, if θ 3 is excessive, the synchronization of stator and rotor cannot be maintained Speed, that is to say, that can produce step-out phenomenon, motor may stop suddenly.The present embodiment as solve the problem means, It is relevant with the technology for preventing phase angle θ 3 excessive and correctly set in advance in the design phase scope of phase angle θ 3.

Fig. 8 as these problems solution, the spring performance of torque buffer unit is set to it is non-linear, make its with The size of phase angle θ 3, increases spring constant.Transverse axis be the phase angle θ 3, longitudinal axis for torsion-bar spring 40 generation torque Ts or Spring constant K.Curve A is nonlinear spring, and straight line B is common Hookean spring.

Relative to the increase of the increased Ts or K of θ 3, Hookean spring B is certain, and nonlinear spring A is with the increasing of θ 3 Plus, increment rate can become big.Therefore, with axle square increase conversely, the increment rate of θ 3 can reduce.The non-linear torsion-bar spring, relatively Maximum, the problem that prevent θ 3 excessive in axle square.

Solution shown in from Fig. 9 to Figure 11, is two parts by the higher limit of θ 3 and lower limit, or certain portion Divide the gimmick limited by limiting plate, set the value of θ 3 in the design phase in advance.That is, phase angle θ 3 passes through the He of eccentric shaft 10 The difference decision of the anglec of rotation of rotor 30, if paying close attention to this point, between eccentric shaft 10 and rotor 30, can be by additional rotation Corner limiting means determine the higher limit and lower limit of θ 3.

In fig .9, if the anglec of rotation of the pipe projection 36a for possessing in the internal diameter at pipe end 36 is maximum, with main shaft 11 The main shaft projection 11e that possesses of shaft end contacted.Thereafter, eccentric shaft 10 and rotor 30 are rotated by identical angular speed, so The increase of phase angle θ 3 can stop.

This acts through Figure 10 and illustrates.In the stopping of rotor 30, such as left figure pipe projection 36a and main shaft projection 11e Stop after contact.At this moment θ 3=0 °.If increasing axle square in the anticlockwise rotation of rotor 30, θ 3 can increase, pipe Projection 36a is contacted with the side of main shaft projection 11e the opposing party, can be stopped (right figure).The anglec of rotation of pipe projection 36a at this moment The maximum of θ 3, because axle square thereafter increases, θ 3 will not increase, and rotor 30 and eccentric shaft 10 are carried out by identical angular speed Rotation.

The anglec of rotation of eccentric shaft 10 is advanced, and if axle square is reduced, pipe projection 36a leaves main shaft projection 11e, θ 3 and diminishes, If axle square minimum, θ 3 is zero, returns to the position of left figure.That is, in 1 turn of rotor 30, θ 3 is θ3 Higher limit and lower limit be respectively 180 degree and 0 degree.

In the design, the lower limit of θ 3 is set as there is gap between 0 ° but pipe projection 36a and main shaft projection 11e, such as If θ 3=-30 °, in the rotation of rotor 30 or after rotor 30 stops, θ 3=-30 °, to need torsion-bar spring 40 to carry out big The twisting of opposite direction.But, the torque of rotor 30 is generally bigger than axle square, so reverse twisting is not had, even just stop When, also will not be θ 3=-30 ° therefore, 2 projections will not be contacted.

On the other hand, the higher limit of θ 3 is set as the θ 3 in 180 ° but the generally maximum of axle square or the axle square of prediction Maximum if if 150 °, until 2 projections contacts, also 30 ° of surplus.In the design phase, to θ 3 Lower limit and higher limit stay a little surpluses, make 2 discontiguous words of projection, it is prevented that 2 projections in Practical Condition Contact.And, with above-mentioned nonlinear spring and if using it is also good.

By above-mentioned design techniques, the excessive motor stopping for causing of phase angle θ 3 or the excessive loads to torsion-bar spring can To reduce, reliability is improved.Furthermore it is possible to prevent the percussion and damage that the impact of projection causes.

Figure 11 represents the above-mentioned pipe projection 36a of replacement, using the method for R torques rod 43.Left figure is the Y-Y sections of right figure. According to the method, the higher limit of phase angle θ 3 may be limited to below 180 degree, it is convenient to omit pipe projection 36a.

Embodiment 3

Embodiment 1 is manufacture method fixed in compression mechanism 5 and the housing inner diameter of the integration of rotor 30.Relative to this Mode, compression mechanism 5 and stator 4 are fixed on after the internal diameter of housing 2, and rotor 30 is inserted into the method that main shaft 11 is assembled Also there is popularization.The present embodiment is correspondence later approach.

In Figure 12 and Figure 13, in the center at R motion ends 45 and pipe end 36, possesses the rod groove to their outer openings 45c (Figure 13) and pipe groove 36c.After inserting rotor 30 in main shaft 11, make the fluting direction of above-mentioned 2 grooves consistent, by R torques Rod 43 is inserted in these grooves.Thereafter, in the circle for being the peripherally inserted plain washer 47 and then possessing in R motion ends 45 of R motion ends 45 Embedded C grades of ring 48 in circumferential groove, such rotor 30 is secured to R motion ends 45 and suffers.

The oscillation crosswise that cylindrical damping ring 41a shown in Figure 12, the resonance of the torsion rotation due to turning round axle 41 cause, can To evade the situation that axle 41 conflicts with the inwall generation of axle mesopore 14 of turning round.In addition, only having very between damping ring 41a and axle mesopore 14 Small glade plane space.

Damping ring 41a changes the internal diameter design of the variable-frequency motor, reduction axle mesopore 14 of rotating speed in wide scope, also has, big It is necessary when torsion-bar spring 40 is more long in type rotary compressor.The design of damping ring 41a, can select and turn round axle 41 1 Method or the design turned round on axle 41 is fixed on as other component that body shapes.

In addition, in main shaft 11, to the stomata 11d of perforate in axle mesopore 14 and housing 2, with the C used with embodiment 1 Gas grooves 46a and R gas grooves 45a equal function.

Embodiment 4

Embodiment 4 shown in Figure 14 is using cases of design of the invention in the DC variable-frequency motors for not needing end ring.Make For the pipe 35 used in the grade of embodiment 1 will be discarded, feature is that the design and manufacture of rotor 30 are succinct.

Rotor 30 is made up of the iron core plate 39 and magnet (not shown) that are laminated, and they are combined by several rivet 31c.Iron The internal diameter of core plate 39 has two kinds, and each with the column part of the rotational slide of main shaft 11, and the periphery of R motion ends 45 has embedded Hexagon ring 31a parts constitute.In addition, shape of the upper end side of R motion ends 45 for hex screw.In addition, plain washer 47 is in insertion Installed before to the main shaft 11 of rotor 30.

After R motion ends 45 are embedded into hexagon ring 31a, C grades of ring 48 is fixed in the groove of R motion ends 45.As a result, rotor 30 Assembling with R motion ends 45 is just completed, and internal diameter and the main shaft 11 of rotor 30 are slidably supported.The shaft end of main shaft 11 and rotor Possesses end play 31b between 30 internal diameter, so the thrust load of rotor 30 will not be produced.R motion ends 45 and iron core plate 39 if if wabbler screw form, the intensity of this part can be lifted.

Can be omitted according to the present embodiment, in the middle pipe 35 for using such as embodiment 1 and torque rod 43, reach reduction manufacture The effect of cost.In addition, the assembling design of the R motion ends 45 of the present embodiment announcement and rotor 30 can be applied above-mentioned all of In embodiment.

The present invention refers to not only induction machine, can also be applied in the variable-frequency motor of variable speed.In addition, by eccentric shaft Horizontal positioned it is horizontal, also make in housing for that can also be applied in the rotary compressor of low pressure.In addition, these compressors are taken It is loaded in air-conditioner, fridge-freezer, water heater, vehicle-mounted freezing and air-conditioning device.

In summary, the invention problem to be solved is：Due to the eccentric axle power of the rotary compressor that gas compression brings Square changes, and brings the angular speed of the rotor being directly connected to eccentric shaft to change, and causes the whirling vibration of compressor.

Solving a specific embodiment of the use of above-mentioned problem is：The pipe 35 being fixed in the internal diameter of rotor 30 and master The rotational slide of axle 11.The motion end twice 46 and 45 of the torsionspring 40 received in the axle mesopore 14 of main shaft 11 connects main shaft respectively 11 and pipe 35.Eccentric shaft 10 makes angular speed change with the increase and decrease axle of axle power square, but rotor 30 can be by reversing bullet The torque buffering effect of spring 40 makes angular speed stabilization.

Rotary compressor according to embodiments of the present invention buffers dress by rotor 30 and eccentric shaft 10 using torque Put and have the following advantages that：

(1) present invention uses torsion-bar spring, so benefit can be to be accommodated in inside eccentric shaft.

(2) can apply in a variety of electric motors, the interchangeability aspect with conventional rotary compressor is advantageous.

(3) design freedom is larger, it is possible to use in the rotary compressor of low output and height output, Reliability comparotive It is advantageous.

(4) problem that electric efficiency will not be produced to decline.

(5) simple structure, it is easy to manufacture.

In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature " on " or D score can be with It is the first and second feature directly contacts, or the first and second features are by intermediary mediate contact.And, fisrt feature exists Second feature " on ", " top " and " above " but fisrt feature are directly over second feature or oblique upper, or be merely representative of Fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " lower section " and " below " can be One feature is immediately below second feature or obliquely downward, or is merely representative of fisrt feature level height less than second feature.

In the description of this specification, reference term " one embodiment ", " some embodiments ", " example ", " specifically show The description of example " or " some examples " etc. means to combine specific features, structure, material or spy that the embodiment or example are described Point is contained at least one embodiment of the invention or example.In this manual, to the schematic representation of above-mentioned term not Identical embodiment or example must be directed to.And, the specific features of description, structure, material or feature can be with office Combined in an appropriate manner in one or more embodiments or example.Additionally, in the case of not conflicting, the skill of this area Art personnel can be tied the feature of the different embodiments or example described in this specification and different embodiments or example Close and combine.

Although embodiments of the invention have been shown and described above, it is to be understood that above-described embodiment is example Property, it is impossible to limitation of the present invention is interpreted as, one of ordinary skill in the art within the scope of the invention can be to above-mentioned Embodiment is changed, changes, replacing and modification.

Claims (11)

1. a kind of rotary compressor, it is characterised in that including：

Possesses the motor of stator and rotor；

Compression mechanism, the compression mechanism is included with the rotor rotational slide and with the inclined of the axle mesopore to its shaft part opening Heart axle, the compression mechanism are provided with compression chamber, and the compression chamber is built-in by the eccentric shaft-driven compression assembly；

Torsion-bar spring, the both sides motion end of the torsion-bar spring connects the rotor and the axle mesopore respectively；

In the action of the compression assembly, the difference of the anglec of rotation of the anglec of rotation of the eccentric shaft and the rotor is phase angle, institute State phase angle and have increase and decrease；

Limit the phase angle limiting part of the scope at the phase angle.

2. rotary compressor according to claim 1, it is characterised in that it is circle that the torsion-bar spring is formed as section Or non-circular linear torsion axle, the linear both sides motion end at least one party for turning round axle is cylinder or polygon.

3. rotary compressor according to claim 1, it is characterised in that possess in the rotor and the eccentric shaft The pipe of rotational slide.

4. rotary compressor according to claim 3, it is characterised in that the motion end of described torsion-bar spring one end and institute State pipe connection.

5. rotary compressor according to claim 1, it is characterised in that slided in the rotor and eccentric shaft rotation In dynamic sliding surface, possesses the circumferential groove in the gap for expanding the sliding surface.

6. the rotary compressor according to any one of claim 1-5, it is characterised in that the torsion-bar spring is constructed Can increased non-linear torsion-bar spring into the increase with its torsion angle, torsional moment rate or spring constant.

7. rotary compressor according to claim 3, it is characterised in that the phase angle limiter assembly includes being located at institute State in pipe and the eccentric shaft projection on either one.

8. rotary compressor according to claim 5, it is characterised in that possess to the axle mesopore and the circumferential groove The intercommunicating pore of middle perforate.

9. rotary compressor according to claim 1, it is characterised in that at least the one of the motion end of the torsion-bar spring Side is provided with the gas grooves that gas passes through.

10. rotary compressor according to claim 1, it is characterised in that in the scope of the axial length of the torsion-bar spring In, it is provided with for reducing the amplitude controlling component with the gap of the axle mesopore.

11. a kind of refrigerating circulatory devices, it is characterised in that including the rotary pressure according to any one of claim 1-10 Contracting machine.