CN202132234U - Double-slip-sheet type rotary compressor - Google Patents

Abstract

A double-slip-sheet type rotary compressor includes a motor assembly and a compression assembly which are arranged in the casing, wherein the compression assembly includes an air cylinder, an eccentric crank shaft, a main bearing and an auxiliary bearing which are used for supporting the eccentric crank shaft; a piston, a first slip sheet groove and a second slip sheet groove are arranged in the air cylinder; a first slip sheet and a slip sheet spring are arranged in the first slip sheet groove; a second slip sheet is arranged in the second slip sheet groove; the second slip sheet groove is communicated with a second slip sheet cavity; and the second slip sheet cavity is communicated with a pressure switch pipe. The exhaust starting angle is theta d in a low energy mode, and the exhaust completing angle is gamma in the low energy mode; when the piston rotates to any angle, the radial clearance between the piston and the air cylinder is delta, the radial clearance delta is arranged to be minimum at the beta angle, and the beta angle is the core adjusting angle. In the utility model, the radial clearance during the operation in the low energy model can be effectively controlled through limiting the beta, so that the radial leakage is reduced, and the volume efficiency of the compressor is improved.

Description

Two sliding vane type rotary compressors

Technical field

The utility model relates to a kind of rotary compressor, particularly a kind of pair of sliding vane type rotary compressor.

Background technique

In recent years, through the rotating speed of converter technique change rotary compressor, the method for the displacement variation of realization rotary compressor is more and more universal.But the method has increased the quantity of electronic component, has increased cost of production.Though the research of twin-tub variable capacity rotation compressor is in the develop rapidly,, the twin-tub variable capacity rotation compressor is compared with the single cylinder rotary compressor, has the many and high shortcoming of fabricating cost of number of components and parts.And, because the twin-tub variable capacity rotation compressor has increased by a cover compression assembly, make frictional loss increase.To this situation, the research of two slide plate rotary compressors is advancing.

In rotary compressor, when piston forwards to when arbitrarily angled, the radial clearance between piston and the cylinder is δ, and it is minimum value at the β angle that radial clearance δ is set, and then the β angle is called and transfers the core angle.According to traditional accent core angle design; Good operation in the time of can only guaranteeing the work of ability pattern, but this pair sliding vane type rotary compressor generally is in the capabilities mode of operation, exists radial clearance excessive so; Radial leakage increases, the problem of compressor volume inefficiency.

The model utility content

The purpose of the utility model aims to provide a kind of simple and reasonable, flexible operation, low, the radial leakage when reducing the capabilities pattern of fabricating cost; With two sliding vane type rotary compressors of the volumetric efficiency that improves this compressor, to overcome deficiency of the prior art.

A kind of pair of sliding vane type rotary compressor by this purpose design; Comprise the electric machine assembly and the compression assembly that are arranged in the housing, compression assembly comprises the main bearing and the supplementary bearing of cylinder, eccentric crankshaft, support eccentric crankshaft, is provided with piston, first vane slot and second vane slot in the cylinder; Be provided with first slide plate and sliding blade spring in first vane slot; Be provided with second slide plate in second vane slot, second vane slot communicates with the second slide plate chamber, and the second slide plate chamber is switched pipe with pressure and communicated; When the second slide plate chamber led to low pressure, compressor was the ability pattern, when the second slide plate chamber leads to high pressure; Compressor is the capabilities pattern, and the exhaust initial angle during the capabilities pattern is θ d, and it is γ that the exhaust during the capabilities pattern finishes the angle; Forward to when arbitrarily angled at piston, the radial clearance between piston and the cylinder is δ, and it is minimum value at the β angle that radial clearance δ is set; Then the β angle is called accent core angle, it is characterized in that β satisfies following relation:

$-\frac{\mathrm{\&pi;}}{18}<\mathrm{\&beta;}-\frac{9}{28}\mathrm{\&gamma;}-\frac{19}{28}\mathrm{\&theta;d}<\frac{\mathrm{\&pi;}}{18}.$

Traditional accent core angle design all is to be directed against the ability pattern, and according to traditional accent core angle, the radial leakage during the capabilities pattern is relatively large, causes compressor volume decrease in efficiency.And under the actual conditions, two sliding vane type rotary compressors generally are in the capabilities mode state.In order to guarantee the compressor performance under the capabilities pattern, must corresponding adjustment transfer the core angle, the utility model is through limiting β, and the radial clearance in the time of can controlling the work of capabilities pattern effectively reduces radial leakage, improves compressor volume efficient.

The utlity model has simple and reasonable, flexible operation, low, the radial leakage when reducing the capabilities pattern of fabricating cost, with the characteristics of the volumetric efficiency that improves this compressor.

Description of drawings

Fig. 1 is the utility model one embodiment's a broken section structural representation.

Fig. 2 is the structural representation of the utility model when the ability pattern.

Fig. 3 is the structural representation of the utility model when the capabilities pattern.

Fig. 4 is the accent core angle design schematic representation of the utility model when the capabilities pattern.

Among the figure: 10 is housing, and 11 is cylinder, and 12 is piston, and 13.1 is first slide plate, and 13.2 is second slide plate; 13.5 be the first withdrawing hole, 13.6 is the second withdrawing hole, 13.7 is the first exhaust otch, and 13.8 is the second exhaust otch, and 13.9 is sliding blade spring; 14 is supplementary bearing, and 15 is main bearing, and 16 is eccentric crankshaft, and 17 is rotor, and 18 is stator; 19 for pressure switches pipe, and 20 is suction port, and 81 is air aspiration cavity, and 82 is compression chamber, and 83 is intermediate cavity; 84 is the first slide plate chamber, and 85 is the second slide plate chamber, the exhaust initial angle when θ d is the capabilities pattern, and the exhaust when γ is the capabilities pattern finishes the angle, and β is for transferring the core angle.

Embodiment

Below in conjunction with accompanying drawing and embodiment the utility model is further described.

Referring to Fig. 1-Fig. 4, this pair sliding vane type rotary compressor comprises the electric machine assembly and the compression assembly that are arranged in the housing 10, and electric machine assembly comprises stator 18 and rotor 17, and stator 18 is fixed on the inwall of housing 10, and rotor 17 is fixed on the eccentric crankshaft 16.Compression assembly comprises cylinder 11, eccentric crankshaft 16, is used to support the main bearing 15 of eccentric crankshaft 16 and the both sides that supplementary bearing 14 is arranged on cylinder 11, is provided with piston 12, first vane slot and second vane slot in the cylinder 11.The rear portion that the rear portion of first vane slot is provided with the first withdrawing hole, 13.5, the second vane slots 13.4 is provided with the second withdrawing hole 13.6.The first withdrawing hole 13.5 surrounds 84, the second withdrawing holes 13.6, the first slide plate chamber jointly with main bearing 15 and supplementary bearing 14 and surrounds the second slide plate chamber 85 jointly with main bearing 15 and supplementary bearing 14.Be provided with in first vane slot in first slide plate 13.1 and pressure spring 13.9, the second vane slots and be provided with second slide plate 13.2.Second vane slot 13.4 communicates with the second slide plate chamber 85, and the second slide plate chamber 85 is switched pipe 19 with pressure and communicated.Through switching the second slide plate chamber, 85 pressure, realize transfiguration.

When pressure switching pipe 19 led to low pressure Ps, as shown in Figure 2, the pressure in the second slide plate chamber 85 was low pressure Ps, and second slide plate 13.2 is accommodated in second vane slot under the suction-operated of gas differential pressure power fully.The first slide plate chamber, 84 pressure are high pressure P d always, and the periphery of the tip of first slide plate 13.1 and piston 12 is joined, and first slide plate 13.1 is reciprocating in first vane slot.Therefore, cylinder 11, piston 12 and first slide plate 13.1 have been divided into air aspiration cavity 81 and compression chamber 82 totally two chambers to the active chamber of cylinder 11.Eccentric crankshaft 16 drives piston 12 and rotates, and is compressed into the pressurized gas that pressure is Pd to the low-pressure gas that is drawn into air aspiration cavity 81 from suction port 20, and pressurized gas are discharged from the first exhaust otch 13.7.This working procedure is the ability pattern.

When pressure switching pipe (19) leads to high pressure P d; As shown in Figure 3; The pressure in the second slide plate chamber 85 is high pressure P d; And the pressure in the first slide plate chamber 84 is high pressure P d always, and the tip of first slide plate 13.1 and second slide plate 13.2 joins with the periphery of piston 12 respectively under the effect of gas differential pressure power, and first slide plate 13.1 and second slide plate 13.2 are reciprocating in first vane slot, second vane slot respectively.Therefore, cylinder 11, piston 12, first slide plate 13.1 and second slide plate 13.2 have been divided into air aspiration cavity 81, compression chamber 82 and intermediate cavity 83 totally three chambers to the active chamber of cylinder 11.Eccentric crankshaft 16 drives pistons 12 and rotates, the low-pressure gas that is drawn into air aspiration cavity 81 from suction port 20 be compressed into pressure be Pd pressurized gas, and with pressurized gas from 13.8 discharges of the second exhaust otch.This working procedure is the capabilities pattern.

As shown in Figure 2, represent the residing position of piston with the line of centers 001 of cylinder and piston.001 when overlapping with the center line 0A of first vane slot, as corner starting point θ=0.Piston rotates by the illustrated direction of arrow, counterclockwise, turns over suction port, begins compression.

When the pressure in the cylinder compression chamber was enough to make outlet valve to be opened, compression finished, the beginning exhaust, this moment rotational angle theta=θ d, and θ d is called the exhaust initial angle.Under the state of exhaust valve opening, along with piston motion, the volume of cylinder compression chamber constantly dwindles, and pressurized gas is discharged from the exhaust otch.

When the cylinder compression chamber is communicated with through another cylinder compression chamber chamber that exhaust otch and its are in breathing process at the back; Pressurized gas in it are the expansion moment completion of a cylinder compression chamber backward; Exhaust finishes, this moment rotational angle theta=γ, and γ is called exhaust and finishes the angle.

Piston rotates by the illustrated direction of arrow, counterclockwise, rotates back into the center line 0A of first vane slot again, is regarded as turning over a circle 2 π angles.

Fig. 4 is the accent core angle design schematic representation under the capabilities mode state, and pressure switches pipe 19 logical low pressure Pd, and the exhaust initial angle of this pattern is θ d, and it is γ that exhaust finishes the angle, i.e. the rear edge angle γ of the second exhaust otch.When piston 12 forwards to when arbitrarily angled, the radial clearance between piston 12 and the cylinder 11 is δ, and it is minimum value at the β angle that radial clearance δ is set, and then the β angle is called and transfers the core angle.All angles are benchmark with the center line of first vane slot 13.3 all, measure along piston 12 sense of rotation.β satisfies following relation:

$-\frac{\mathrm{\&pi;}}{18}<\mathrm{\&beta;}-\frac{9}{28}\mathrm{\&gamma;}-\frac{19}{28}\mathrm{\&theta;d}<\frac{\mathrm{\&pi;}}{18}.$

The utility model is owing to having adopted above-mentioned design proposal, so when the capabilities pattern was worked, radial leakage was little, has improved the volumetric efficiency of two sliding vane type rotary compressors.

Claims (1)

1. two sliding vane type rotary compressor; Comprise the electric machine assembly and the compression assembly that are arranged in the housing (10); Compression assembly comprises cylinder (11), eccentric crankshaft (16), supports the main bearing (15) and the supplementary bearing (14) of eccentric crankshaft (16); Be provided with piston (12), first vane slot and second vane slot in the cylinder (11), be provided with first slide plate (13.1) and sliding blade spring (13.9) in first vane slot, be provided with second slide plate (13.2) in second vane slot; Second vane slot communicates with the second slide plate chamber (85), and the second slide plate chamber (85) is switched pipe (19) with pressure and communicated; When the second slide plate chamber (85) led to low pressure, compressor was the ability pattern, when the second slide plate chamber (85) leads to high pressure; Compressor is the capabilities pattern, and the exhaust initial angle during the capabilities pattern is θ d, and it is γ that the exhaust during the capabilities pattern finishes the angle; Forward to when arbitrarily angled at piston (12), the radial clearance between piston (12) and the cylinder (11) is δ, and it is minimum value at the β angle that radial clearance δ is set; Then the β angle is called accent core angle, it is characterized in that β satisfies following relation:

$-\frac{\mathrm{\&pi;}}{18}<\mathrm{\&beta;}-\frac{9}{28}\mathrm{\&gamma;}-\frac{19}{28}\mathrm{\&theta;d}<\frac{\mathrm{\&pi;}}{18}.$

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