CN105570132A - Compressor - Google Patents

Abstract

The invention discloses a compressor. The compressor comprises a crankshaft, a piston, a cylinder and a slide sheet, wherein an eccentric part is arranged on the crankshaft; the piston coats the eccentric part; a compression cavity and a slide sheet groove communicated with the compression cavity are formed in the cylinder; the piston is arranged in the compression cavity; the slide sheet is movably arranged in the slide sheet groove, and is normally contacted with the piston; the eccentricity of the piston is e; the height of the cylinder is H; and e and H satisfies the following formula: e not more than 0.65H and not less than 0.05H. As the compressor enables the relation between the eccentricity e of the piston and the height H of the cylinder to satisfy the formula of e not more than 0.65H and not less than 0.05H, the design of the compressor can be optimized, the surface heat dissipation area is reduced as far as possible, and the working efficiency of the compressor can be promoted.

Description

Compressor

Technical field

The present invention relates to technical field of refrigeration equipment, especially relate to a kind of compressor.

Background technique

In correlation technique, when the compression chamber of compressor generally optimizes, consider that the size of clearance volume and air-breathing heat and pulsation loss.That is because the refrigerating capacity loss of conventional refrigerant R22 and R410a is mainly derived from this two aspects, accounts for about 60% of overall refrigerating effect loss.Especially the density under R22 and R410a standard condition is 2 times and 3 times of R290, and under identical refrigerating capacity, demand discharge capacity is less.Therefore, have in correlation technique when the compression chamber of R410a is optimized and select the pump housing that cylinder is high and cylinder diameter is little all as far as possible.But, R290 is different, R290 density is little, air-breathing backflow and air-breathing heat account for that overall refrigerating effect loses 3%, and demand discharge capacity is respectively 1.18 times of R22 under identical refrigerating capacity, 1.6 times of R410a, simultaneously, existing refrigerant substitute technology is pointed out, because R290 and R22 has substantially identical pressure and temperature under identical work operating mode, then do not need to carry out particular design and changes in material to existing R22 Machinery Ministry, therefore the R22 pump housing directly being increased cylinder height lifting discharge capacity is general way, or the platform being amplified to larger series goes to realize.But just the physical property of R290 itself and thermodynamic property have larger difference with R22, but lack and do not have correlation technique to point out to go specific aim optimal design to R290 refrigerant feature.

From thermodynamics analysis, the entropy of R290 is higher than R22, this means, the latent heat of vaporization of R290 is large, and in fact the R290 latent heat of vaporization is 1.8 times of R22, is 2.3 times of R410a.Therefore, in compression process because the heat radiation of pressure channel causes useless compression work to increase.That is, in order to increase the discharge capacity of R290, compression chamber volume will certainly increase, and while increase volume, the cooling surface area of compression chamber can increase simultaneously, and the loss brought in order to avoid cooling surface area increase, we wish that cooling surface area is the smaller the better.

Summary of the invention

The present invention is intended to solve one of technical problem in correlation technique at least to a certain extent.For this reason, the present invention proposes a kind of compressor, and described compressor has the high advantage of working efficiency.

According to the compressor of the embodiment of the present invention, comprising: bent axle, described bent axle is provided with eccentric part; Piston, described piston sleeve is located on described eccentric part; Cylinder, the vane slot that there is in described cylinder compression chamber and be communicated with described compression chamber, described piston is located in described compression chamber; And slide plate, described slide plate is located in described vane slot movably and described slide plate often contacts with described piston, and wherein, described piston offset is e, and described cylinder height is H, and described e and described H is satisfied: 0.05H≤e≤0.65H.

According to the compressor of the embodiment of the present invention, 0.05H≤e≤0.65H is met by making the relation of piston eccentric amount e and cylinder height H, the design of compressor can be optimized thus, surface radiating surface area is reduced as far as possible, thus the working efficiency of compressor can be promoted.

According to some embodiments of the present invention, described piston offset is e, and described cylinder height is H, and described e and described H meets: 0.1H≤e≤0.5H.

According to some embodiments of the present invention, described piston offset is e, and described cylinder height is H, and described e and described H meets: 0.1H≤e≤0.45H.

According to some embodiments of the present invention, described piston offset is e, and described cylinder height is H, and described e and described H meets: 0.1H≤e≤0.4H.

According to some embodiments of the present invention, described piston offset is e, and described cylinder height is H, and described e and described H meets: 0.15H≤e≤0.4H.

According to some embodiments of the present invention, described piston offset is e, and described cylinder height is H, and described e and described H meets: 0.15H≤e≤0.35H.

Accompanying drawing explanation

Fig. 1 is the partial structurtes schematic diagram of the compressor according to the embodiment of the present invention;

Fig. 2 is the partial structurtes schematic diagram of the compressor according to the embodiment of the present invention;

Fig. 3 is the cross-sectional schematic in A-A direction in Fig. 2;

Fig. 4 is the schematic cross-section at the maximum cross-section place of the pressure channel of compressor according to the embodiment of the present invention;

Fig. 5 is refrigerant R290 and R22 density correlation curve figure;

Fig. 6 is refrigerant R290 and R22 entropy correlation curve figure;

Fig. 7 is λ and the COP graph of relation of the compressor according to the embodiment of the present invention.

Reference character:

Compressor 100,

Bent axle 110, eccentric part 111,

Piston 120,

Cylinder 130, compression chamber 131, vane slot 132, pressure channel 133,

Slide plate 140,

Upper bearing (metal) 150, lower bearing 160,

Plug offset is e, and cylinder height is H,

Embodiment

Be described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the present invention, and can not limitation of the present invention be interpreted as.

The compressor 100 according to the embodiment of the present invention is described in detail referring to Fig. 1-Fig. 7.It should be noted that, the compressor 100 of the embodiment of the present invention can be a kind of rotary compressor for new environmental protection R290 refrigerant.

As shown in Fig. 1-Fig. 7, according to the compressor 100 of the embodiment of the present invention, comprise bent axle 110, piston 120, cylinder 130, upper bearing (metal) 150, lower bearing 160 and slide plate 140.

Specifically, upper bearing (metal) 150 is located on the upper-end surface of cylinder 130, lower bearing 160 is located on the lower end surface of cylinder 130, there is in cylinder 130 compression chamber 131, upper-end surface, the upper bearing (metal) 150 of compression chamber 131 and cylinder 130 form the upper meniscus level sealed, lower end surface, the lower bearing 160 of compression chamber 131 and cylinder 130 form facing next month sealed, and bent axle 110 runs through upper bearing (metal) 150, cylinder 130 and lower bearing 160 successively.Bent axle 110 has eccentric part 111, and eccentric part 111 is positioned at compression chamber 131, eccentric part 111 is arranged with piston 120.Cylinder 130 has the vane slot 132 be communicated with compression chamber 131, and slide plate 140 is located in vane slot 132 movably and slide plate 140 often contacts with piston 120.

According to the dimensional chain relation of compressor 100, as shown in Figure 2, the area (dash area) that the volume V of compression chamber 131 equals crescent moon part is multiplied by cylinder 130 cylinder height H, is also the volume that the volume of cylinder 130 deducts shared by piston 120, the relation of V can be obtained, as follows:

$V=H*\[\mathrm{\π}{\left(\frac{D}{2}\right)}^2-\mathrm{\π}{\left(\frac{d}{2}\right)}^2\]---\left(1\right)$

d＝D-2e(2)

Wherein, D is compression chamber 131 diameter, and d is piston 120 diameter.

Relation V=π He (D-e) can be derived by formula (1) and (2).

Determine at V, when D is certain, need the parameter of optimal design to be then H and e.

To ensure this structure feasibility, key is control piston 120 eccentric amount e and cylinder 130 height H, introduces optimization control parameter lambda, namely for this reason

e＝λH(3)

As shown in Figure 3, cooling surface area comprise be made up of upper bearing (metal) 150, lower bearing 160 last month tooth surface and lower crescent surface, if pressure channel 133 is carried out differential, and the sectional shape at the maximum cross-section place of pressure channel 133 determines the basic shape of passage, if therefore wish, surface radiating reduces, then need the cross section of pressure channel 133 (S) and girth (L) little as far as possible, and the sectional area (S) of increase pressure channel 133 large as far as possible under making same discharge capacity (V), makes refrigerant circulation length reduce as far as possible.Wherein:

S＝2e*H(4)

L＝4e+2H(5)

Here it should be noted that, in order to improve the performance of compressor 100, needing that S is the bigger the better, L is the smaller the better.

Want to get Smax value (i.e. the maximum value of S) and Lmin (i.e. the minimum value of L) value simultaneously.Then need to introduce function:

$f=\frac{L}{S}=\frac{4e+2H}{2eH}=\frac{2}{H}+\frac{1}{e}---\left(6\right)$

To get f minimum value, and H and e structurally can not obtain maximum value simultaneously, therefore certain relation that there is best H and e.Thus, e=λ H can be supposed.

From formula (6), H and e need to exhaust simultaneously may large value could to meet f minimum.And in compressor 100 project organization, once after discharge capacity and cylinder bore determine, H and e is inversely proportional to, and it is impossible that general H and e gets maximum value simultaneously.In order to solve this contradiction, the best relation value of H and e must be found, thus the lambda parameter that publicity (3) is introduced, determine to have optimum range value.

Bring a series of λ value by experiment into, fitting compaction machine 100 efficiency curve, as shown in Figure 7, when 0.05≤λ≤0.65, there is obvious flex point in the COP of compressor.

Therefore in R290 cold medium compressor 100 designs, piston 120 eccentric amount e and cylinder 130 height H demand fulfillment following formula relation: 0.05≤λ≤0.65, i.e. 0.05H≤e≤0.65H, can make in its refrigerant flow process and surface radiating surface area reduces as far as possible, to promote compressor 100 efficiency.

According to the compressor 100 of the embodiment of the present invention, 0.05H≤e≤0.65H is met by making the relation of piston 120 eccentric amount e and cylinder 130 height H, the design of compressor 100 can be optimized thus, surface radiating surface area is reduced as far as possible, thus the working efficiency of compressor 100 can be promoted.

In compressor 100 technical field, the modular construction related in the process of optimization of compressor 100 is numerous and structural parameter complicated, when not carrying out great many of experiments, the feasibility of unpredictable technological scheme, also cannot expect the technique effect of technological scheme.The selection of technical parameter is most important, and the minor alteration of any parameter all may bring diverse technique effect, and optimized technical parameter is all need could be determined by a large amount of exploitative experiments, and cannot by simply predicting acquisition.

Particularly, from thermodynamics analysis, as shown in Figure 6, the entropy of R290 is higher than R22, this means, the latent heat of vaporization of R290 is large, and in fact the R290 latent heat of vaporization is 1.8 times of R22, is 2.3 times of R410a.Therefore, in compression process because the heat radiation of pressure channel 133 causes useless compression work to increase.That is, in order to increase the discharge capacity of R290, compression chamber 131 volume will certainly increase, while increase volume, the cooling surface area of compression chamber 131 can increase simultaneously, and the loss brought in order to avoid cooling surface area increase, we wish that cooling surface area is the smaller the better.For solving above-mentioned technical contradiction, once taked in relevant technologies to adopt structure or the materials such as heat insulation, insulation to forming the parts avoided of compression chamber 131.And the present invention to be intended to compression chamber 131 basic structure directly to optimize volume and to increase and reduce surface contact as far as possible, meet the condition of the optimum optimization that compressor 100 designs.

Provide a kind of for new environmental protection R290 cold medium compressor 100 according to some embodiments of the present invention, the compressor 100 of the embodiment of the present invention can for R290 compressor 100 provides optimal compression passage 133 and best pump body structure on existing pump housing platform.This compressor 100 comprises: the lower end surface of the upper meniscus level of the sealing that the compression chamber 131 formed by cylinder 130, upper bearing (metal) 150, lower bearing 160 and compression chamber 131 are formed with upper-end surface and the upper bearing (metal) 150 of cylinder 130, compression chamber 131 and cylinder 130 and lower bearing 160 form facing next month of sealing, described compression chamber 131 inside placed to exist eccentric rotary-piston 120 with cylinder 130 center, and is used for the slide plate 140 that can carry out translation at vane slot 132 in separately high low pressure chamber.

Cylinder 130 comprises vane slot 132, intakeport, exhaust angular cut, upper bearing (metal) 150 and lower bearing 160 are provided with the relief opening be communicated with the hyperbaric chamber of described compression chamber 131 respectively or simultaneously, relief opening is provided with the valve block of movement vertical with discharge directions, and restricted valve block moves the baffle plate of height, described baffle plate, valve block are positioned at the groove that metal (upper 160 is offered.Described compression chamber 131 may be used for the compression of R290 refrigerant.Described R290 refrigerant molecular weight compared with in the physical property of existing conventional R22 refrigerant is half as large, gas density little (as shown in Figure 5, Fig. 5 is the density relationship figure of R290 refrigerant and R22 refrigerant).In thermodynamic property, R290 and R22 compares, R290 entropy higher (as shown in Figure 6), and lower with refrigerant mass flow rate under discharge capacity, and therefore affecting loss by heat radiation can be larger.Meanwhile, more with the volume needs of R22 cold medium compressor 100 under ability, if the pump body compression room designed according to existing R22 refrigerant technical pattern, then in refrigerant flow channel, surface area heat dissipating capacity is large, analyzes from thermomechanics, and during its flowing, radiation loss becomes large.

By utilizing a series of λ value, after a large amount of experiments, can simulate compressor 100 efficiency curve as shown in Figure 7, in this efficiency curve, there is obvious flex point in COP in a series of λ value.Pass through again a large amount of experiment repeatedly, when 0.1≤λ≤0.5, i.e. during 0.1H≤e≤0.5H, the flex point of the COP of compressor 100 is positioned at this scope.Thus, the design of compressor 100 can be optimized further, promote the performance of compressor 100.

By a large amount of experiments repeatedly, progressively can reduce the span of λ, be positioned at this scope with the flex point of the COP by compressor 100.Such as, when 0.1≤λ≤0.45, i.e. during 0.1H≤e≤0.45H, the flex point of the COP of compressor 100 is positioned at this scope.For another example, when 0.1≤λ≤0.4, i.e. during 0.1H≤e≤0.4H, the flex point of the COP of compressor 100 is positioned at this scope.And for example, when 0.15≤λ≤0.4, i.e. during 0.15H≤e≤0.4H, the flex point of the COP of compressor 100 is positioned at this scope.And for example, when 0.15≤λ≤0.35, i.e. during 0.15H≤e≤0.35H, the flex point of the COP of compressor 100 is positioned at this scope.

According to the compressor 100 of the embodiment of the present invention, 0.05H≤e≤0.65H is met by making the relation of piston 120 eccentric amount e and cylinder 130 height H, the design of compressor 100 can be optimized thus, surface radiating surface area is reduced as far as possible, thus the working efficiency of compressor 100 can be promoted.

In describing the invention, it will be appreciated that, term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end " " interior ", " outward ", " clockwise ", " counterclockwise ", " axis ", " radial direction ", orientation or the position relationship of the instruction such as " circumference " are based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore limitation of the present invention can not be interpreted as.

In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristics.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise at least one this feature.In describing the invention, the implication of " multiple " is at least two, such as two, three etc., unless otherwise expressly limited specifically.

In the present invention, unless otherwise clearly defined and limited, the term such as term " installation ", " being connected ", " connection ", " fixing " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or integral; Can be mechanical connection, also can be electrical connection or each other can communication; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals or the interaction relationship of two elements, unless otherwise clear and definite restriction.For the ordinary skill in the art, above-mentioned term concrete meaning in the present invention can be understood as the case may be.

In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature " on " or D score can be that the first and second features directly contact, or the first and second features are by intermediary mediate contact.And, fisrt feature second feature " on ", " top " and " above " but fisrt feature directly over second feature or oblique upper, or only represent that fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " below " and " below " can be fisrt feature immediately below second feature or tiltedly below, or only represent that fisrt feature level height is less than second feature.

In the description of this specification, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present invention or example.In this manual, to the schematic representation of above-mentioned term not must for be identical embodiment or example.And the specific features of description, structure, material or feature can combine in one or more embodiment in office or example in an appropriate manner.In addition, when not conflicting, the feature of the different embodiment described in this specification or example and different embodiment or example can carry out combining and combining by those skilled in the art.

Although illustrate and describe embodiments of the invention above, be understandable that, above-described embodiment is exemplary, can not be interpreted as limitation of the present invention, and those of ordinary skill in the art can change above-described embodiment within the scope of the invention, revises, replace and modification.

Claims (6)

1. a compressor, is characterized in that, comprising:

Bent axle, described bent axle is provided with eccentric part;

Piston, described piston sleeve is located on described eccentric part;

Cylinder, the vane slot that there is in described cylinder compression chamber and be communicated with described compression chamber, described piston is located in described compression chamber; And

Slide plate, described slide plate is located in described vane slot movably and described slide plate often contacts with described piston,

Wherein, described piston offset is e, and described cylinder height is H, and described e and described H meets: 0.05H≤e≤0.65H.

2. compressor according to claim 1, is characterized in that, described piston offset is e, and described cylinder height is H, and described e and described H meets: 0.1H≤e≤0.5H.

3. compressor according to claim 1, is characterized in that, described piston offset is e, and described cylinder height is H, and described e and described H meets: 0.1H≤e≤0.45H.

4. compressor according to claim 1, is characterized in that, described piston offset is e, and described cylinder height is H, and described e and described H meets: 0.1H≤e≤0.4H.

5. compressor according to claim 1, is characterized in that, described piston offset is e, and described cylinder height is H, and described e and described H meets: 0.15H≤e≤0.4H.

6. compressor according to claim 1, is characterized in that, described piston offset is e, and described cylinder height is H, and described e and described H meets: 0.15H≤e≤0.35H.