CN202209278U - Rotary supporting lubrication structure for rotary compressor - Google Patents

Abstract

The utility model provides a rotary supporting lubrication structure for a rotary compressor. The rotary supporting lubrication structure comprises a crank, an oil path extending along the axial direction of the crank is arranged in the crank, the crank comprises a first crank section, a second crank section and an eccentric crank section, a first bearing and a second bearing are respectively arranged on the upper end surface and the lower end surface of an air cylinder of the rotary compressor; the first bearing and the second bearing are used for supporting the first crank section and the second crank section respectively; the eccentric crank section is positioned in the air cylinder; a ring-shaped oil cavity is arranged between a first ring-shaped contact part and a second ring-shaped contact part; and a first end of the first crank section is contacted with the air cylinder. According to the rotary supporting lubrication structure, the ring-shaped oil cavity arranged in the first bearing is used for dividing a contact part between the first bearing and the crank into the first contact part and the second contact part, so that lubrication oil can be used for lubricating the first contact part and the second contact part through the ring-shaped oil cavity, and finally better lubrication effect is achieved.

Description

Lubricating structure is supported in the revolution of rotary compressor

Technical field

The utility model relates to the rotary compressor field, and more specifically, lubricating structure is supported in the revolution that relates to a kind of rotary compressor.

Background technique

Fig. 1 shows the schematic representation of the revolution support lubricating structure of rotary compressor of the prior art.As shown in Figure 1, this revolution is supported lubricating structure and is comprised bent axle, and this bent axle is supported on first radial sliding bearing 1 and second radial sliding bearing 2, to guarantee that under the driving of motor this bent axle can reliablely and stablely be realized the refrigeration agent compression.Wherein, the end face of the lower end of the eccentric segment of this bent axle and this second radial sliding bearing 2 is inconsistent, so the end face of second radial sliding bearing 2 forms thrust surface 3, moves on it is axial to prevent bent axle.

Fig. 2 shows the schematic representation of the revolution support lubricating structure of rolling rotor type compressor.As shown in Figure 2; This revolution is supported lubricating structure and is used for the revolution support system of rolling rotor type compressor is lubricated; Wherein, this revolution support system comprises bent axle, and bent axle comprises first shaft part 4 and second shaft part 5; First shaft part 4 and second shaft part 5 are supported on respectively on first radial sliding bearing 1 and second radial sliding bearing 2; Be provided with eccentric shaft part 6 between first shaft part 4 and second shaft part 5, eccentric shaft part 6 is arranged in the cylinder 7 of rolling rotor type compressor, and first radial sliding bearing 1 and second radial sliding bearing 2 are separately positioned on the both sides of cylinder 7.Be provided with oil duct 8 in the bent axle; Transition position at first shaft part 1 and eccentric shaft part 6 is provided with first oil pocket 9; Transition position at the eccentric shaft part 6 and second shaft part 2 is provided with second oil pocket 11; Be provided with first oilhole 10 in the zone corresponding to first oil pocket 9 of bent axle, be provided with second oilhole 12 in the zone corresponding to second oil pocket 11 of bent axle.The working procedure that lubricating structure is supported in this revolution is following: be inhaled in the oil duct 8 in the oil sump of lubricant oil by the bottom of shell of rolling rotor type compressor; And it is upwards mobile along oil duct 8; When flow of lubricant when first oilhole 10, flow out and be pooled in first oil pocket 9 by first oilhole 10.The pump-absorb action of a part that is pooled to the lubricant oil in first oil pocket 9 through being arranged on the spiral helicine oil groove (not shown) on first shaft part 1 is to first radial sliding bearing, 1 fuel feeding; So that first radial sliding bearing 1 is lubricated; The lubricant oil that flow to the bent axle upper end is after flow guide structure overflows; The rotor that is used for cooling motor falls under gravity in the bottom of shell oil sump at last.The another part that is pooled to the lubricant oil in first oil pocket 9 leaks into downwards in the cylinder 7, and further is downward through eccentric shaft part 6, and is last so that eccentric shaft part 6 is lubricated, and is pooled in second oil pocket 11.Simultaneously, the lubricant oil that is flowed out by second oilhole 12 also is pooled in second oil pocket 11, and the part of the lubricant oil in second oil pocket 11 is lubricated second annular bearing with rolling contact under the spiral fluted pump-absorb action on second shaft part; Owing to have the gap between the end face of eccentric shaft part and first, second radial sliding bearing; Therefore, another part oil leak is used for eccentric shaft part and cylinder are lubricated in cylinder; And be compressed to exhaust with refrigerant gas; Further in gravity and motor driving and under the action of centrifugal force that causes, lubricant oil separates with exhaust, thereby falls into the oil sump of bottom of shell.Yet the wide footpath of first radial sliding bearing of rotary compressor of the prior art is bigger, and therefore, this first radial sliding bearing can not get lubricated preferably; In addition, the wearing and tearing of second radial sliding bearing are also than the serious wear of first sliding bearing.Further; End face of second radial sliding bearing constitutes stop surface 3, an end of eccentric shaft part 6 and 3 conflicts of this stop surface, thus constitute an axial thrust structure; Fig. 3 shows the sectional view of the block face of this thrust structure in the existing technology; The thrust surface of this thrust structure of the prior art can not make this thrust structure form effective dynamic lubrication, and friction power loss is big, the problem of serious wear thereby have, and has influenced the efficiency of rotary compressor.

The model utility content

The utility model aims to provide a kind of revolution of rotary compressor and supports lubricating structure, with the clutch shaft bearing of the rotary compressor that solves existing technology because width-diameter ratio can not get the problem of better lubricating greatly.

For solving the problems of the technologies described above; An aspect according to the utility model; Provide a kind of revolution of rotary compressor to support lubricating structure; Comprise: bent axle, be provided with axially extended oil duct in the bent axle along bent axle, bent axle comprise first shaft part, second shaft part and be arranged on first shaft part and second shaft part between eccentric shaft part; On the upper-end surface of the cylinder of rotary compressor and lower end surface, be respectively arranged with the clutch shaft bearing and second bearing, the clutch shaft bearing and second bearing support first shaft part and second shaft part respectively, and the eccentric shaft section is positioned at cylinder; Clutch shaft bearing comprises axis hole; First shaft part is located in the axis hole; Between first shaft part and axis hole, contact slidably each other with the second annular contacting part through the first annular contacting part; Clutch shaft bearing comprises first end and second end, and the first annular contact position is in a side of first end, and the second annular contact position is in a side of second end; Between the first annular contacting part and the second annular contacting part, be provided with annular oil cavity; First end of clutch shaft bearing contacts with cylinder.

Further, the position corresponding to annular oil cavity of bent axle is provided with first oilhole, and annular oil cavity is communicated with through first oilhole with oil duct.

Further, the inwall of the axis hole of clutch shaft bearing is provided with oil groove, oil groove on first end of clutch shaft bearing and the sidewall between second end relatively the axioversion of axis hole extend, and this sidewall is provided with through hole, oil groove is communicated with through hole.

Further, through hole is arranged on the end of oil groove.

Further, the end portion, supports of second shaft part of bent axle is on the end face of second bearing.

Further, second bearing with second shaft part in the corresponding zone of oil duct in be provided with through hole.

Further, the perisporium of second shaft part is provided with second oilhole, and second oilhole is communicated with the interior oil duct of bent axle.

Further, be provided with the 3rd oilhole at first shaft part of bent axle and the intermediate location of eccentric shaft part, the 3rd oilhole is communicated with oil duct.

Further, annular oil cavity is a groove, and groove is arranged on the inwall of clutch shaft bearing or is arranged on the outer surface of first shaft part.

The utility model is divided into first contacting part and second contacting part through the annular oil cavity that in clutch shaft bearing, is provided with the contact segment between clutch shaft bearing and the bent axle; So that lubricant oil can be lubricated first contacting part and second contacting part through this annular oil cavity, reached better lubrication effect.

Description of drawings

The accompanying drawing that constitutes the application's a part is used to provide the further understanding to the utility model, and illustrative examples of the utility model and explanation thereof are used to explain the utility model, do not constitute the improper qualification to the utility model.In the accompanying drawings:

Fig. 1 has schematically shown the revolution of rotary compressor of the prior art and has supported the lubricating structure schematic representation;

Fig. 2 has schematically shown the revolution of rolling rotor type compressor of the prior art and has supported the lubricating structure schematic representation;

Fig. 3 has schematically shown the structural representation of thrust surface of the prior art;

Fig. 4 has schematically shown the revolution of the rotary compressor among the embodiment in the utility model and has supported the lubricating structure schematic representation;

Fig. 5 has schematically shown the sectional view of the clutch shaft bearing in the utility model;

Fig. 6 has schematically shown the revolution of the rotary compressor among another embodiment in the utility model and has supported the lubricating structure schematic representation;

Fig. 7 has schematically shown the structural representation of the thrust surface among Fig. 6;

Fig. 8 has schematically shown the structural representation the when bent axle among Fig. 6 is in heeling condition;

Fig. 9 has schematically shown the variation relation figure of friction power loss loss with bearing length; And

Figure 10 has schematically shown friction power loss loss among the embodiment with the variation relation figure of bearing length.

Embodiment

Embodiment to the utility model is elaborated below in conjunction with accompanying drawing, but the multitude of different ways that the utility model can be defined by the claims and cover is implemented.

As an embodiment of the utility model, the utility model provides a kind of revolution of rotary compressor to support lubricating structure.Said revolution as shown in Figure 4 is supported lubricating structure and is comprised bent axle, is provided with the axially extended oil duct 8 along bent axle in the bent axle, bent axle comprise first shaft part 4, second shaft part 5 and be arranged on first shaft part 4 and second shaft part 5 between eccentric shaft part 6; On the upper-end surface of the cylinder (not shown) of rotary compressor and lower end surface, be respectively arranged with the clutch shaft bearing 1 and second bearing 2, the clutch shaft bearing and second bearing support first shaft part 4 and second shaft part 5 respectively, and eccentric shaft part 6 is positioned at cylinder; Clutch shaft bearing 1 comprises axis hole; First shaft part 4 is located in the axis hole; Between first shaft part 4 and axis hole, contact slidably each other with the second annular contacting part 13 through the first annular contacting part 12; Clutch shaft bearing 1 comprises first end and second end, and the first annular contacting part 12 is positioned at a side of first end, and the second annular contacting part 13 is positioned at a side of second end; Between the first annular contacting part 12 and the second annular contacting part 13, be provided with annular oil cavity 7; First end of clutch shaft bearing 1 contacts with cylinder.Preferably, the position corresponding to annular oil cavity 7 of bent axle is formed with first oilhole 9, and annular oil cavity 7 is communicated with through first oilhole 9 with oil duct 8.Preferably, annular oil cavity 7 is grooves, and this groove is arranged on the inwall of clutch shaft bearing 1 or is arranged on the outer surface of first shaft part 4.In the present embodiment, second bearing 2 has stop surface 3, and an end of eccentric shaft part 6 contacts with stop surface 3 slidably, thereby bent axle is also supported in its axial stop.Owing to be provided with annular oil cavity 7; Thereby make the contact area between clutch shaft bearing 1 and the bent axle be separated into the first annular contacting part and the second annular contacting part; Make clutch shaft bearing in fact play the effect of two bearings (corresponding respectively to the first annular contacting part and the second annular contacting part); Further, lubricant oil can arrive first oilhole, 9 places through oil channel 8, and gets in the annular oil cavity 7 through first oilhole 9; Thereby improved the fuel delivery of clutch shaft bearing; Be respectively the first annular contacting part and the second annular contacting part is lubricated, the big and not enough problem of fuel feeding that cause of the width-diameter ratio that has solved radial sliding bearing has been improved the fuel feeding situation and the greasy property state of clutch shaft bearing.

Preferably; As shown in Figure 5, the inwall of the axis hole of clutch shaft bearing 1 is provided with oil groove 14, and the axioversion of oil groove 14 above-mentioned relatively axis hole on first end of clutch shaft bearing and the sidewall between second end extends; And this sidewall is provided with through hole 15, and oil groove 14 is communicated with through hole 15.Preferably, through hole 15 is arranged on the end of oil groove 14.Preferably, the distance between second end of through hole 15 and clutch shaft bearing is 1mm.Preferably, oil groove 14 is opened in little zone of load or non-bearing zone.Preferably, oil groove 14 helicallies are arranged on the inwall of axis hole of clutch shaft bearing 1.

Preferably, like Fig. 4, shown in 6, the perisporium of second shaft part is provided with second oilhole, 10, the second oilholes 10 and is communicated with the interior oil duct of bent axle, especially, correspondingly is provided with oil pocket at these second oilhole, 10 places.Be provided with the 3rd oilhole 11, the three oilholes 11 in the intermediate location of first shaft part of bent axle and eccentric shaft part and be communicated with oil duct in the bent axle, especially, 11 places correspondingly are provided with oil pocket at the 3rd oilhole.Not only can realize lubricated to the eccentric shaft part of bent axle through second oilhole and the 3rd oilhole, can also realize lubricated to other position, thereby improve the efficiency of rotary compressor.

Below, in conjunction with Fig. 6, to the width of the first annular contacting part of clutch shaft bearing and the second annular contacting part confirm be elaborated.

(1) confirms first end of clutch shaft bearing according to the dimensional space of rotary compressor and act on second end of first distance and clutch shaft bearing between the point of action of the external load on the bent axle and act on the second distance between the point of action of the external load on the bent axle; Through formula (A) and (B) confirm the width H of the first initial annular contacting part ₁Width H with the initial second annular contacting part ₂:

$\frac{H_2}{H_1}\frac{{2B}_2-H_2}{{2B}_1+H_1}=1$ Formula (A)

H ₁=B ₂-B ₁-H ₂Formula (B);

(2) confirm the span D of the internal diameter of clutch shaft bearing according to formula (C),

$\frac{F}{D}\frac{2B_1+2H_1+H_2}{H_1(H_1+H_2)}<\left[p\right]$ Formula (C);

(3) width with the width of the first initial annular contacting part and the initial second annular contacting part is a benchmark; Confirm a plurality of samples; Each sample all comprises the width of one first annular contacting part and the width of one second annular contacting part; Calculate the total friction power loss between the pairing bent axle of each sample and first shaft part, second shaft part, the pairing sample of minimum value of selecting total friction power loss is as the width of the first annular contacting part of clutch shaft bearing and the width of the second annular contacting part.Need to prove,, in the scope that dimensional space allows, get bigger shaft diameter (inside diameter D that is clutch shaft bearing is got bigger value), can guarantee that axle has enough rigidity with regard to sliding bearing; H ₁+ H ₂Value more little, the viscous friction of clutch shaft bearing loss W so _JlJust more little, but H ₁+ H ₂When too small, the stable variation of axle operation, the easy run-off the straight of bent axle, thus the solid contact takes place, cause the solid contact friction loss W of clutch shaft bearing _1cRise.

In formula (A), (B), (C), B ₁It is first distance between first end of clutch shaft bearing and the point of action that acts on the external load on the bent axle; B ₂It is the second distance between second end of clutch shaft bearing and the point of action that acts on the external load on the bent axle; H ₁It is the width of the first annular contacting part; H ₂It is the width of the second annular contacting part; F is the size of external load; D is the internal diameter of clutch shaft bearing; [p] is the oil pressure allowable value of clutch shaft bearing.

Derivation in the face of above-mentioned formula (A), (B), (C) describes down.

As shown in Figure 6, in the process of work, produce the first average oil film pressure P on the clutch shaft bearing ₁With the second average oil film pressure P ₂, the first average oil film pressure P ₁With the second average oil film pressure P ₂Act on the bent axle, make bent axle be in state of equilibrium.In addition, bent axle also receives the effect of external load F, and at this moment, bent axle satisfies following force system in equilibrium equation:

P ₁H ₁D-P ₂H ₂D＝F (1)

P ₁H ₁DL ₁-P ₂H ₂DL ₂＝0 (2)

Wherein, H ₁It is the width of the first annular contacting part; H ₂It is the width of the second annular contacting part; D is the internal diameter of clutch shaft bearing; F is the size of external load; L ₁Be the first average oil film pressure P ₁And act on the distance between the point of action of the external load on the bent axle, L ₂Be the second average oil film pressure P ₂And act on the distance between the point of action of the external load on the bent axle.

Further, can know by Fig. 6,

${\mathrm{<figure-callout\; id="1"\; label="L"\; filenames="HDA0000088410120000092.png"\; state="\{\{state\}\}">L</figure-callout>}}_1=B_1+\frac{H_1}{2}---\left(3\right)$

${\mathrm{<figure-callout\; id="2"\; label="L"\; filenames="HDA0000088410120000092.png"\; state="\{\{state\}\}">L</figure-callout>}}_2=B_2-\frac{H_2}{2}---\left(4\right)$

Wherein, B ₁It is first distance between first end of clutch shaft bearing and the point of action that acts on the external load on the bent axle; B ₂It is the second distance between second end of clutch shaft bearing and the point of action that acts on the external load on the bent axle.

Get by following formula (1), (3) and (4):

$\frac{P_1}{{\mathrm{<figure-callout\; id="2"\; label="P"\; filenames="HDA0000088410120000092.png"\; state="\{\{state\}\}">P</figure-callout>}}_2}=\frac{H_2}{H_1}\frac{L_2}{{\mathrm{<figure-callout\; id="1"\; label="L"\; filenames="HDA0000088410120000092.png"\; state="\{\{state\}\}">L</figure-callout>}}_1}=\frac{H_2}{H_1}\frac{{2B}_2-H_2}{2B_1+H_1}---\left(5\right)$

Further, the ideal design state of clutch shaft bearing should satisfy following condition:

$\frac{P_1}{{\mathrm{<figure-callout\; id="2"\; label="P"\; filenames="HDA0000088410120000092.png"\; state="\{\{state\}\}">P</figure-callout>}}_2}=1---\left(6\right)$

Therefore, obtain formula (A) by following formula (5), (6).

Further, get by following formula (1), (6), (3) and (4)

${\mathrm{<figure-callout\; id="1"\; label="P"\; filenames="HDA0000088410120000092.png"\; state="\{\{state\}\}">P</figure-callout>}}_1=\frac{F}{H_1\mathrm{<figure-callout\; id="1"\; label="D"\; filenames="HDA0000088410120000092.png"\; state="\{\{state\}\}">D</figure-callout>}}\frac{1}{1-\frac{L_1}{{\mathrm{<figure-callout\; id="2"\; label="L"\; filenames="HDA0000088410120000092.png"\; state="\{\{state\}\}">L</figure-callout>}}_2}}=\frac{F}{D}\frac{{2B}_2-H_2}{({2B}_2-{2B}_1-H_2)H_1-H_1^2}---\left(7\right)$

During design, hope P ₁As far as possible little, further, when

H ₁=B ₂-B ₁-H ₂When (8) (promptly obtaining formula (B)), P ₁Minimalization

${\mathrm{<figure-callout\; id="1"\; label="P"\; filenames="HDA0000088410120000092.png"\; state="\{\{state\}\}">P</figure-callout>}}_1=\frac{F}{D}\frac{{2B}_1+{2H}_1+H_2}{H_1(H_1+H_2)}---\left(9\right)$

Simultaneously, P ₁And satisfy the oil pressure allowable value [p] of clutch shaft bearing, promptly

P ₁≤[p] (10)

Therefore, obtain formula (C) by above-mentioned (9), (10).

Preferably, carried out optimal design at second shaft part to the bent axle in the foregoing description, as shown in Figure 6; The end portion, supports of second shaft part of bent axle on the stop surface of second bearing, thereby form backstop to bent axle, thereby shortened the length of second shaft part; Second shaft part need not insert in the axis hole of second bearing; One direction has been saved material, has simplified the structure of system on the other hand, and has avoided wearing and tearing.Fig. 7 shows the structural representation of the thrust surface among Fig. 6, and the thrust surface in visible the utility model is circular regular texture, and the irregular thrust surface than existing technology more should form effective dynamic lubrication.Preferably, the corresponding zone of oil duct with in second shaft part of second bearing is provided with through hole 14, and especially, the diameter of this through hole 14 is less than the diameter of second shaft part, and through hole is blocked in the end of second shaft part.Especially, in order to obtain more effectively dynamic lubrication, under the situation of considering the product size space, can increase the diameter of said second shaft part as much as possible.Further, as shown in Figure 8, when the inclination of bent axle is big more, the maximal clearance H between the end face of the thrust surface and second shaft part ₀Also become big, thereby form thicker oil film more easily, thereby produce more efficiently hydrodynamic lubrication, so that friction power loss between the end face of thrust surface and second shaft part and wear extent decline, thereby improved the efficiency of rotary compressor.At this moment, total friction power loss loss comprises that the viscous friction of clutch shaft bearing loses W _Jl, clutch shaft bearing solid contact friction loss W _1cAnd the friction power loss between the end face of the thrust surface and second shaft part; Like this; Just can be according to the variation relation (as shown in Figure 9) of total friction power loss loss with the length (i.e. the width of the first annular contacting part and the second annular contacting part) of clutch shaft bearing, the width of confirming the rational first annular contacting part and the second annular contacting part is (promptly; H ₁+ H ₂Value).In Fig. 9, the longitudinal axis is the ratio (no unit) of friction power loss, promptly chooses certain length H ₁+ H ₂Under friction power loss be worth as a reference.In addition, second shaft part is designed to above-mentioned form, has reduced a friction pair, and reduced finishing step one; Simultaneously, also reduce the center of gravity of compressor, thereby reduced the vibration and the noise of compressor.

Below in conjunction with a concrete embodiment the utility model is further specified.

At first,, on the basis of the revolution support system of the existing compressor of existing technology, can confirm the width of the first annular contacting part and the second annular contacting part in a manner mentioned above, thereby accomplish corresponding design for revolution support system shown in Figure 5.

Secondly; For revolution support system shown in Figure 6; Can utilize formula (A) and formula (B) earlier; Utilize the minimized principle of bearing load to confirm the method for bearing size, confirm the bearing size parameter haply, and then confirm suitable bearing parameter according to the principle of minimumization of friction power loss.

For example:,, get B according to its dimensional space for the rotary compressor of a model ₁=10mm, B ₂＜50mm solves significant separating: H according to formula (A) and formula (B) ₁=26.055mm, H ₂=13.945mm is then with H ₁, H ₂Value substitution W formula (C) in, obtain:

$D\&GreaterEqual;0.0826\frac{F}{\left[p\right]}$

If average oil pressure allowable value [the p]=10MPa of clutch shaft bearing, external load F=1400N then obtains the inside diameter D >=11.564mm of clutch shaft bearing.

Consider the requirement of product size space and rigidity, the inside diameter D value of clutch shaft bearing is 18mm.For the diameter of second shaft part, consider the product size space, for effectively forming dynamic lubrication, should design bigger thrust surface as much as possible, for example, in the present embodiment, the internal diameter of second bearing is got 6mm, and the external diameter of second shaft part is got 12mm.

Width with the width of the said initial said first annular contacting part and the said initial said second annular contacting part is a benchmark; Confirm a plurality of samples (as shown in table 1); Calculate the total friction power loss between the pairing bent axle of each sample and first shaft part, second shaft part, and analyze friction power loss with sample changed trend (shown in figure 10).Thereby confirm optimum value: H ₁=24.752mm, H ₂=13.247mm.

Table 1

Sample number	1	2	3	4	5	6	7
								H 1	22.147	23.45	24.752	26.055	27.357	28.661	29.963
H 2	11.853	12.55	13.247	13.945	14.642	15.340	16.037

The preferred embodiment that the above is merely the utility model is not limited to the utility model, and for a person skilled in the art, the utility model can have various changes and variation.All within the spirit and principle of the utility model, any modification of being done, be equal to replacement, improvement etc., all should be included within the protection domain of the utility model.

Claims (9)

1. lubricating structure is supported in the revolution of a rotary compressor, it is characterized in that, comprising:

Bent axle is provided with the axially extended oil duct along said bent axle in the said bent axle, said bent axle comprises first shaft part, second shaft part and is arranged on the eccentric shaft part between said first shaft part and second shaft part; On the upper-end surface of the cylinder of said rotary compressor and lower end surface, be respectively arranged with the clutch shaft bearing and second bearing, the said clutch shaft bearing and second bearing support said first shaft part and second shaft part respectively, and said eccentric shaft section is positioned at said cylinder;

Said clutch shaft bearing comprises axis hole; Said first shaft part is located in the said axis hole; Between said first shaft part and said axis hole, contact slidably each other with the second annular contacting part through the first annular contacting part; Said clutch shaft bearing comprises first end and second end, and the said first annular contact position is in a side of said first end, and the said second annular contact position is in a side of said second end; Between the said first annular contacting part and the second annular contacting part, be provided with annular oil cavity; First end of said clutch shaft bearing contacts with said cylinder.

2. lubricating structure is supported in revolution according to claim 1, it is characterized in that the position corresponding to said annular oil cavity of said bent axle is provided with first oilhole, and said annular oil cavity is communicated with through said first oilhole with said oil duct.

3. lubricating structure is supported in revolution according to claim 1; It is characterized in that; The inwall of the axis hole of said clutch shaft bearing is provided with oil groove; The axioversion of said oil groove said relatively axis hole on first end of said clutch shaft bearing and the sidewall between second end extends, and this sidewall is provided with through hole, and said oil groove is communicated with said through hole.

4. lubricating structure is supported in revolution according to claim 3, it is characterized in that said through hole is arranged on the end of said oil groove.

5. lubricating structure is supported in revolution according to claim 1, it is characterized in that the end portion, supports of second shaft part of said bent axle is on the end face of said second bearing.

6. lubricating structure is supported in revolution according to claim 5, it is characterized in that, said second bearing with said second shaft part in the corresponding zone of said oil duct in be provided with through hole.

7. support lubricating structure according to each described revolution among the claim 1-6, it is characterized in that the perisporium of said second shaft part is provided with second oilhole, said second oilhole is communicated with the interior said oil duct of said bent axle.

8. lubricating structure is supported in revolution according to claim 7, it is characterized in that be provided with the 3rd oilhole at first shaft part of said bent axle and the intermediate location of eccentric shaft part, said the 3rd oilhole is communicated with said oil duct.

9. support lubricating structure according to each described revolution among the claim 1-6, it is characterized in that said annular oil cavity is a groove, said groove is arranged on the inwall of said clutch shaft bearing or is arranged on the outer surface of said first shaft part.

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