CN1089864C

CN1089864C - Closed type compressor

Info

Publication number: CN1089864C
Application number: CN97118242A
Authority: CN
Inventors: 铃木一浩; 石山明彦; 内田宏政; 长里胜美
Original assignee: Hitachi Ltd
Current assignee: Hitachi Ltd
Priority date: 1996-09-10
Filing date: 1997-09-09
Publication date: 2002-08-28
Anticipated expiration: 2017-09-09
Also published as: JPH1089255A; KR100227420B1; CN1186165A; KR19980024449A

Abstract

To effectively feed lubrication oil to the pressure surface of a slicler during a compression process, in a scotch yoke type hermetic motor-driven compressor. A slider 8 is reciprocated in a slide pipe 10b, formed integrally with a piston 10, since an eccentric part 6a in which a slider 6a is rotatably fitted is eccentrically rotated. A crank pin branch hole 6d extending through an inner surface to an outer surface is formed in the eccentric part 6a and this constitution feeds lubrication oil to the inner surface of the fitin hole of the eccentric part 6a of the slider 8 from the interior of the eccentric part 6a. Further, a slider oil feed hole 8c extending through the fit-in hole of the slider 8 to an outer peripheral part 8b. When the slider oil feed hole is connected to a crank pin branch hole 6d, lubrication oil is fed to the outer surface part 8b of the slider 8 from the interior of the eccentric part 6a. An opening at the slider oil feed hole 8c and on the outer peripheral surface 8b side of the slider 8 is set to a position in the vicinity of a part making contact with a slide pipe 10b making contact with a slide pipe 10b during the compression stroke of the outer peripheral surface 8b of the slider 8.

Description

Hermetic motor compressor

Technical field:

The present invention relates to be installed on refrigerating device for example the electricity of the so-called scotch yoke formula in the refrigerator drive

Hermetic motor compressor, be specifically related to a kind of so electrically driven (operated) hermetic motor compressor, wherein change

Advanced the lubrication property of moving element between piston type slip pipe and sliding sleeve, thereby demonstrated very high

The friction resistant feature.

Background technique: Fig. 9 is vertically the cuing open of hermetic motor compressor structure of traditional scotch yoke formula by motor driven

Face figure, the label 1 among the figure refers to closed container, 2 refer to the motor parts, the 3 finger pressures machine mechanism part that contracts,

4 specify son, and 5 refer to rotor, and 6 refer to bent axle, and 6a refers to eccentric part, the inwall of 6b spindle receiving hole,

Septated hole on the 6c spindle acceptance division, 6d refers to the septated hole on the crankpin, 6e refers to the crankpin inwall

Top edge, 7 refer to frameworks, 8 refer to sliding sleeves, 9 refer to cylinders, 9a refers to the interior circumferential portion of cylinder, 10

Refer to piston, 10a refers to the outer peripheral portion of piston, and 11 refer to refrigerator oil (lubricant oil), and 12 refer to pump

Parts, and 13 thrum springs.

Generally, as shown in Figure 9, in this hermetic motor compressor, motor part 2 is located at sealing

The bottom of container 1,3 of compressor means parts are located at the top that point 1 is held in sealing, and they pass through

Spring 13 flexibly is supported in the closed container 12.Motor part 2 is by 5 groups of stator 4 and rotors

Become, the bent axle 6 that inserts in the rotor 5 has an eccentric part 6a who rotates with it (to be called " bent axle later on

Pin ").

Compressor section 3 comprises: bent axle 6, as this bent axle lay the framework 7 of portion, with bent axle

6 rotational transform is reciprocating sliding sleeve 8 and back and forth transports with the sliding sleeve motion in cylinder 9

Moving to change the piston 10 that volume promptly repeats suction process and compression process.

Accumulate the bottom of closed container 1 refrigerator oil 11, is used for protecting each motion parts to avoid different

Normal wearing and tearing or by jam, and be used for making their smooth motions.Refrigerator oil 11 is by being located at bent axle 6 times

The pumping that makes progress of pump parts 12 in the portion, the rotation by bent axle 6, and owing to also increased because bent

Axle 6 the centrifugal force that rotation produced and rising on the inwall 6b of the batter that is coupling of bent axle 6.To

The refrigerator oil 11 of last pumping is separated, and a part is supplied to the part that must move, passes through bent axle

The septated hole 6c of 6 axle acceptance division or be located at the septated hole 6d (being the crankpin septated hole) of crankpin 6a, remaining part then scatters from the top edge 6e punishment of crankpin 6a inwall, part is fed to the interior perimembranous 9a (being the interior week of cylinder) of cylinder 9, and part is supplied with piston 10 (being the periphery of cylinder).

Figure 10 (a) and 10 (b) have shown cylinder 9, piston 10, sliding sleeve 8 and the compression process of bent axle 6 in the closed type electromotive compressor of scotch yoke formula, have shown simultaneously to give their runners of each supply refrigerator oil 11.Figure 10 (a) is a vertical cross section, and Figure 10 (b) is the horizontal sectional drawing along line of cut A-A among Figure 10 (a), label 8a wherein refers to that the internal diameter of sliding sleeve (is called " sliding sleeve internal diameter " later on, 8b refers to the peripheral part of sliding sleeve, 8c refers to the oil supply hole of sliding sleeve and 10b refers to sliding tube, wherein for attached with identical label with corresponding part shown in Figure 9 and/or parts.

In Figure 10 (a) and 10 (b), crankpin 6 is with the central axis eccentric rotary of radius of gyration R around bent axle 6, and rotatably with predetermined gap be inserted into piston 10 integrant sliding tube 10b in move.As crankpin 6a during by described mode eccentric rotary, sliding sleeve 8 just moves in sliding tube 10b thereupon, meanwhile, and piston 10 to-and-fro motion cylinder 9 in, the suction and the compression process of repetition gas in cylinder 9 thus.

Refrigerator oil 11 is shown in arrow among Figure 10 (a), the inwall 6b that rises to the batter that is coupling goes up and shunts as follows: first portion, and it is supplied in the internal diameter 8a and the hole C1 between the crank pin 6a (being referred to as " crankpin gap " later on) of sliding sleeve from the septated hole 6d of crank pin; Second portion, when it cooperates with the septated hole 6d of crankpin by the rotation of crankpin 6a as the sliding sleeve oil supply hole a that is provided with along the axis of piston 10 from the center of slider internal diameter 8a, by the septated hole 6d and the sliding sleeve oil supply hole 8c of crankpin, supply with the outer circumferential face 8b (being the sliding sleeve outer circumferential face) of sliding sleeve 8 and the hole C2 (being referred to as " sliding tube gap " later on) between the sliding tube 10; Third part, it disperses by crankpin inwall top edge 6e, connects the clearance C 3 (being referred to as " glade plane space " later on) between the outer circumferential face 10a of the interior circumferential portion 9a of supply cylinder 9 and piston 10 again; The 4th part, in a single day it promptly supplies with sliding tube clearance C 2 in the mode that flows into after being attached to sliding sleeve outer circumferential face 8b.

But the heat that the viscosity coefficient Yin Mada 2 (Fig. 9) of refrigerator oil 11 produces reduces with the frictional heat of each moving element, and refrigerator oil has just reduced lubricating coefficient thus for the refrigerant that sucks in the closed container 1 dilutes simultaneously.Like this, owing to reduced the viscosity coefficient of refrigerator oil 11, become big from the distance of crankpin inwall top edge 6e institute spreading refrigerator oil 11, the result will wear away between sliding sleeve outer peripheral portion 8b and sliding tube 10b, reliability is reduced, this is because supplying with the amount of the refrigerator oil 11 of sliding tube clearance C 2 reduces, or the like.

In addition, shown in Figure 10 (b), to be used for oil is supplied to the sliding sleeve oil supply hole 8C position of sliding tube clearance C 2 be that the axis along piston 10 distributes through the center of 8a in the sliding sleeve owing to be provided with, this oil supply hole just just just lead to the septated hole 6d of crankpin by the moment when just finishing the compression process load and reach maximum, but form in the compression process of oil film when supplying refrigerator oil, do not give sliding tube clearance C 2 fuel feeding again.So just can not improve the abrasion between sliding sleeve outer peripheral portion 8b and sliding tube 10b significantly.

For this reason, as the countermeasure that solves the abrasion between sliding sleeve peripheral part and slip pipe, all imaginations have been made in the prior art.For example in clear 57-73384 number disclosed closed type electromotive compressor of Japan Patent (disclosing), it is a kind of new imagination that oil drainage hole is positioned on the sliding sleeve peripheral part, and in clear 58-109577 number disclosed closed type electromotive compressor of Japan Patent (disclosing), sliding sleeve then is to be become by the hollow tubular system, and the septated hole of crankpin and this hollow aperture then are to be under the condition of not conducting refrigerator oil is supplied to each motion parts and parts.

But in any above-mentioned prior art, all reckon without this fact: supply with the absolute oil mass in sliding tube gap, owing to the feasible spreading from crankpin of oil body coefficient decline reduces apart from increasing.In clear 58-109577 number disclosed closed type electromotive compressor of above-mentioned Japan Patent (disclosing), because sliding sleeve is to be become by the hollow tubular system, lubricant oil just will be along the peripheral direction spreading of axle but not directly is supplied to sliding tube clearance C 2 (Figure 10 (b)), so just is helpless to the improvement of attrition resistance.

Summary of the invention: in order to address the above problem, one of purpose of the present invention is to provide a kind of height reliable hermetic motor compressor, wherein improved the lubricant oil method of supplying in sliding tube gap and formed oil film fully, improved the friction resistant characteristic of sliding tube and/or sliding sleeve peripheral part therefrom.

To achieve these goals, according to the invention provides a kind of hermetic motor compressor, it comprises:

Cylinder;

Reciprocating piston in cylinder;

According to inserting perpendicular to the direction of piston central axial line in the piston and forming the sliding tube of unit with piston;

Be movably located on the sliding sleeve in the sliding tube; And

Rotatingshaft, this rotatingshaft has one to insert the eccentric part in the above-mentioned sliding sleeve rotationally and be formed on lubricated bent road in it, wherein be provided with the inboard and the outside that an eccentric part septated hole passes the endoporus of this rotatingshaft, simultaneously be provided with oil supply hole on this sliding sleeve, the outer surface with above-mentioned sliding sleeve leads in the compression process so that described eccentric part septated hole is at piston.

In addition, according to the present invention, the aperture position of sliding sleeve oil supply hole on the sliding sleeve peripheral part then is located at, and when the piston in the cylinder carried out compression process to gas, the peripheral part of above-mentioned sliding sleeve abutted to the vicinity of the part on the sliding tube internal surface.

Adopt said structure, lubricant oil just can supply with effectively in compression process, to recline that part of on the sliding tube internal surface that is positioned on the sliding sleeve side face.

Have again, according to the present invention, being located at can be in constituting sliding sleeve fuel supply line on the sliding sleeve reciprocating in the sliding tube of unit through being arranged to piston, in the process of gas by the Piston Compression in the cylinder, this oil supply hole can lead to the eccentric part septated hole that is located in the crankshaft eccentric portion that rotatably inserts in this sliding sleeve.

Like this, in compression process, when strengthening the load of this sliding sleeve therefrom on sliding sleeve clings to the internal surface of sliding tube, lubricant oil is promptly by these eccentric part septated holes and sliding sleeve oil supply hole, is supplied in clinging on sliding tube internal surface that part of of sliding sleeve peripheral part.

Also have,, be provided with a chute in the periphery of the sliding sleeve oil supply hole on the sliding sleeve outer periphery according to the present invention.

Under said structure, even lubricant oil is when stopping making machine not carry the internal surface of rotatingshaft, because contain lubricant oil in above-mentioned chute, when compressor started once more, this stored in lubricant oil in the chute and just is fed between sliding sleeve peripheral part and the sliding tube internal surface and is lubricated.

Description of drawings: Fig. 1 is the sectional drawing that amplifies as the closed type electromotive compressor major component of a kind of form of implementation of the present invention;

Fig. 2 shows be applied to the characteristic curve of the pressure on the sliding sleeve with respect to the eccentric rotary angle of crankpin in general closed type electromotive compressor;

Fig. 3 shows among bright left Fig. 1 embodiment, the position the when sliding sleeve in the sliding tube rotates with respect to the sliding sleeve pin, and the relation of the position between crankpin septated hole and the sliding sleeve oil supply hole.

Fig. 4 is a vertical cross section, shows when sliding tube tilts in any compression process of Fig. 2 the tilt condition of sliding sleeve.

Fig. 5 is a vertical cross section, shows in any compression process of the above embodiment of the present invention the desired location of sliding sleeve oil supply hole;

Fig. 6 is the vertical cross section of the sliding sleeve oil feeding mechanism in the above embodiment of the present invention;

Fig. 7 is the amplification vertical cross section of sliding sleeve major component among Fig. 6;

Fig. 8 is the amplification vertical cross section of sliding sleeve major component among Fig. 6;

Fig. 9 is a vertical cross section, the closed type electromotive compressor that illustration is traditional; And

Figure 10 is the sectional drawing that amplifies, and shows the joint of bent axle shown in the above-mentioned traditional closed type electromotive compressor and piston space.

Concrete enforcement

Embodiments of the invention are described with reference to the accompanying drawings all sidedly.Mode:

Fig. 1 shows the embodiment's of closed type electromotive compressor of the present invention major component, wherein figure

1 (a) is its vertical cross section, and Fig. 1 (b) is the horizontal section along line of cut A-A among Fig. 1 (a)

Figure.Attached with identical label among Fig. 1 with corresponding part described in Fig. 9 and 10 and/or parts

Omit its duplicate explanation.

In Fig. 1 (a) and 1 (b), when bent axle 6 rotations, it is axial that the refrigerating machine pasta rises to bent axle 6

On the inwall 6b in hole, rise to simultaneously on the inwall of crankpin 6a.At this moment, part refrigerator oil

The centrifugal force that the eccentric rotary of 11 logical crankpin 6a produces is supplied with crankpin from crank pin septated hole 6d

Part clearance C 1.This part refrigerator oil 11 of supplying with this gap C1 further passes with sliding sleeve 8

Endoporus 8a and the sliding sleeve oil supply hole 8c that leads to of outer periphery 8b, flow in the sliding tube clearance C 2,

6d often is supplied with refrigerator oil 11 from the crankpin septated hole, thereby refrigerator oil can be supplied with sliding

Moving ligament C2.

Here, suppose that lower dead center is 0 ° of angle, is added to the load (institute on the sliding sleeve peripheral part 8b

Applied pressure) as shown in Figure 2, the rotational angle as crankpin 6a is in 0 ° of supreme ending of lower dead center

In the scope that point is 180 °, increase to maximum in compression process.Particularly change in the off-centre of crankpin 6a

Moving angle is in 130 ° to 180 ° scope the time, and sliding sleeve peripheral part 8b goes up applied pressure and reaches

Greatly.When load becomes big, must in above-mentioned scope, give in the sliding tube clearance C 2 and supply refrigerator oil

11。

According to this embodiment, shown in Fig. 1 (b), for refrigerator oil 11 is supplied with the sliding tube gap

C2,8c is opened on the sliding sleeve 8 in such a way with the sliding sleeve oil supply hole, makes this sliding sleeve fuel feeding

Hole 8c the eccentric rotary face of crankpin 6a in 0 ° of lower dead center to 180 ° of scopes of top dead center in one

During predetermined angle, lead to the septated hole 6d of crankpin.In other words, in biography shown in Figure 10

In the system technology, sliding sleeve oil supply hole 8c is the axis from the center of sliding sleeve endoporus 8a along piston 10

Be provided with, and in the present embodiment, sliding sleeve oil supply hole 8c then is along being parallel to straight line and logical

Cross the form of straight lines setting at the center of sliding sleeve endoporus 8a, this straight line then with piston 10

Axis parallels and separates.

Fig. 3 has shown sliding sleeve 8 position with respect to sliding sleeve pin 6a in sliding tube 10b, and the position of crankpin septated hole 6d and sliding sleeve oil supply hole 8c relation, show that wherein sliding sleeve pin 6a in the eccentric rotary (changes) of understanding at 180 ° is in 0 ° (360 °), 90 °, 130 °, the 180 ° various situations during with 270 ° of rotations.

Prove the operation of this closed type electromotive compressor below referring to Fig. 2.

Among Fig. 2,, be applied to the load minimum on the sliding sleeve peripheral part 8b, and the crankpin septated hole 6d that is positioned at piston 10 opposite sides does not overlap with sliding sleeve oil supply hole 8c promptly when the rotational angle of crankpin 6a is when 0 ° (lower dead center).Crankpin 6a makes eccentric rotary with respect to sliding sleeve 8 counter clockwise according to shown in Figure 2, and sliding sleeve 8 then moves in sliding tube 10B according to the arrow B direction, and piston 10 moves according to the arrow A direction simultaneously.Like this, the gas in the cylinder 9 is compressed the pressure that is applied on the sliding sleeve peripheral part 8b gradually and then strengthens, as shown in Figure 2.

When the eccentric rotary angle of crankpin 6a reaches 90 °, sliding sleeve 8 just is in the state towards the motion of arrow B direction with respect to sliding tube 10B basically, and crankpin 6a then is in and turns over 90 ° state with respect to sliding sleeve 8 in the direction of the clock.Under above-mentioned state, crankpin septated hole 6d does not still overlap with sliding sleeve fuel supply line 8c.When the further eccentric rotary of crankpin, although sliding sleeve 8 beginning with respect to sliding tube 10b according to the arrow B opposite with the arrow B direction ' the direction motion, but piston 10 continues to move according to the arrow A direction, gas in the cylinder 9 then further is compressed, and has also further strengthened the pressure that is applied on the sliding sleeve peripheral part 8b.

When the eccentric rotary angle of crankpin 6a reaches 130 °, when the gas pressures in the cylinder 9 reached a predetermined value, the gas of pressurized just began to discharge from cylinder 9.Meanwhile, crankpin septated hole 6d promptly leads to sliding sleeve oil supply hole 8c, and like this, refrigerator oil 11 just is fed to sliding tube clearance C 2 from the inwall of crankpin 6a.

When the further eccentric rotary of crankpin 6a, slider 8 with respect to sliding tube 10b according to arrow B ' direction motion, and piston 10 is further according to the motion of arrow A direction, the gases that are compressed in this moment in the cylinder 9 continue to discharge.Immediately, crankpin septated hole 6d is separated from sliding sleeve oil supply hole 8c.When the eccentric rotary angle of crankpin 6a reaches 180 °, crankpin septated hole 6d is positioned at the piston side on piston 10 central axis, and under this kind state, piston 10 is motion to greatest extent in the direction of arrow A, so far finishes to discharge gases from cylinder 9.

When crankpin 6a continues eccentric rotary, though slider 8 continue with respect to sliding tube 10b towards arrow B ' the direction motion, 10 in piston conversely along the arrow A opposite with arrow A ' direction move.Meanwhile, pressure anticlimaxs in the cylinder 9 and gas is sucked in the cylinder 9, and also the pressure that is applied on the slider peripheral part 8b also descends suddenly.Then, when the eccentric rotary angle of crankpin 6a reaches 270 °, sliding sleeve 8 under this state according to arrow B ' direction do motion to greatest extent, and constantly from this, sliding sleeve 8 is just changed into the direction of arrow B with respect to the moving direction of sliding tube 10b, and the eccentric rotary angle that always proceeds to crankpin 6a reaches 0 °.During the period, piston 10 continues according to arrow A ' direction motion gas to be sucked in the cylinder 9.

Under aforesaid way, in the eccentric rotary angle of crankpin 6a (in the above-mentioned example, be when being 130 °) at the eccentric rotary angle of crankpin 6a, from 0 ° to 180 ° compression process, by with the position regulation of the sliding sleeve oil supply hole 8c of sliding sleeve 8 to partially or entirely leading at the septated hole 6d of predetermined instant with crankpin, just can be in compression process institute's application of load when maximum, refrigerator oil is supplied in sliding sleeve peripheral part 8b compression-side (piston side), so just can reduces sliding sleeve significantly the abrasion between perimembranous 8b and the sliding tube 10b.

In the above, although understand the moment that crankpin septated hole 6d and sliding sleeve oil supply hole 8c partly or entirely lead to, be equal to the pressure that is applied on the sliding sleeve peripheral part 8b and almost reach the peaked moment shown in Figure 2 (being about 130 ° moment of eccentric rotary angle of crankpin 6a), and be set to this and constantly just can form oil film most effectively, if but the eccentric rotary face of crankpin 6a is in about 90 ° to 180 ° scope, also can between sliding sleeve peripheral part 8b and sliding tube 10b, (being sliding tube clearance C 2) form oil film effectively, so just can reduce abrasion effectively and the very high reliability of acquisition.

In addition, sliding sleeve oil supply hole 8c only is located on piston 10 1 sides of sliding sleeve 8.This is because by the sliding sleeve 8 of research after the Continuous Drive test of finishing compressor, finds that abrasion on piston 10 1 sides are than anti-violent on piston 10 1 sides.Act on sliding sleeve 8 anti-pressure on piston 10 1 sides, owing to be in suction process, to be loaded into instead on a side of piston 10 in the model that carries out above-mentioned driving test, compare with the pressure on piston 10 these sides of sliding sleeve, become the about 1/20 of this force value, thereby can be lubricated fully with a certain amount of lubricant oil that from respective aperture, oozes out.

Have again, as shown in Figure 4, sliding sleeve 8 is owing to the rotation of crankpin 6a inhour trend (be arrow C show to) is tilted by sliding tube clearance C 2, so cause a part of 8j that load is high and the low part of loading on the compression-side (being this side of piston 10) of sliding sleeve peripheral part 8b in compression process.This part the high 8j that loads is positioned on peripheral part top edge face outside one side that the 6a of crankshaft eccentric portion on the 8b compression-side of sliding sleeve lateral part makes eccentric rotary.In sliding sleeve 8a, sliding sleeve oil supply hole 8c is located on this side of the slider peripheral part 8b that is defined as compression-side, its present position then is located at becomes the limit of high load part 8j part vicinity in the compression process, this position then makes as previously mentioned around oilhole 8c when crankpin 6a is in about 90 ° to 180 ° scopes at its eccentric rotary angle, partly becomes entirely to lead to crankpin septated hole 8c.Thus just can be reliable and effectively refrigerator oil 11 is supplied with the high load part 8j of sliding sleeves 8 peripheral part 8b, there is oil film to be formed at reliably between the internal surface of high load part 8j and sliding tube 10b simultaneously, thereby can improves the abrasion resisting performance between sliding sleeve peripheral part 8b and sliding tube 10b significantly.

Have again, refrigerator oil 11 just thinks that crankpin septated hole 6d just is supplied in sliding sleeve peripheral part 8b when being communicated with oil supply hole 8c, outside at this moment, the refrigerator oil 11 that flows into crankpin septated hole 6d is just supplied with between the 8a of endoporus portion of the peripheral part of crankpin 6a and sliding sleeve, like this, crankpin part clearance C 1 just can not lack the lubricant oil supply, and can reduce abrasion between crankpin 6a and the sliding sleeve endoporus 8a of portion.

Fig. 5 is a vertical cross section, is used for showing another embodiment's of closed type electromotive compressor of the present invention major component, and is attached with identical label corresponding in the past illustrated part and/or parts among the figure.

In the aforementioned embodiment, shown in Fig. 1 (b), sliding sleeve oil supply hole 8c is that the central axial line with piston 10 is located on the sliding sleeve 8 with paralleling, but according to present embodiment, as shown in Figure 5, above-mentioned oil supply hole is then with respect to the formation inclination angle shown in Fig. 1 (b), that is along the straight line by sliding sleeve 8 endoporus 8a centers, and almost be to point on this part of sliding sleeve 8 peripheral part 8b compression-sides, and this part promptly becomes high load part 8j in compression process.

In compression process, when crankpin septated hole 6d and sliding sleeve oil supply hole 8c lead under the predetermined angle in crankpin 6a eccentric rotary mutually, these two holes just point-blank, the result, refrigerator oil 11 just with centrifugal force to from crankpin septated hole 6d along the peripheral direction spreading, under this spreading state,, arrive on the high load part 8j of sliding sleeve 8 peripheral part 8b compression-sides by above-mentioned fuel supply line 8c.So just can provide more refrigerator oil to the sliding tube gap, and because oil supply hole 8c is provided in a side of the vicinity of the high load part 8j of sliding sleeve lateral part 8b compression-side, just lubricant oil directly can be supplied to the 8j of high load portion, be convenient to like this on this part, form oil film, and can significantly improve attrition resistance between sliding sleeve peripheral part 8b and the sliding tube 10b.

Fig. 6 is a major component of showing bright sliding sleeve 8 another examples, and label 8d wherein refers to sliding sleeve fuel feeding chute, and is then attached with identical label with former corresponding part and/or parts among the figure.

Among Fig. 6, sliding sleeve fuel feeding chute 8d is located at the orifice part office of the sliding sleeve oil supply hole 8c on the sliding sleeve peripheral part 8b, is able to the refrigerator oil that sliding sleeve oil supply hole 8c supplies with sliding sleeve peripheral part 8b gathered be used for collecting among the fuel feeding chute 8d of this oil.

To this closed type electromotive compressor re-lighting and parking operation.After stopping, arrives by this compressor starting once more, for making the refrigerator oil of building up in closed container 1 (Fig. 9) bottom 11 be fed to the sliding tube clearance C 2 that is positioned at this container 1 top, need for some time, therefore, within period, sliding tube clearance C 2 just is in does not have its state of oil supply at this section.

Aforesaid sliding sleeve oil supply 8d is set in above-mentioned example now, refrigerator oil 11 just can be gathered in wherein, when the refrigerator oil of being assembled 11 is used in this closed type electromotive compressor starting, so just can not occur in the operation under the no-oil-supply state, and can be able to significantly improve the abrasion resisting performance of sliding sleeve peripheral part 8b and sliding tube 10b.

Have again, as shown in Figure 7, form wide than sliding sleeve oil supply hole 8c, perhaps angular surface type is processed in the aperture of this oil supply hole 8c by the diameter that makes sliding sleeve fuel feeding chute 8d, just can be easily with refrigerator oil 11 supply sliding tube clearance C 2.

In addition, if sliding sleeve oil supply 8d be parallel to the axial setting of sliding tube 10b and extend axially along this, just can be to the total length of sliding sleeve 8 fuel feeding equably basically.

Now the example shown in Fig. 6 to 8 is combined with aforementioned each embodiment, just can more reliably refrigerator oil 11 be supplied with sliding tube clearance C 2, can solve simultaneously no-oil-supply to the shop problem under this gap C2 state, even this closed type electromotive compressor constantly repeats its starting and stops moving already also harmless, can improve the abrasion resisting characteristic between sliding sleeve peripheral part 8b and sliding tube 10b thus, and make this compressor have very high reliability.

According to above comprehensive explanation, according to the present invention, can reliably lubricant oil be supplied to the sliding tube gap, can avoid simultaneously not having operation under the condition that oil is supplied in this gap, thereby can improve the abrasion resisting performance between sliding sleeve peripheral part and the sliding tube, make this closed type electromotive compressor show very high reliability simultaneously and unusual friction and jam can not take place.

Claims

1. hermetic motor compressor, this compressor comprises: cylinder; Reciprocating piston in cylinder; According to inserting perpendicular to piston central axial line direction in the piston and forming the sliding tube of unit with piston, be movably located on the sliding sleeve in the sliding tube, and rotatingshaft, this rotatingshaft has one to insert the eccentric part in the above-mentioned sliding sleeve rotationally and be formed with oil leab in it, wherein be provided with the inboard and the outside that an eccentric part septated hole passes the described hole of this rotatingshaft, simultaneously on sliding sleeve, be provided with oil supply hole, so that the moment that the pressure of described eccentric part septated hole on being applied to the cylinder peripheral part begins to discharge gas when almost reaching maximum value leads to the outer surface of above-mentioned sliding sleeve.

2. hermetic motor compressor, it has a closed container, bottom accumulation at it has lubricant oil, be provided with the compression mechanical part that comprises piston and cylinder on the top of closed container, the motor that this mechanism is located on this closed container bottom connects, and includes eccentric part by one and is able to motor driven for this reason with the rotatingshaft that extends to the hollow endoporus of this eccentric part;

One columniform sliding tube is arranged, and piston forms the unit along extending also therewith perpendicular to the central axial line direction of above-mentioned piston, in this sliding tube, be provided with a movably cylindrical sliding sleeve, the eccentric part of such rotation axle passes sliding tube and rotatably inserts within the sliding sleeve, wherein, along with the eccentric rotary that is this rotatingshaft eccentric part of described motor driven, the i.e. to-and-fro motion in sliding tube of this sliding sleeve, this sliding tube makes piston along himself central axial line direction to-and-fro motion then along the direction to-and-fro motion of aforementioned piston middle spindle line therefrom simultaneously;

Bore area from above-mentioned eccentric part one bore area to sliding sleeve penetratingly is provided with an eccentric part septated hole, in order to supply aforementioned lubricant oil, this lubricant oil is inhaled into the bore area by rotatingshaft, arrives the internal surface of oil jacket by the eccentric part septated hole from the bore area of described eccentric part;

From then on the endoporus of sliding sleeve extends through its peripheral part and is provided with the sliding sleeve oil supply hole, so that the moment that the pressure of described eccentric part septated hole on being applied to the cylinder peripheral part begins to discharge gas when almost reaching maximum value communicate with the outer surface of above-mentioned sliding sleeve, with aforementioned lubricant oil from the bore area of eccentric part by described eccentric part septated hole and sliding sleeve oil supply hole supply sliding sleeve peripheral part; Simultaneously

On above-mentioned sliding sleeve peripheral part, one orifice part is set for described sliding sleeve oil supply hole, make this orifice part be positioned at that aforementioned piston one side is on pressurized one side on the sliding sleeve peripheral part, be in respect to cause described sliding sleeve for the eccentric rotary of eccentric part and do between the center of this eccentric part one patchhole on the center of rotation of eccentric rotary and the sliding sleeve.

3. hermetic motor compressor as claimed in claim 2, it is characterized in that: the position, aperture of aforementioned sliding sleeve peripheral part upper sliding sleeve oil supply hole is provided in a side of in that part of adjacent area that clings to the sliding tube internal surface of piston to this sliding sleeve peripheral part in the gas compression processes in the described cylinder.

4. as hermetic motor compressor as described in claim 2 or 3, it is characterized in that: described slider oil supply hole is partly or wholly to lead to mutually with aforementioned eccentric part in the angular range of 90 ° to 180 ° of Kong Zaiyue, the lower dead center of supposing this piston this moment at 0 ° and top dead center at 180 °.

5. hermetic motor compressor as claimed in claim 4, be characterised in that: when described slider oil supply hole and eccentric part septated hole are when partly or entirely leading to mutually, the eccentric rotary angle of this eccentric part is to be set in the angular range that is limited when gas pressure that the piston in the described cylinder produces reaches head pressure.

6. as claim 2 or 3 described hermetic motor compressors, it is characterized in that: on described sliding sleeve oil supply hole peripheral part, be provided with the chute that is used for building up lubricant oil in the adjacent area of aforementioned orifice part.

7. hermetic motor compressor as claimed in claim 6 is characterized in that: described chute is extending axially according to aforementioned sliding tube.

8. hermetic motor compressor as claimed in claim 5 is characterized in that: be provided with the chute that is used for building up lubricant oil in the adjacent area of aforementioned orifice part on described sliding sleeve oil supply hole peripheral part.

9. hermetic motor compressor as claimed in claim 8 is characterized in that: described chute is extending axially according to aforementioned sliding tube.