CN1708646A

CN1708646A - Dual capacity compressor

Info

Publication number: CN1708646A
Application number: CNA2003801025966A
Authority: CN
Inventors: 崔喆洛; 姜达洙; 卢铁基; 徐敏荣; 金碁株; 许俊洙
Original assignee: LG Electronics Inc
Current assignee: LG Electronics Inc
Priority date: 2002-10-31
Filing date: 2003-10-31
Publication date: 2005-12-14
Anticipated expiration: 2023-10-31
Also published as: KR100487962B1; CN100402851C; KR20040038376A

Abstract

Dual capacity compressor including a power generating part (20) having a reversible motor (21, 22) and a crank shaft (23) inserted in the motor (21, 23), a compression part (30) having a cylinder (32), a piston (31), and a connecting rod (33), a crank pin (110) in an upper part of the crank shaft (23) eccentric to an axis of the crank shaft, an eccentric sleeve (120) rotatably fitted to the crank pin (110), and the connecting rod (33) respectively, a key member (130) for positive fastening of the eccentric sleeve (120) to the crank pin (110) in all rotation directions of the motor, and an eccentric mass (200) provided to the eccentric sleeve (120) for rotating the eccentric sleeve (120) around the crank pin (110), thereby preventing relative motion between components that sustain the eccentricity, and permitting a smooth motion between the components.

Description

Double-volume compressor

Technical field

The present invention relates to be used for the working fluid such as refrigeration agent is compressed to the compressor of required pressure, and relate in particular to the compressor that a kind of its compression volume changes with sense of rotation.

Background technique

Double-volume compressor is the reciprocal compressor that a kind of its piston stroke and compression volume change along with the sense of rotation of motor and bent axle, and this compressor is to form by means of the eccentric adjusting sleeve that combines with the crank pin of bent axle in rotating mode.Because the compression volume of double-volume compressor can change according to required load, thereby this compressor is widely used in the equipment of the compression that needs working fluid, in the household electric appliance that particularly in refrigeration cycle, turn round, such as refrigerator, so that improve the running efficiency of compressor.U. S. Patent 4236874 discloses a kind of general double-volume compressor, and the present invention does concise and to the point description with reference to this patent to the double-volume compressor of prior art.

Fig. 1 shows the cross section of U. S. Patent 4236874 disclosed double-volume compressors, and Fig. 2 schematically shows the drive manner of this double-volume compressor.

With reference to Fig. 1, double-volume compressor is provided with following key member: piston 7, bent axle 1, crank pin 3, the eccentric hoop 4 that is connected with crank pin 3 in the cylinder 8 with axis 3a of the axis 1a that is eccentric in bent axle 1 and be connected in eccentric hoop 4 and piston 7 between connecting rod 6.Eccentric hoop 4 and connecting rod 6 can relatively rotate with respect to each other, and also can rotate with respect to the axis 3a of crank pin.The district of release 9 is arranged respectively on the surface of contact of crank pin 3 and eccentric hoop 4, and in this release district, be useful on the key member 5 of connecting crank pin 3 and eccentric hoop 4.To the operation of the relevant compression volume of double-volume compressor be described below.As shown in Figure 2, in double-volume compressor, the stroke of piston 7 is by different throw of eccentric is regulated with eccentric hoop 4 residing positions, wherein, larger capacity if desired, just (conventional direction) rotation in a clockwise direction of bent axle 1 so, and if desired than small capacity, bent axle 1 is just with (in the other direction) rotation counterclockwise so.Piston 7 was positioned at the moment of upper dead center (dead point) during Fig. 2 A at length showed and rotates in the clockwise direction, and Fig. 2 B at length show in the clockwise direction rotate in piston 7 be positioned at moment of lower dead centre, at this moment, because throw of eccentric is maximum, thereby piston stroke Lmax also is maximum.Piston 7 was positioned at the moment of lower dead centre during Fig. 2 C showed in the counterclockwise direction and to rotate, and Fig. 2 D show rotate in the counterclockwise direction in piston 7 be positioned at moment of upper dead center, at this moment, because throw of eccentric is minimum, thereby piston stroke Lmin also is minimum.

Yet, in aforementioned drive manner, crank pin 3 and eccentric hoop 4 all are subjected to action of centrifugal force, described centrifugal force respectively by crank pin and eccentric hoop around the rotation of the axis 1a of bent axle and produce, and be applied on the lighting outlet between the axle center 3a of the axle center 1a of bent axle and crank pin respectively and axle center 1a to the lighting outlet between the center of gravity of eccentric hoop 4a.Thereby, different with Fig. 2 B with Fig. 2 A is, in the situation of Fig. 2 C and Fig. 2 D, because two lines of action are not on same straight line, thereby the local torque that on eccentric hoop 4, has produced relative crank pin 3, the sense of rotation identical (counterclockwise) that applies direction and bent axle 1 of this torque, its size is for to the perpendicular distance ' d ' of pin 3 and the product of this eccentric hoop self centrifugal force.Because crank pin 3 and eccentric hoop 4 are the parts that can move relative to each other, therefore moment of rotation causes eccentric hoop 4 relatively rotating on the sense of rotation of bent axle 1, key member 5 is thrown off from crank pin 3 and eccentric hoop 4, and eccentric hoop 4 and key member 5 are moved along sense of rotation shown in the dotted line among Fig. 3.And, as shown in Figure 3, for example, when moving in the clockwise direction, inner cylinder pressure after the compression ' P ' (swelling pressure again of working fluid) promotes eccentric hoop 4 to the sense of rotation of bent axle 1, so that eccentric hoop 4 rotates with respect to crank pin 3 along the sense of rotation of bent axle.Like this, thisly relatively rotate the running that makes compressor and become unstable, thereby can't realize desired compression performance.

In fact, because key member 5 can't keep crank pin 3 and eccentric hoop 4 well, thereby can relatively rotate.No matter when the sense of rotation of bent axle changes, and key member 5 all can rolling in discharging the district, thereby causes the serious friction on the corresponding surface of contact, and this has shortened the operating life of compressor.

Except U. S. Patent 4236874, the double-volume compressor technology that also had a lot of patent disclosures will be done concise and to the point the description to these technology below.

Similarly, U. S. Patent 4479419 discloses a kind of double-volume compressor with crank pin, eccentric cam and key member.Key member is fixed to eccentric cam, and the track in the crank pin moves when the sense of rotation of compressor changes.Yet because key member can not keep crank pin and eccentric cam rigidly, so U. S. Patent 4479419 also has the running astatically that causes by relatively rotating.

U. S. Patent 5951261 discloses a kind of compressor with eccentric part and eccentric cam.This eccentric part has an internal diameter that passes the hole of eccentric part formation, and this eccentric cam has another hole, and the internal diameter in this hole is identical with the internal diameter in the hole that forms in eccentric part one side.In the hole of eccentric part, be provided with pin, and be provided with pressure spring in the hole in eccentric adjusting sleeve.Therefore, when described hole in rotation on time, pin just in action of centrifugal force is moved to the hole of cam, thereby eccentric part and eccentric cam are kept together.Yet, in U. S. Patent 5951261 owing to only be provided with a hole in the eccentric cam, therefore have only when compressor when a specific direction rotates, eccentric part and eccentric cam can keep together.And, be difficult to realize owing to pin passes the accurate motion of these holes from the eccentric part to the eccentric cam, thereby just can not guarantee operating reliability.

Simultaneously, each aforesaid double-volume compressor has all used eccentric part basically, such as eccentric hoop and eccentric cam, and utilizes the throw of eccentric of described eccentric part to change the stroke and the compression volume of piston.Because these eccentric parts and its being oppositely arranged along with the sense of rotation of compressor of parts on every side change, so throw of eccentric changes thereupon.Therefore, change in order to produce an amount of throw of eccentric, before correctly connecting described eccentric part described eccentric part accurately being arranged on also is very important on the desired location.

Summary of the invention

An object of the present invention is to provide a kind of double-volume compressor with different compression volumes, even compressor rotates with any direction, this compressor can both keep a constant throw of eccentric, and this compressor can runs steadily.

As mentioned above, the present inventor understands, between on-stream period, the local centrifugal force of eccentric adjusting sleeve and the external loading by connecting rod etc. has caused the bumpy running of double-volume compressor.Although as long as use eccentric stiffener, these reasons just can't be avoided, the inventor understands, if cooperate rigidly with eccentric adjusting sleeve at on-stream period chien shih crank pin, so just can address this problem.Have the idea of the key member of this connection features for use, revise this key member and relevant parts thereof to prevent relatively rotating between crank pin and the eccentric adjusting sleeve.

And, the stroke distances that is known that throw of eccentric and piston along with eccentric adjusting sleeve and other adjacent component directly or relatively rotate and change.Therefore, the present inventor has also further improved compressor, so that eccentric adjusting sleeve rotates reposefully and accurately be provided with to realize the operating reliability of compressor.

Therefore, the invention provides a kind of double-volume compressor, it comprises the power generating part branch, and described power generating part branch comprises the reversible motor and embeds the bent axle of this motor; Compression member, described compression member have the piston and the connecting rod that is connected with this piston in cylinder, the cylinder; Crank pin, this crank pin is positioned at bent axle top, and is eccentric in the axis of bent axle; Eccentric adjusting sleeve, its inner peripheral surface matches with the outer peripheral surface of crank pin in rotating mode, and its outer peripheral surface matches with an end of connecting rod in rotating mode; Key member, it is used on all sense of rotation of motor eccentric adjusting sleeve being rigidly secured to crank pin; And eccentric mass, this eccentric mass is arranged on the eccentric adjusting sleeve, is used to make eccentric adjusting sleeve to rotate around crank pin.

Key member keeps eccentric adjusting sleeve at a plurality of somes place, and more preferably, key member keeps eccentric adjusting sleeve on 2 of the center line setting on any direction between with respect to on-stream period.

To be described in more detail these members below.

Crank pin comprises a pair of key member mating part that forms toward each other.

Crank pin also comprises at least one first oil supply hole, and this first oil supply hole is used for fuel feeding between eccentric adjusting sleeve and crank pin, and this first oil supply hole is formed in the bent axle, so that be connected with the oil circuit that is used for to each moving member fuel feeding of compressor.Preferably, described crank pin has a pair of first oil supply hole positioned opposite to each other in crank pin.

Eccentric adjusting sleeve comprises a rail portion that is formed along a circumference thereof, and it is used to make eccentric adjusting sleeve self to rotate with respect to the projection of key member; With a restricted part that forms with respect to rail portion, it is used for the rotation of the projection of limit key parts.The rail portion of described eccentric adjusting sleeve is the part of cutting away of along the circumferential direction cutting apart from top certain depth place, or along the circumferential direction extends the through hole of a length apart from top certain depth place.

Preferably, the step that is provided with between rail portion and restricted part is parallel to the lighting outlet that connects bent axle axle center and crank pin axle center, and more preferably, described step and the spacing size of the lighting outlet in the axle center of axle center that is connected bent axle and crank pin equal half of key member thickness.

Eccentric adjusting sleeve also comprises second oil supply hole that the first interior oil supply hole of at least one and crank pin is connected.Described eccentric adjusting sleeve also is included on its outer peripheral surface the oil pocket that forms around second oil supply hole, with on its outer peripheral surface from the vertical oil groove that stretches out of second oil supply hole.

Key member comprises first projection, and it engages from length of crank pin protrusion and with the step of eccentric adjusting sleeve; First retainer, it is used to limit the protrusion length of first projection; With second projection, it protrudes on the direction opposite with the protrusion direction of first projection and engages with the opposite side step of eccentric adjusting sleeve in rotation.

Preferably, key member also comprises an elastic member, and it is used to be embedded on second projection and supports first projection, so that regardless of the operating condition of compressor, first projection all protrudes constantly.Preferably, key member also comprises second retainer, and its direction according to centrifugal force limits the length that second projection protrudes from crank pin.

Eccentric mass rotating eccentric sleeve tube is so that make this eccentric mass be kept by the part of key member, and produces a moment of rotation that is used for the rotating eccentric sleeve tube under action of centrifugal force.

Preferably, eccentric mass make eccentric adjusting sleeve with eccentric adjusting sleeve on the identical direction of the relative friction forces direction that produced rotate, and along the direction of the direction of rotation of bent axle.Eccentric mass is set to the relative lighter part of weight of eccentric adjusting sleeve, and preferred, is arranged to the rail portion near eccentric adjusting sleeve.

Eccentric mass is a plate-like piece on the outer peripheral surface that is arranged on eccentric adjusting sleeve top.Eccentric mass and eccentric adjusting sleeve form parts, perhaps are independent of eccentric adjusting sleeve and form, and be fixed in eccentric adjusting sleeve.

Thereby double-volume compressor of the present invention has prevented relatively rotating between crank pin and the eccentric adjusting sleeve, makes the compressor runs steadily and has improved the running efficiency of compressor.Eccentric adjusting sleeve accurately is provided with, and so that desired throw of eccentric to be provided, and guarantees the operating reliability of compressor simultaneously.

Description of drawings

Provide accompanying drawing so that further understand the present invention, accompanying drawing shows some embodiments of the present invention and is used from explanation principle of the present invention with specification one.In the accompanying drawings:

Fig. 1 is the sectional view of existing double-volume compressor;

The drive manner of the schematically illustrated existing double-volume compressor shown in Figure 1 of Fig. 2;

Fig. 3 is the sectional view of some critical components of existing double-volume compressor, relatively rotating between its schematically illustrated crank pin and the eccentric adjusting sleeve;

Fig. 4 is the sectional view of double-volume compressor according to a preferred embodiment of the present invention;

Fig. 5 A is the side view of the partial cross section of double-volume compressor according to a first advantageous embodiment of the invention;

Fig. 5 B is the planimetric map of the partial cross section of double-volume compressor according to a first advantageous embodiment of the invention;

Fig. 6 A is the perspective view of the partial cross section of double-volume compressor according to a first advantageous embodiment of the invention;

Fig. 6 B be from crank pin shown in Fig. 6 A improve and the perspective view of crank pin;

Fig. 7 A is the perspective view of eccentric adjusting sleeve of the present invention;

Fig. 7 B～Fig. 7 E shows the various variations of eccentric adjusting sleeve of the present invention respectively;

Fig. 8 is the perspective view of key member of the present invention;

Fig. 9 is the planimetric map of a kind of variation of the key member that is coupled to crank pin shown in Figure 8;

Figure 10 A and Figure 10 B are the perspective views with key member of dismountable first retainer;

Figure 11 A～Figure 11 C is the planimetric map of various variations with key member of second retainer;

Figure 12 A and Figure 12 B are planimetric maps, and every figure has shown the relation between the power that eccentric mass of the present invention and eccentric mass produce;

Figure 13 A and Figure 13 B are planimetric maps, and every figure has shown the drive manner that double-volume compressor of the present invention clockwise rotates; With

Figure 14 A and Figure 14 B are planimetric maps, and every figure has shown the drive manner that double-volume compressor of the present invention rotates counterclockwise.

Embodiment

Now will be at length with reference to the preferred embodiments of the present invention, some examples of the embodiment of the invention have been shown in the accompanying drawing.When describing embodiments of the invention, identical parts will be represented with identical title and reference character, and omit being repeated in this description them.The overall structure of double-volume compressor of the present invention is described with reference to Fig. 4.

With reference to Fig. 4, double-volume compressor of the present invention comprises: power generating part divides 20, and it is positioned at the compressor bottom, is used to produce and transmit required power; Compression member 30, it is positioned at power generating part and divides 20 tops, comes compression working fluid to use power.And except these common segments, double-volume compressor also comprises the stroke alteration part 40 that is connected between power section 20 and the compression member 30, and it is used for changing the compression volume of compression member 30 between on-stream period.Simultaneously, described compressor also comprises shell, and this shell is closed power section 20 and compression member 30, to prevent freezing medium leakage; And framework 12, this framework flexibly is bearing on a plurality of support members (being spring) that are fixed in described enclosure.Described compressor also comprises refrigerant inlet 13 and refrigerant outlet 15, and they are installed to the inside of shell and are connected with the inside of shell.

Power generating part below the framework 12 divides 20 to comprise a motor with stator 21 and rotor 22, and it produces rotating force by external power supply; With a bent axle 23.Motor is reversible.Bent axle 23 has the bottom that embeds rotor 22, and it is used to transmit power; Also have oilhole and oil groove, the lubricant oil that they are used for remaining on described bottom supplies to driver part.

Compression member 30 is installed in and is positioned on the framework 12 that power generating part divides 20 tops, and it comprises the extraction valve and the escape cock that are used for the mechanical driving member of compressed refrigerant and are used for the auxiliary drive parts.Except the cylinder 32 that has in fact formed a compression volume, driver part has in 32 li pistons reciprocating 31 of cylinder; With the connecting rod 33 that reciprocating power is sent to piston 31.Described valve receives and refrigeration agent is discharged to this cylinder from the cylinder 32 that links to each other with cylinder cowl 35 with cylinder head 34.

Below will describe the stroke alteration part 40 of double-volume compressor of the present invention in detail, and omit power generating part and divided and compression member explanation same as the prior art.

With reference to Fig. 5 A, in general, described stroke alteration part 40 comprises that being positioned at bent axle pushes up the crank pin 110 of going up and being eccentric in bent axle; Be engaged in the outer peripheral surface of crank pin 110 and the eccentric adjusting sleeve 120 between the connecting rod 33 in rotating mode; With the key member 130 that is engaged in 110 li of crank pins.Key member 130 keeps crank pin 110 and eccentric adjusting sleeve 120 relative position each other during compressor operation.Eccentric adjusting sleeve 120 is arranged in the described stroke alteration part 40 and in the stroke alteration part and rotates, so that its effective throw of eccentric is along with the sense of rotation variation (normal direction or opposite direction) of motor.In order to keep this altered effective throw of eccentric, key member 130 is maintained on the eccentric adjusting sleeve 120.Thereby if the sense of rotation of motor is changed by stroke alteration part 40, the running length of connecting rod and piston stroke can change because of the change of effective throw of eccentric so basically, and in view of the above, compression volume is also along with sense of rotation changes.Stroke alteration part 40 of the present invention is described below with reference to accompanying drawings in more detail.

Fig. 5 A and Fig. 5 B are respectively the side view and the planimetric maps of double-volume compressor of the present invention, wherein reach for convenience of explanation clearly to explain, its member shows with the partial sectional view of assembling condition.Fig. 6 A～Figure 12 shows these members individually.

With reference to Fig. 5 A, described crank pin 110 is a part hollow, so that in a movable manner key member 130 is engaged in the hollow space.This crank pin 110 also has a pair of key member mating part 111 that forms toward each other; Be positioned at the oil supply hole 113 of bottom with oil circuit 112 and at least one.

With reference to Fig. 5 A and Fig. 5 B,

mating part

111a and 111b are formed in the tubular portion of hollow, so that described mating part is arranged on the vertical plane of the axis 111a of the axis 23a that comprises bent axle and crank pin.Thereby the described key member 130 in this

mating part

111a and 111b has been subjected to being applied to along described key member 130 influence of the vertical centrifugal force F on the lighting outlet between axis 23a and the axis 110a.By the effect of centrifugal force F, this key member 130 can move under the guiding of described mating part 111a and 111b.As shown in Figure 6A, in fact this

mating part

111a and 111b can be set to a through hole.The mating part 111 of described through hole can prevent that key member 130 from coming off between on-stream period.Preferably, shown in Fig. 6 B, be easy to cooperate with crank pin 110 for making key member 130, at least one among this mating part 111a and the 111b can be the slit that reaches a position from the top of crank pin 110 walls.More preferably, has a part 111c at an end of this mating part, so that key member 130 stably cooperates.

With reference to Fig. 5 A, described oil circuit 112 both was connected with the oil groove of bent axle 23 outer surfaces, was connected with first oil supply hole 113 again.This first oil supply hole 113 can be the through hole on crank pin 110 arbitrary positions.Yet, if described oil supply hole 113 is parallel to mating

part

111a and 111b forms, promptly forming along the lighting outlet that connects described

mating part

111a and 111b, this oil supply hole 113 will reduce the intensity of crank pin significantly so.Therefore, shown in Fig. 7 C and Fig. 7 D, this oil supply hole 113 is formed on the direction perpendicular to the lighting outlet (being the lighting outlet between axis 23a shown in Fig. 5 B and the 110a) that connects described mating part 111a and 111b.And preferably, a pair of first oil supply hole 113 forms relative to one another, is used for providing lubricant oil equably between crank pin 110 and eccentric adjusting sleeve 120.The lubricant oil of compressor bottom at first passes oil groove and oil circuit 112, and from the ejection of the upper end of oil circuit 112, so that between the surface of contact of member, providing lubricant oil between on-stream period, to prevent the member wearing and tearing and member turned round reposefully, and lubricant oil also can be directly supplies to gap between crank pin 110 and the eccentric adjusting sleeve 120 by oil supply hole 113 from oil circuit 112.Preferably, described crank pin 110 is formed on the position that is higher than eccentric adjusting sleeve 120, to spray lubricant oil from eminence equably to member.

Basically, described eccentric adjusting sleeve 120 has inner peripheral surface and outer peripheral surface, and this inner peripheral surface is connected with the outer peripheral surface of rotating mode with crank pin 110, and this outer peripheral surface is connected with an end of connecting rod 33 in rotating mode.More specifically, shown in Fig. 7 A, described eccentric adjusting sleeve 120 comprises the rail portion 121 that is formed along a circumference thereof and is used to limit the restricted part 122 of the track of rail portion 121.Two

step

123a and 123b are arranged between described rail portion 121 and described restricted part 122.Shown in Fig. 5 A, because at least a portion of key member 130 is protruded, so that be maintained on the eccentric adjusting sleeve 120 between not on-stream period of compressor, thereby described rail portion 121 can make described eccentric adjusting sleeve self rotate with respect to key member.That is to say that described eccentric adjusting sleeve 120 can be formed with therein in the scope of rail portion and rotate around crank pin 110.Opposite with rail portion 121, stop and on-stream period between, restricted part 122 restriction described eccentric adjusting sleeves self are with the rotation of key member 130.In fact, described key member 130 is maintained on step 123a and the 123b.

In described eccentric adjusting sleeve 120, described rail portion 121 in fact can be the part of cutting away of along the circumferential direction cutting apart from a degree of depth place on eccentric adjusting sleeve 120 tops.Shown in Fig. 5 B and Fig. 7 B, the lighting outlet that

step

123a and 123b are parallel between the axis 110a of the axis 23a of bent axle and crank pin forms.That is to say, described

step

123a and 123b in fact are parallel to the maximum ga(u)ge of eccentric adjusting sleeve and the lighting outlet setting between the minimum thickness, so that described step has different width, and during compressor operation, this lighting outlet is on the lighting outlet between axis 23a and the axis 110a.That is to say that described

step

123a and 123b are positioned on the lighting outlet of lighting outlet of parallel to the axis 23a and axis 110a at one time.Thereby, be arranged on same the key member 130 on the lighting outlet and can be maintained on described two step 123a and the 123b, so that described

step

123a and 123b in fact form the public surface of contact to key member 130.Preferably, described

step

123a and 123b and lighting outlet between axis 23a and the axis 110a separate half the distance of size for described key member 130 thickness ' t '.Therefore, key member 130 can by more stable, be maintained more precisely on described step 123a and the 123b.On the other hand, described

step

123a and 123b can form has the inclined-plane respectively, each inclined-plane all and axle 23a and the lighting outlet of axle between the 110a at an angle.More particularly,

step

123c and 123d can be along the radially lighting outlet settings from the axle 110a of crank pin, and this lighting outlet is the angle θ that tilts of the lighting outlet between the 110a with respect to axle 23a and axle.And

step

123e and 123f can be to the described restricted part angles that tilts, and described restricted part is centrally located in a point of intersection with the inner peripheral surface of crank pin 110.Even in above-mentioned situation, described

step

123c, 123d, 123e and 123f also have the public point of contact with this key member 130 so that these they engage each other.And described rail portion 121 not only can be the part of cutting away shown in Fig. 7 A, also can be along the circumferential direction to extend the through hole of a length at certain depth place, distance eccentric adjusting sleeve 120 top shown in Fig. 7 E.Rail portion 121 with described through hole keeps this key member 130, so that this key member can not break away from from Vertical direction.

In addition, with reference to Fig. 7 C and Fig. 7 D, described eccentric adjusting sleeve 120 can also be included in second oil supply hole 124 that forms on the height.This second oil supply hole 124 forms when compressor operation with first oil supply hole 113 in the crank pin 110 and is connected.More specifically, when compressor operation of the present invention, described key member 130 continues to keep described eccentric adjusting sleeve 120.Therefore, as shown in the figure, basically preferably, when key member 130 kept eccentric adjusting sleeve 120, described second oil supply hole 124 was connected with first oil supply hole 113.And, as previously mentioned because first oil supply hole 113 is perpendicular to key member 130, therefore require this second oil supply hole 124 also perpendicular to key member 130 contacted step 123a and 123b.And shown in Fig. 7 C, when the sense of rotation of bent axle changed, eccentric adjusting sleeve 120 all can relatively be provided with key member 130, to change the throw of eccentric of eccentric adjusting sleeve 120.Therefore, relative another one second oil supply hole of second oil supply hole 124 that eccentric adjusting sleeve 120 is had be connected with first oil supply hole 113 is very useful.That is, eccentric adjusting sleeve 120 becomes and has a pair of second oil supply hole 124 respect to one another.Like this, regardless of the sense of rotation during the compressor operation, any one in two second oil supply holes 124 all is connected with first oil supply hole.According to the sense of rotation of compressor, second oil supply hole optionally keeps being connected with first oil supply hole.Thereby between on-stream period, lubricant oil can be continuously fed with the gap between eccentric adjusting sleeve 120 and the connecting rod 33.In addition, the oil pocket 124a with certain depth is arranged on around second oil supply hole, and it is used to form a spare space, distributing the lubricant oil around second oil supply hole 124, thereby is convenient to supplying lubricating oil between eccentric adjusting sleeve 120 and connecting rod 33.And, be provided with the oil groove 124b that extends in vertical direction along the outer peripheral surface of eccentric adjusting sleeve 120, so that be connected, so that lubricant oil arrives the top and the bottom of eccentric adjusting sleeve 120 outer peripheral surfaces from second oil supply hole 124 along oil groove 124b with second oil supply hole 124.In view of the above, lubricant oil can be fed between eccentric adjusting sleeve 120 and the connecting rod 33 equably.

Refer again to Fig. 7 A, preferably, described step 123a between described rail portion 121 and the described restricted

part

122 and 123b handle through fillet.More specifically, as shown in the figure, between 121 and step 123a of rail portion, a fillet part 125 is arranged.When key member 130 was maintained at eccentric adjusting sleeve 120, key member 130 was supported on the fillet part 125.The curved surface of this fillet part 125 forms to such an extent that make: fillet part 125 is contacted in big as far as possible zone with key member 130.In view of the above, utilize fillet part 125, key member 130 can remain on the eccentric adjusting sleeve 120 with being stabilized.And because fillet part 125, key member 130 can not contact with eccentric adjusting sleeve 120 by aspectant mode by point-to-point.And fillet part 125 has in fact improved the intensity of described step 123a and 123b.Thereby even key member 130 contacts during compressor operation repeatedly and constantly with eccentric adjusting sleeve 120, described key member 130 and described eccentric adjusting sleeve 120 can the stress that be caused do not concentrated and fatigue causes fracture owing to frequently contact yet.

Fig. 5 A, Fig. 5 B or Fig. 8 show in detail key member 130.As shown in the figure, basically this key member 130 has first projection 131 and second projection 132, even described first projection does not all protrude a length from crank pin 110 when compressor turns round, described second projection protrudes a length from crank pin 110 when compressor operation.Described key member 130 also has first retainer 133, and it is used to limit the protrusion length of first projection 131.This key member 130 has and above-mentioned part elastic member 140 together, its be used for compressor stop or on-stream period between the position of control key parts 130.In the present invention, when key member 130 because action of centrifugal force and when mobile, key member 130 is keeping eccentric adjusting sleeve 120.Especially, as previously mentioned, during compressor operation, second projection 132 is owing to its protrusion keeps eccentric adjusting sleeve 120.For second projection is protruded by the centrifugal force that produces during compressor operation, second projection 132 need be arranged on the direction identical with the direction of centrifugal force.Thereby as shown in the figure, when second projection 132 was located opposite from the radius outside of bent axle 23 and crank pin 110, first projection 131 was positioned at the inner sides of radius of bent axle 23 and crank pin 110.That is to say that in fact described second projection 132 is arranged in the crank pin 110 that the axis 23a with bent axle separates, to be subjected to bigger centrifugal force, and relative therewith, described first projection 131 is arranged near center 22a.And, maintain described eccentric adjusting sleeve 120 when the compressor operation simultaneously in order to make described first projection 131 and described second projection 132, preferred, this key member 130 has the length bigger than the external diameter of crank pin 110.

More specifically, with reference to Fig. 5 A, regardless of the working state of compressor (stop or turning round), first projection 131 all protrudes and engages with described

step

123a and 123b from crank pin 110, even and also keep the state that engages during compressor operation.For this reason, elastic member 140 is matched with on second projection 132, and flexibly supports first retainer 133 with the inwall of crank pin 110.The protrusion length of described first projection is owing to the inwall of first retainer, the 133 obstruction crank pins 110 of described key member 130 is restricted.In order to make more runs steadily of compressor, preferably, the length of first projection is at least half of minimum width of described step 123a and 123b.And as previously mentioned, because first projection 131 is positioned at bent axle 23 and crank pin 110 inboard radially, therefore first projection 131 is constantly towards radially inner side, just the axis 23a of bent axle protrudes.Thereby described key member 130 always is maintained at least a portion of eccentric adjusting sleeve 120, and described eccentric adjusting sleeve relatively is positioned the radially inner side of bent axle 23.

Described second projection protrudes along the direction opposite with the protrusion direction of described first projection, so that engage with another step during compressor operation.In view of the above, first projection 131 of this key member 130 and second projection 132 engage with eccentric adjusting sleeve 120 simultaneously.Along with the rotational velocity of bent axle 23 becomes more and more faster, progressively increase to overcome the elastic force of elastic member 140 along the centrifugal force of key member 130.In view of the above, described second projection moves and protrusion along the direction (i.e. lighting outlet direction between axle 23a and the axle 110a) of centrifugal force.In this example, described eccentric adjusting sleeve 120 rotates around crank pin 110, changes throw of eccentric when changing with the sense of rotation at compressor.Thereby in order not influence the rotation of eccentric adjusting sleeve 120, the length that needs second projection 132 to be had can not protrude into outside the excircle of crank pin 110 its end when compressor turns round.

According to the sense of rotation of bent axle, described first and

second projections

131 and 132 alternately engage with described step 123a and 123b.Since described key member 130 is arranged on the lighting outlet between axis 23a and the axis 110a or be parallel on the straight line of this lighting outlet at least, therefore, if the thickness of described first and second projections ' t1 ' is different with ' t2 ', key member 130 is also different with 123b contact position separately with described step 132a so.Therefore, accurately engage with

step

123a and 123b, require first and

second projections

131 and 132 to have identical thickness ' t1 ' and ' t2 ' in order to make key member.Although the cross section of key member 130 is circular in description of the invention and accompanying drawing, the cross section of Any shape such as square or hexagonal, as long as they can make key member engage with described

step

123a and 123b, just can be used.

With reference to Fig. 9, the surface of contact 133a of described first retainer 133 can have the shape that matches with the inner peripheral surface of crank pin 110.In view of the above, this key member 130 can accurately engage with crank pin 110, and can make running more steady (promptly increase centrifugal force make second projection, 132 easier protrusions) because of the increase of weight.Preferably, described first retainer 133 can also comprise groove 133b, and it is used for stably holding elastic member 140.This surface of contact 133a and groove 133b in fact help the steady running of key member 130.Simultaneously, described first retainer 133 can form parts with key member 130, perhaps is coupled to individually on the key member 130.The example of first retainer 133 of this separate type is shown in Figure 10 A and Figure 10 B.

With reference to Figure 10 A, first retainer 133 can comprise the projection 133a that radially extends internally.In view of the above, when locational circumferential grooves of projection 133a sunk key parts 130, first retainer 133 just is engaged on the key member 130.Perhaps, shown in Figure 10 B, first retainer 133 is a simple annular element, can be fastened on the position of key member 130 by secure component.Even when two key

member mating part

111a and 111b were through hole, the retainer 133 of these independent types also can make key member 130 be coupled to crank pin 110.More specifically, the inside by retainer 133 being placed on crank pin 110 and insert by key member 130 being passed through hole, retainer 133 engages with key member 130.

Simultaneously, as previously mentioned, in key member 130, during running well, the protrusion length of second projection 132 in key member 130 can regulate by the elastic force that elastic member 140 produces.Yet at compressor start constantly, the moment of bent axle 23 and crank pin 110 sharply quickens to cause sizable moment centrifugal force to be applied on the key member 130.Very possible is that under centrifugal action, second projection protrudes excessively and is enough to cause first projection 131 to break away from from mating part 111.Therefore, preferably, key member 130 also comprises second retainer 134, and its protrusion length that is used to limit second projection 133 exceeds crank pin 110 under centrifugal action.

With reference to Figure 11 A, second retainer 134 can be the pipe part 134a of hollow, and on the length direction of second projection 132, this pipe part is engaged on described second projection in a movable manner.In this example, elastic member 140 is installed between the second retainer 134a and second projection 132.When key member 130 was mobile on the direction of centrifugal force, the second retainer 134a both contacted with first retainer 133, and the inwall with crank pin 110 contacts again, thereby had prevented that second projection, 133 protrusions from exceeding a length.Shown in Figure 11 B, second retainer 134 can be extension 134b, and its thickness is at least greater than the thickness of second projection 133.That is to say that the second retainer 134b shown in Figure 11 B is actually the longitudinal extension of first retainer 133.In this case, elastic member 140 is engaged on the excircle of the second retainer 134b.Perhaps, shown in Figure 11 C, second retainer 134 can make the part 134c that radially extends to desired thickness of second projection, and in fact it have and first retainer, 133 similar shapes.In this case, elastic member 140 is engaged between the inner peripheral surface and the second retainer 134c of crank pin 110.Be similar to the various variations with reference to Figure 10 A and described first retainer 133 of Figure 10 B, the second retainer 134b and 134c can be the separate parts that is individually fixed on the key member 130.

Say that briefly the length of key member 130 is than big at least one the predetermined quantity of the diameter of crank pin basically, and described key member is installed in the crank pin in a movable manner.Even under the situation that compressor does not turn round, at least a portion of described key member 130 (i.e. first projection) is protruded from crank pin, and its another part (i.e. second projection) protrudes from crank pin owing to centrifugal force when compressor operation.That is to say that described key member 130 is remained at least a portion of eccentric adjusting sleeve 120 constantly, and remained in addition on the eccentric adjusting sleeve 120 during the compressor operation.Thereby key member 130 contacts with eccentric adjusting sleeve 120 at a plurality of somes place, and more particularly, and key member 130 in fact contacts with opposite end with respect to the eccentric adjusting sleeve 120 of the center line setting of same time any direction between on-stream period.At last, key member 130 engages eccentric adjusting sleeve 120 rigidly with crank pin 110 on any sense of rotation of motor, thereby has prevented eccentric adjusting sleeve 120 and crank pin 110 relatively moving each other.

Simultaneously, if the sense of rotation of bent axle 23 changes, eccentric adjusting sleeve 120 rotates around crank pin 110 so, to change throw of eccentric, piston stroke and compression volume.Shown in Figure 12 B, when bent axle 23 begins to rotate, the crank pin 110 that rotates with bent axle 23 and with crank pin 110 relative static connecting rods 33 between produce frictional force ' f ', i.e. the opposite direction (seeing that from the top accompanying drawing is a clockwise direction) of sense of rotation (seeing that from the top accompanying drawing is a counter clockwise direction) in eccentric adjusting sleeve 120 upper edges with crankshaft.Usually, the rotation of eccentric adjusting sleeve 120 is produced by this relative friction forces ' f ', up to step 123a of eccentric adjusting sleeve or 123b with till first projection 131 of key member contacts.Yet this relative friction forces ' f ' will overcome frictional force between eccentric adjusting sleeve 120 and the connecting rod 33 and the frictional force between eccentric adjusting sleeve 120 and the crank pin 110, and is applied on the eccentric adjusting sleeve 120.Thus, decide on working order, this relative rotatory force may deficiency so that eccentric adjusting sleeve 120 rotate reposefully.For example, if the lubricant oil between crank pin 110, eccentric adjusting sleeve 120 and the connecting rod 33 is under-supply, the frictional force between the parts 110,120 and 33 will increase so, so that this relative friction forces ' f ' can not make eccentric adjusting sleeve 120 rotate.Perhaps, if unusual external force is applied on the eccentric adjusting sleeve 120 by connecting rod 33, this relative friction forces ' f ' also is not enough to overcome external force and eccentric adjusting sleeve 120 is rotated so.

In above-mentioned situation, eccentric adjusting sleeve 120 can not be arranged on the accurate position, producing the change of a required throw of eccentric, thereby can't obtain desired two different compression volumes.That is to say that eccentric adjusting sleeve 120 can't rotate fully so that among step 123a and the 123b is maintained on first projection 131, this makes second projection 132 can't keep another step, thereby can't keep eccentric adjusting sleeve 120 rigidly.Therefore, in the present invention, eccentric adjusting sleeve 120 is provided with eccentric mass 200, so that eccentric adjusting sleeve 120 rotates reposefully.

With reference to Figure 12 A, eccentric mass 200 is eccentric in eccentric adjusting sleeve 120, and therefore has eccentric center of gravity G.When bent axle 23 began to rotate, centrifugal force ' C ' was applied on the center of gravity ' G ' along the axle center 23a of bent axle and the lighting outlet between the center of gravity ' G '.Because obviously away from the axle center 23a of bent axle, described axle center is the center of rotation of eccentric adjusting sleeve 120 to center of gravity ' G ', so arm of force length ' d ' straight line of drawing perpendicular to the axis 23a from bent axle.Therefore, centrifugal force ' C ' is owing to the arm of force ' d ' has produced a partial rotational moment ' M ', so that described eccentric adjusting sleeve 120 rotates along clockwise direction.The moment of rotation ' M ' that described eccentric mass 200 produces is big fully, even under any external disturbance, this moment all is enough to make eccentric adjusting sleeve 120 stably to rotate around crank pin 110.Thereby described eccentric adjusting sleeve 120 keeps rotating always, is maintained on the key member 130, or rather, be maintained on first projection 131, and described eccentric adjusting sleeve has produced required accurate throw of eccentric, so that compression volume changes.Optionally, as shown in phantom in FIG., described eccentric mass 200 can be arranged on the eccentric adjusting sleeve 120 symmetrically.On in this case, when bent axle 23 begins to rotate, the centrifugal force ' C ' ' just be applied to center of gravity ' G ' ', and owing to the arm of force ' d ' ' produced moment of rotation ' M ' '.Similarly, moment of rotation ' M ' ' eccentric adjusting sleeve 120 is stably rotated, so that eccentric adjusting sleeve 120 is maintained on first projection 131 of key member.Thereby, even eccentric mass 200 is arranged on the arbitrary portion of eccentric adjusting sleeve 120, described eccentric mass 200 moment that all can rotate, and described eccentric adjusting sleeve 120 is rotated.

As mentioned above, with reference to Figure 12 B, in the rotation of bent axle 23, frictional force ' f ' is applied on the eccentric adjusting sleeve 120.If the direction of frictional force ' f ' is opposite with the direction of moment of rotation ' M ', frictional force ' f ' will weaken moment of rotation ' M ' so, thereby influences the rotation of eccentric adjusting sleeve.Therefore, preferably, eccentric mass 200 is arranged on the eccentric adjusting sleeve 120, so that eccentric mass 200 produces and the direction moment ' M ' in the same way of frictional force ' f '.That is to say that in a preferred embodiment of the invention, eccentric mass 200 is configured such that eccentric adjusting sleeve 120 rotates with the direction identical with the direction of frictional force ' f '.And, because the direction of rotation that applies direction and bent axle 23 of frictional force ' f ', thereby, preferably, eccentric mass 200 make eccentric adjusting sleeve 120 with the direction rotation of the direction of rotation of bent axle 23.

And as shown in the figure, eccentric adjusting sleeve 120 has eccentric center of gravity ' Gs ', and this is not only because sleeve self in uneven thickness, also since rail portion 121 by cutting away formation.That is, center of gravity ' Gs ' is positioned on the heavier restricted part 122.Thereby in bent axle 23 rotation processes, centrifugal force ' Cs ' is applied on the lighting outlet between the axle 23a of the center of gravity ' Gs ' of eccentric adjusting sleeve 12 and bent axle.Because the off-centre of center of gravity ' Gs ', thereby centrifugal force ' C ' is by the perpendicular distance between the 110a of described lighting outlet and crank pin 110, and promptly arm of force length ' ds ' has produced a moment of rotation ' Ms '.Moment of rotation ' Ms ' always is applied on the direction identical with the sense of rotation of bent axle 23.That is, shown in Figure 12 B, in bent axle 23 rotated counterclockwise, moment of rotation ' Ms ' produced on eccentric adjusting sleeve 120 with counter clockwise direction by center of gravity ' Gs '.And although not shown, in bent axle 23 clockwise rotated, moment of rotation ' Ms ' then produced in a clockwise direction.As described, frictional force ' f ' makes eccentric adjusting sleeve 120 to rotate with the direction of the direction of rotation of compressor, till eccentric adjusting sleeve 120 is kept by first projection 131.Yet moment of rotation Ms trends towards making eccentric adjusting sleeve 120 to rotate with the sense of rotation of compressor.When even the moment ' M ' that produces when eccentric mass 200 is applied on the eccentric adjusting sleeve 120, moment ' Ms ' also makes eccentric adjusting sleeve with the direction of the direction of rotation that produces with eccentric mass 200 slightly, rotate off and on.Thereby the fine rotation of eccentric adjusting sleeve 120 has influenced the protrusion and the maintenance of second projection 132 that is used for fully keeping eccentric adjusting sleeve 120.Because this unsettled action is to be caused by the inequality on eccentric adjusting sleeve 120 weight, so preferred, eccentric mass 200 is arranged on that lighter part of eccentric adjusting sleeve 120 weight.Promptly shown in Figure 12 B, eccentric mass 200 is set near rail portion 121.This eccentric mass 200 has been transferred to the center of gravity ' Gs ' of eccentric adjusting sleeve 120 on the position of axle 110a of close crank pin, and the arm lengths of exerting all one's strength ' ds ' minimum is to eliminate the influence of the moment of rotation ' Ms ' on the eccentric adjusting sleeve 120.In view of the above, prevented the fine rotation of eccentric adjusting sleeve 120, thereby made second projection 132 more stably keep eccentric adjusting sleeve 120 by it self centrifugal force ' F '.And, as shown in the figure, the eccentric mass 200 on the rail portion 121 on the direction identical with the direction of frictional force ' f ', promptly with the direction of the direction of rotation of bent axle 23 on, produced moment of rotation, so that eccentric adjusting sleeve 120 rotates.Thereby most preferably, the eccentric mass 200 on the rail portion 121 is in an accurate position and eccentric adjusting sleeve 120 is remained on this exact position in eccentric adjusting sleeve 120 rotates.

As long as eccentric mass 200 can be by the action of centrifugal force moment that rotates, eccentric mass 200 just can be arranged on the arbitrary position.For example, heavy weight eccentric mass can be arranged in the hole of eccentric adjusting sleeve 120.Yet the eccentric adjusting sleeve of this structure needs a bigger eccentric adjusting sleeve 120, thereby has increased the size of other parts that engage with eccentric adjusting sleeve 120.Therefore, preferably, shown in Fig. 5 A, eccentric mass 200 is arranged on the outer peripheral surface of eccentric adjusting sleeve 120, and it is made by sheet member, to avoid influencing other adjacent parts.When eccentric mass 200 is during from part that the outer peripheral surface of eccentric adjusting sleeve 120 extends, eccentric mass 200 is set to a part of eccentric adjusting sleeve 120.Perhaps, eccentric mass 200 can be independent of the outer peripheral surface that eccentric adjusting sleeve 120 was provided with and was fixed to eccentric adjusting sleeve 120.Under the situation that does not influence connecting rod 33, eccentric mass 200 can be arranged on the top of eccentric adjusting sleeve 120 or below.Yet shown in Fig. 5 A, the eccentric mass 200 above the eccentric adjusting sleeve 120 can prevent that connecting rod 33 upwards breaks away from from eccentric adjusting sleeve 120.

The drive manner of double-volume compressor is described with reference to the accompanying drawings.Figure 13 A and 13B are planimetric maps, and every figure shows the drive manner of double-volume compressor of the present invention when it clockwise rotates; And Figure 14 A and 14B are planimetric maps, and every figure shows the drive manner of double-volume compressor of the present invention when it rotates counterclockwise.

Figure 13 A is a planimetric map, show bent axle 23 beginning with normal, be the relative position of clockwise direction key member 130 and eccentric adjusting sleeve 120 when rotating.As mentioned above, under the effect of elastic force, first projection 131 always radially inwardly protrudes into outside the crank pin 110 towards crank pin 110.Under the state that first projection 131 protrudes, when bent axle 23 beginnings were rotated in a clockwise direction, crank pin 110, eccentric adjusting sleeve 120 and key member 130 began the rotational around bent axle.In rotation, between crank pin 110 and connecting rod 33, relative friction forces ' f ' is created on the direction with the direction of rotation of bent axle.Because the effect of frictional force ' f ', eccentric adjusting sleeve 120 is counterclockwise to rotate around crank pin 110.Meanwhile, the effect by going up the centrifugal force ' C ' that produces in the center of gravity ' G ' of eccentric mass 200 has produced moment of rotation ' M ', and this moment of rotation rotates eccentric adjusting sleeve 120 with frictional force ' f ' in the counterclockwise direction more reposefully.In view of the above, the step 123b on the eccentric adjusting sleeve 120 thin sides is remained on first projection 131 of protrusion rigidly.In case bent axle 23 rotates, because frictional force ' f ' and moment of rotation ' M ' are to continue to produce, therefore the maintenance between first projection 131 and the step 123 also continues.Shown in Figure 13 B, if rotational velocity reaches certain level, under the effect of centrifugal force ' F ', key member 130 can move along the lighting outlet between axis 23a and the axis 110a.In view of the above, when keeping in touch between first projection 131 and step 123a, second projection 132 also engages with the step 123b of a thicker side.The multiple spot contact of this while makes key member 130 engage rigidly with eccentric adjusting sleeve 120.Therefore, under normal sense of rotation, even other the power that the external force ' P ' that expands again from compression back working fluid is arranged or apply by connecting rod 33, the present invention can prevent relatively rotating between crank pin 110 and the eccentric adjusting sleeve 120.Even produced a partial rotational moment on eccentric adjusting sleeve 120, the present invention also can prevent relatively rotating between crank pin 110 and the eccentric adjusting sleeve 120.Shown in Figure 13 B, solid line in the accompanying drawing partly shows the state of upper dead center, dotted portion in the accompanying drawing shows the state of lower dead centre, and under the situation that normal direction is rotated, eccentric adjusting sleeve 120 is set to: make this eccentric adjusting sleeve 120 produce maximum throw of eccentric between connecting rod 33 that is connected to the piston (not shown) and crank pin 110.In view of the above, piston moves back and forth maximum running length Lmax, and compressor of the present invention has maximum compression volume.

Simultaneously, when bent axle 23a with oppositely, when promptly counter clockwise direction begins to rotate, between crank pin 110 and connecting rod 33, relative friction forces ' f ' is created in the direction of direction of rotation, is on the clockwise direction, with the moment ' M ' that rotates on the direction identical with turning to of eccentric mass 200.Under the effect of frictional force ' f ' and moment of rotation ' M ', eccentric adjusting sleeve 120 rotates around the axis 110a of crank pin in a clockwise direction from the position shown in Figure 13 A, and, shown in Figure 14 A, on a thicker side, described eccentric adjusting sleeve 120 has the step 123a that engages with first projection 131.Similarly, in bent axle 23 rotated, under the effect of frictional force ' f ' and moment of rotation ' M ', first projection 131 kept engaging with step 123a.Identical with dromic rotation, as shown in Figure 14B, when rotational velocity reaches certain level, by the effect of centrifugal force ' F ', second projection 132 engages with the step 123b of thin side, so that produce the multiple spot contact between eccentric adjusting sleeve 120 and the key member 130.Therefore, in backward rotation, even the external force ' P ' that has the pressure of working fluid in compression to cause acts on the piston, and have other external force to act on the piston, relatively rotating between crank pin 110 and the eccentric adjusting sleeve 120 can both be prevented from.And as shown in Figure 14B, under counter-rotational situation, because eccentric adjusting sleeve 120 is set to have minimum throw of eccentric, so piston moves back and forth minimum running length Lmin, and compressor of the present invention has minimum compression volume.

Like this, making element by key member 130 is that crank pin 110 and eccentric adjusting sleeve 120 keep throw of eccentric, by eliminating relatively rotating between the described element, compressor of the present invention can be at any operating condition, i.e. runs steadily under forward and backward rotation.

And eccentric mass 200 rotates eccentric adjusting sleeve 120 and it is engaged reposefully with key member 130.That is, eccentric mass 200 is used for eccentric adjusting sleeve 120 accurately is arranged on the desired position, so that throw of eccentric suitably changes.

It will be apparent to those skilled in the art that under the situation that does not deviate from marrow of the present invention or scope, can make various modifications and variations the present invention.Therefore, the present invention will have been contained various change of the present invention and variation, as long as these changes and variation have fallen in the scope of claims and equivalent thereof.

Industrial applicibility

During operation, the Multi-contact between eccentric adjusting sleeve and the key member is so that crank-pin and inclined to one side Heart sleeve is by the rigidly combination of effect of key member, so that any external cause or internal cause all can not Make to produce between eccentric adjusting sleeve and the crank-pin to relatively move, thereby in the situation that does not change output, Make the compressor can runs steadily. That is to say, because eccentric throw is constant, thereby Do not make in the situation of change, just can reach the compression volume of design. And the present invention prevents Relatively rotate the frictional dissipation that causes between crank-pin and the eccentric adjusting sleeve. Like this, this kind Stable running has just brought the raising of the running efficient of double volume capacity compressor. In addition, originally Invention has also prevented from relatively rotating the noise of generation, and has improved the service life of member.

The rotation moment that is produced by the eccentric block on the eccentric adjusting sleeve is so that stability of rotation, and makes off-centre The eccentric throw of sleeve changes. Therefore, eccentric adjusting sleeve accurately is arranged on the desired position On, in order to before eccentric adjusting sleeve is fully kept by key member, change eccentric throw and compression volume, Thereby improved the reliability of compressor operation of the present invention.

Claims

1. double-volume compressor, it comprises:

Power generating part branch, described power generating part branch comprise a reversible motor and a bent axle that embeds in the described motor;

Compression member, described compression member comprise the piston and the connecting rod that is connected with piston in cylinder, the cylinder;

Crank pin, described crank pin are positioned at the top of described bent axle and are eccentric in the axis of this bent axle;

Eccentric adjusting sleeve, described eccentric adjusting sleeve have the inner peripheral surface that cooperates with the outer peripheral surface of described crank pin in rotating mode, also have the outer peripheral surface that matches with an end of described connecting rod in rotating mode;

Key member, it is used on all sense of rotation of described motor described eccentric adjusting sleeve being fastened on described crank pin rigidly;

Eccentric mass, described eccentric mass is arranged on the described eccentric adjusting sleeve, is used to make described eccentric adjusting sleeve to rotate around described crank pin;

Thereby, provide different compression volumes by resetting eccentric adjusting sleeve, along with the change of motor sense of rotation, described eccentric adjusting sleeve changes effective throw of eccentric and piston stroke; And, between on-stream period,, in fact prevented relative movement between crank pin and the eccentric adjusting sleeve with key member regardless of the sense of rotation of motor.

2. double-volume compressor according to claim 1 is characterized in that, described key member is continued to remain at least a portion of described eccentric adjusting sleeve, and is designed to remain in addition described eccentric adjusting sleeve place.

3. double-volume compressor according to claim 1 is characterized in that, described key member keeps described eccentric adjusting sleeve at a plurality of somes place.

4. double-volume compressor according to claim 1 is characterized in that, between on-stream period, described key member is locating to keep described eccentric adjusting sleeve along any direction with respect to 2 of center line setting.

5. double-volume compressor according to claim 1 is characterized in that the length of described key member is greater than the external diameter of described crank pin.

6. double-volume compressor according to claim 1 is characterized in that, described crank pin has a pair of key member mating part that forms toward each other.

7. double-volume compressor according to claim 1 is characterized in that, the key member mating part of described crank pin is the some through holes in the described crank pin wall.

8. double-volume compressor according to claim 1 is characterized in that, described crank pin also comprises at least one first oil supply hole, and this oil supply hole is used for fuel feeding between described eccentric adjusting sleeve and described crank pin.

9. double-volume compressor according to claim 8 is characterized in that, described first oil supply hole forms in described bent axle so that be connected with the oil circuit that is used for to the different moving member fuel feeding of compressor.

10. double-volume compressor according to claim 8 is characterized in that, at least one described first oil supply hole has a pair of first oil supply hole that form, respect to one another in described crank pin.

11. double-volume compressor according to claim 1 is characterized in that, described eccentric adjusting sleeve comprises:

The rail portion that is formed along a circumference thereof, described rail portion are used to make described eccentric adjusting sleeve self to rotate with respect to the projection of described key member; With

With respect to the restricted part that described rail portion forms, described restricted part is used to limit the rotation of the projection of described key member.

12. double-volume compressor according to claim 11 is characterized in that, the rail portion of described eccentric adjusting sleeve is the part of cutting away of along the circumferential direction cutting apart from its certain depth place, top.

13. double-volume compressor according to claim 11 is characterized in that, the rail portion of described eccentric adjusting sleeve is one and is along the circumferential direction extending the through hole of a length apart from its certain depth place, top.

14. double-volume compressor according to claim 11 is characterized in that, the step that forms between described rail portion and described restricted part is parallel to the lighting outlet in the axle center of the axle center that connects described bent axle and described crank pin.

15. double-volume compressor according to claim 14 is characterized in that, described step equals half of described key member thickness apart from the spacing size of the lighting outlet in the axle center of axle center that connects described bent axle and crank pin.

16. double-volume compressor according to claim 8 is characterized in that, described eccentric adjusting sleeve also comprises second oil supply hole that the first interior oil supply hole of at least one and described crank pin is connected.

17. double-volume compressor according to claim 16 is characterized in that, described second oil supply hole optionally is connected with described first oil supply hole.

18. double-volume compressor according to claim 11 is characterized in that, the described step between described restricted part and the described rail portion is handled through fillet.

19. double-volume compressor according to claim 16 is characterized in that, described eccentric adjusting sleeve also is included in the oil pocket that forms around described second oil supply hole on its outer peripheral surface.

20. double-volume compressor according to claim 16 is characterized in that, described eccentric adjusting sleeve also is included in the oil groove that vertically stretches out from described second oil supply hole on its outer peripheral surface.

21. double-volume compressor according to claim 1 is characterized in that, described key member comprises:

First projection, even when compressor does not turn round, described first projection also can protrude a length from described crank pin; With

Second projection, when compressor operation, described second projection protrudes a length from described crank pin.

22. double-volume compressor according to claim 21 is characterized in that, the length that described second projection has can not protrude into outside the excircle of described crank pin its end when compressor does not turn round.

23. double-volume compressor according to claim 1 is characterized in that, described key member comprises retainer, and this retainer is used for limit movement with described key member in the key member mating part.

24. double-volume compressor according to claim 1, it is characterized in that described key member also comprises elastic member, it is used to support described key member, so that compressor operation what state no matter, at least a portion of described key member all keeps protruding outside described crank pin.

25. double-volume compressor according to claim 23 is characterized in that, described retainer has the crank pin surface of contact that the inner peripheral surface with described crank pin adapts.

26. double-volume compressor according to claim 23 is characterized in that, described retainer is first retainer that is used to limit the motion in one direction of described key member.

27. double-volume compressor according to claim 23 is characterized in that, described retainer also comprises second retainer that is used to limit the motion of described key member on another direction.

28. double-volume compressor according to claim 1 is characterized in that, described eccentric mass rotates described eccentric adjusting sleeve, so that be maintained at the part place of described key member.

29. double-volume compressor according to claim 1 is characterized in that, described eccentric mass produces a moment of rotation under action of centrifugal force, so that described eccentric adjusting sleeve rotates.

30. double-volume compressor according to claim 1 is characterized in that, described eccentric mass rotates described eccentric adjusting sleeve on the direction identical with the relative friction forces direction of described eccentric adjusting sleeve generation.

31. double-volume compressor according to claim 1 is characterized in that, described eccentric mass make described eccentric adjusting sleeve with the direction of the direction of rotation of described bent axle on rotate.

32., it is characterized in that described eccentric mass is arranged on that lighter relatively part of described eccentric adjusting sleeve weight according to claim 1 or 11 described double-volume compressors.

33. double-volume compressor according to claim 32 is characterized in that, described eccentric mass is arranged to the described rail portion near described eccentric adjusting sleeve.

34. double-volume compressor according to claim 1 is characterized in that, described eccentric mass is the plate-like piece that is arranged on the outer peripheral surface of described eccentric adjusting sleeve.

35. double-volume compressor according to claim 1 is characterized in that, described eccentric mass and described eccentric adjusting sleeve form parts.

36. double-volume compressor according to claim 1 is characterized in that, described eccentric mass is independent of described eccentric adjusting sleeve and forms, and is fixed in described eccentric adjusting sleeve.

37. double-volume compressor according to claim 1 is characterized in that, described eccentric mass is arranged at the top of described eccentric adjusting sleeve.