CN1839261A

CN1839261A - Dual capacity compressor

Info

Publication number: CN1839261A
Application number: CNA200380110453XA
Authority: CN
Inventors: 金钟凤; 金希玹; 裴英珠; 卢铁基
Original assignee: LG Electronics Inc
Current assignee: LG Electronics Inc
Priority date: 2003-12-20
Filing date: 2003-12-23
Publication date: 2006-09-27
Anticipated expiration: 2023-12-23
Also published as: KR100747566B1; CN1839261B; KR20050062233A

Abstract

The present invention relates to a dual capacity compressor for preventing relative movement from taking place between components. For this, the present invention provides a dual capacity compressor including a power generating part (20) having a reversible motor (21, or 22) and a crank shaft (23) inserted in the motor (21, or 22), 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 from an axis of the crank shaft (23), an eccentric sleeve (120) rotatably fitted between the crank pin (110) and an end of the connecting rod (33), a key member (130, or 230) configured such that the key member is held at at least a part of the eccentric sleeve (120), and held at the eccentric sleeve (120) additionally during operation, for latching the eccentric sleeve (120) with the crank pin (110) positively in both direction rotation of the motor.

Description

Double-volume compressor

Technical field

The present invention relates to a kind of be used for working fluid for example refrigeration agent be compressed to the compressor of required pressure, particularly relate to the compressor that a kind of compression volume changes with sense of rotation.

Background technique

Double-volume compressor is a kind of reciprocating-type compressor, and the sense of rotation along with motor and bent axle changes by means of the eccentric adjusting sleeve that is connected in rotating mode with the crankpin of bent axle for its stroke of piston and compression volume.Because the compression volume of double-volume compressor can change with required load, therefore this double-volume compressor is widely used in the equipment that needs compression working fluid, especially for the household electric appliance that are operated in the refrigeration cycle, for example in the refrigerator, to increase work efficiency.

U. S. Patent 4236874 discloses a kind of common double-volume compressor, below with reference to the double-volume compressor of this patent brief description prior art.

Fig. 1 is illustrated in the sectional view of disclosed double-volume compressor in the U. S. Patent 4236874, and Fig. 2 schematically shows the operation of this double-volume compressor.

With reference to Fig. 1, this double-volume compressor is provided with following critical component: the piston 7 that is arranged in cylinder body 8; Bent axle 1; Crankpin 3, the axis 3a of this crankpin 3 departs from the axis 1a of bent axle 1; The eccentric hoop 4 that is connected with crankpin 3; And be connected in connecting rod 6 between eccentric hoop 4 and the piston 7.This eccentric hoop 4 and connecting rod 6 can rotate relative to one another, and the while also rotates with respect to the axis 3a of crankpin.Crankpin 3 and eccentric hoop 4 are respectively equipped with on its contact surface and discharge district 9, are used for the key 5 that crankpin 3 and eccentric hoop 4 link together is arranged in this release district 9.The operation of this double-volume compressor relevant with compression volume will be introduced below.As shown in Figure 2, in double-volume compressor, the stroke of piston 7 is regulated by the eccentricity that changes with eccentric hoop 4 positions, wherein, when the needs larger capacity, bent axle 1 is (forward) rotation along clockwise direction, and when needs during than small capacity, bent axle 1 is (oppositely) rotation in the counterclockwise direction.In detail, Fig. 2 A represents that piston 7 is in the moment of upper dead center when rotating in the clockwise direction, and Fig. 2 B represents that piston 7 is in the moment of lower dead centre when rotating in the clockwise direction, at this moment makes stroke Lmax maximum owing to eccentricity is maximum.Fig. 2 C represents that piston 7 is in the moment of lower dead centre when rotating in the counterclockwise direction, and Fig. 2 D represents that piston 7 is in the moment of upper dead center when rotating in the counterclockwise direction, makes stroke Lmin minimum this moment owing to eccentricity is minimum.

But, in above-mentioned running, crankpin 3 and eccentric hoop 4 are owing to being subjected to centrifugal action around crankshaft center line 1a rotation, the two suffered centrifugal force is respectively perpendicular to crankshaft center line 1a and crankpin axis 3a, and lay respectively at the plane that comprises crankshaft center line 1a and crankpin axis 3a and comprise crankshaft center line 1a and the plane of eccentric hoop center of gravity 4a in.Therefore, different with Fig. 2 A and 2B, under situation shown in Fig. 2 C and the 2D, because active force is not on same straight line, 4 places have produced local running torque with respect to crankpin 3 at eccentric hoop, size be the centrifugal force of eccentric hoop to the perpendicular distance " d " of crankpin 3 and the product of the centrifugal force of himself, this action of centrifugal force direction is identical with the sense of rotation (counterclockwise) of bent axle 1.Because crankpin 3 and eccentric hoop 4 are the parts that can move relative to each other, thereby this running torque makes eccentric hoop 4 rotate relatively along the sense of rotation of bent axle 1, thereby key 5 is broken away from and the engaging of crankpin 3 and eccentric hoop 4, and eccentric hoop 4 and key 5 edge sense of rotation shown in the dotted line among Fig. 3 are moved.In addition, as shown in Figure 3, for example in rotation process along clockwise direction, the pressure " P " (pressure that working fluid is re-inflated) in the cylinder body after the compression promotes eccentric hoop 4 along the sense of rotation of bent axle 1, makes eccentric hoop 4 rotate with respect to crankpin 3 along the sense of rotation of bent axle.As a result, this relatively rotates and makes and the fluctuation of service of compressor can't obtain required compression performance.

In fact, relatively rotating is because key 5 can not block crankpin 3 and eccentric hoop well.As long as the sense of rotation of bent axle changes, key 5 will roll in discharging the district, thereby produces serious wearing and tearing on each contact surface, and shortened the working life of compressor.

Simultaneously, except that U. S. Patent 4236874, also have a lot of patent documentations to disclose the technology of double-volume compressor, below with brief description.

Similarly, U. S. Patent 4479419 also discloses a kind of double-volume compressor, and this compressor has crankpin, eccentric cam and key.This key is fixed on the eccentric cam, and when the sense of rotation of compressor changes along the orbiting in crankpin.But because this key can not block crankpin and eccentric cam well, U. S. Patent 4479419 also has because of relatively rotating the problem of the fluctuation of service that causes.

U. S. Patent 5951261 discloses a kind of compressor, and this compressor has: eccentric part, this eccentric part have the hole of passing this eccentric part and certain diameter being arranged; And eccentric cam, this eccentric cam has another hole in the one side, and this hole is identical with the bore dia of this eccentric part.In the hole of this eccentric part, be provided with pin, in the hole of eccentric adjusting sleeve, be provided with pressure spring.Therefore, when the hole in rotary course on time, the pin under action of centrifugal force, enter in the hole of cam, make this eccentric part and eccentric cam link together thus.But, because 5951261 of U. S. Patents are provided with a hole in eccentric cam, therefore, have only when compressor when specific direction rotates, eccentric part and eccentric cam just can link together.And, because pin is very difficult to accurately moving of cam by each hole from eccentric part, therefore can not guarantee the stability of moving.

Summary of the invention

The purpose of this invention is to provide a kind of double-volume compressor, it can be maintained fixed eccentricity, even and also can stable operation when compressor rotates along the either direction with different compression volumes.

As mentioned above, the inventor recognizes, in running, the irregular operation of double-volume compressor is that the external loading that applies by the local centrifugal force of eccentric adjusting sleeve and by connecting rod etc. is caused.Although use eccentric stiffener will occur these situations inevitably, the inventor recognizes, if crankpin and eccentric adjusting sleeve can be fixed in running rigidly, just can address this problem.Consider key member, key member and associated components thereof are changed to prevent relatively rotating between crankpin and the eccentric adjusting sleeve with fixed structure like this.

According to this point, the invention provides a kind of double-volume compressor, it comprises: power generating part spare, it comprises the bent axle in reversing motor and this motor of insertion; Compression member, it comprises cylinder body, the piston in this cylinder body and the connecting rod that links to each other with this piston; Crankpin, this crankpin are on the top of bent axle, and the eccentric axis of relative bent axle; Eccentric adjusting sleeve, the interior perimeter surface of this eccentric adjusting sleeve matches with the outer surface of crankpin in rotating mode, and the outer surface of this eccentric adjusting sleeve matches with connecting rod one end in rotating mode; Key member, it is configured to remain at least a portion of eccentric adjusting sleeve, also remains on the eccentric adjusting sleeve when operation, so that all rigidly eccentric adjusting sleeve and crankpin are blocked on each sense of rotation of motor.

This key member is fixed on the part of eccentric adjusting sleeve all the time, is positioned at the radially inner side of bent axle relatively.More specifically, this key member comprises first protuberance, is used for stretching out all the time one section predetermined length of crankpin; And second protuberance, be used for only outstanding crankpin one end predetermined length when operation.

This key member prevents that eccentric adjusting sleeve is subjected to centrifugal force and produces ground running torque effect thus and rotate.In order to realize this point, this key member is fixed on the part of eccentric adjusting sleeve all the time, and the direction of the running torque that makes on eccentric adjusting sleeve thus to be produced is opposite with the sense of rotation of bent axle.More specifically, this key member comprises first protuberance that protrudes in crankpin all the time, and second protuberance that protrudes in crankpin all the time, and this second protuberance is fixed on the eccentric adjusting sleeve when compressor operating.

In addition, this key member also comprises elastic component, and regardless of the running state of compressor, this elastic component supports key member all the time, makes its at least a portion give prominence to crankpin.Preferably, these elastic component limit key parts move along a direction.This elastic component has uneven elastic force.This elastic component comprises and contacted first elastic component of key member, and respectively with first elastic component and crankpin in contacted second elastic component of perimeter surface, this second elastic component elastic force is greater than first elastic component.

This eccentric adjusting sleeve also comprises balancer weight, and this balancer weight is used for preventing because the disengaging of the eccentric adjusting sleeve that the rotation before key member blocks eccentric adjusting sleeve well causes from the key member by the center of gravity that changes eccentric adjusting sleeve.This balancer weight is positioned at the center of gravity of eccentric adjusting sleeve to comprise the plane of the bent axle longitudinal axis and the crankpin longitudinal axis.This balancer weight changes the center of gravity of eccentric adjusting sleeve so that be positioned to relative with the plane that comprises the bent axle longitudinal axis and the crankpin longitudinal axis.

Therefore, the present invention prevents relatively rotating between crankpin and the eccentric adjusting sleeve, makes compressor stable operation and improve its efficient.

Description of drawings

The included accompanying drawing of the present invention is used for understanding better the present invention, these description of drawings embodiments of the invention, and be used from specification one and explain principle of the present invention.

In institute's accompanying drawing:

Fig. 1 represents the sectional view of the double-volume compressor of prior art;

Fig. 2 schematically shows the operation of the existing double-volume compressor among Fig. 1;

Fig. 3 represents the sectional view of the key member of existing double-volume compressor, schematically shows the relative rotation between crankpin and the eccentric adjusting sleeve;

Fig. 4 represents the sectional view of the double-volume compressor of the preferred embodiment of the present invention;

Fig. 5 A represents the side view that has partial sectional view of the double-volume compressor of first preferred embodiment of the invention;

Fig. 5 B represents the top view that has partial sectional view of the double-volume compressor of first preferred embodiment of the invention;

Fig. 6 A represents the perspective view of the crankpin of first preferred embodiment of the invention;

The perspective view of the version of the crankpin among Fig. 6 B presentation graphs 6A;

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

Fig. 7 B, 7C and 7D represent top view, side view and the perspective view of the version of eccentric adjusting sleeve of the present invention respectively;

Fig. 8 represents the perspective view of the key member of first preferred embodiment of the invention;

The planimetric map of the version of the key member in Fig. 9 presentation graphs 8, this key member matches with crankpin;

Figure 10 A and Figure 10 B represent the perspective view of key member, and each key member has dismountable first retainer of first preferred embodiment of the invention;

Figure 11 A-11C has represented the planimetric map of key member, and each key member has second stopper of first preferred embodiment of the invention;

Figure 12 represents to be used for the planimetric map of version of elastic component of first embodiment's key member;

Figure 13 A and Figure 13 B are planimetric map, and the operation of the double-volume compressor of first preferred embodiment is adopted in expression respectively, and this compressor is rotated in a clockwise direction;

Figure 14 A and Figure 14 B are planimetric map, and the operation of first embodiment's double-volume compressor is adopted in expression respectively, and this compressor rotates in the counterclockwise direction;

Figure 15 A and Figure 15 B are planimetric map, respectively expression have first embodiment key member eccentric adjusting sleeve along clockwise direction with the relation of counterclockwise rotating the power that is produced;

Figure 16 A～16C is the side view that has partial sectional view and the top view of the double-volume compressor of the present invention of the expression key member that adopts second embodiment;

Figure 17 is the side view of the key member of expression second preferred embodiment of the invention;

Figure 18 is the planimetric map of the version that is installed in the key member in the crankpin of expression second preferred embodiment of the invention;

Figure 19 A～19C is a planimetric map, represents the key member with retainer of second preferred embodiment of the invention respectively;

Figure 20 is the planimetric map of version of the elastic component of the expression key member that is used for second embodiment;

Figure 21 A and Figure 21 B are planimetric maps, the operation of the double-volume compressor of expression employing second embodiment's key member respectively, and this compressor is rotated in a clockwise direction;

Figure 22 A and Figure 22 B are planimetric maps, the operation of the double-volume compressor through changing of expression employing second embodiment's key member respectively, and this compressor rotates in the counterclockwise direction;

Figure 23 A and Figure 23 B are planimetric map, and expression has the relation of the power that the eccentric adjusting sleeve of second embodiment's key member produced with rotation counterclockwise along clockwise direction respectively;

Figure 24 is the perspective view of version that expression has the eccentric adjusting sleeve of balancer weight; And

Figure 25 A and 25B are planimetric maps, and expression has the relation of the eccentric adjusting sleeve of balancer weight along the power that rotation is produced with counter clockwise direction clockwise respectively.

Embodiment

To introduce the preferred embodiments of the present invention in detail below, the example is represented in the accompanying drawings.In described embodiment of the present invention, identical parts have identical title and reference character, and omit the repeat specification to it.Introduce the general structure of double-volume compressor of the present invention below with reference to Fig. 1.

As shown in the figure, double-volume compressor of the present invention comprises: power generating part spare 20, and the bottom that it is positioned at compressor is used for producing and transmitting required drive; And compression member 30, it is positioned at power generating part spare 20 tops, is used to utilize power to come compression working fluid.Except that these basic elements of character, this double-volume compressor also comprises stroke converting member 100, and this stroke converting member 100 is connected between power generating part spare 20 and the compression member 30, is used for changing at running the compression volume of compression member 30.Simultaneously, also be provided with encapsulation power generating part spare 20 and compression member 30 to prevent from the casing of freezing medium leakage, also to be provided with flexibly to be supported on the frame 12 on a plurality of supporting elements (being spring) that link to each other with the inboard of casing.This compressor also has refrigerant inlet 13 and the refrigerant outlet 15 that is installed to and is connected with casing inside.

Being positioned at frame 12 following power generating part spares 20 comprises: motor, this motor have stator 21 and rotor 22, utilize external power supply to produce rotating force; And bent axle 23.This motor can reverse.Insert in the rotor 22 bottom of this bent axle 23, is used for transferring power, and this bent axle 23 has oilhole or oil groove, is used for the lubricant oil that is stored in the bottom is supplied with each drive part.

Compression member 30 is installed on the frame 12 and above power generating part spare 20, it comprises: the mechanical driving member that is used for compressed refrigerant; And the suction valve and the expulsion valve that are used for auxiliary this driver part.Except the cylinder body 32 that in fact forms compression volume, this driver part also has: the connecting rod 33 that is used in cylinder body 32 pistons reciprocating 31 and is used to transmit the reciprocating power of piston 31.Valve combines with cylinder body lid 34 and cylinder front cover 35 and discharges from cylinder body 32 refrigeration agent is received cylinder body 32/.

To introduce the stroke converting member 40 of double-volume compressor of the present invention below in detail, omit explanation simultaneously power generating part spare same as the prior art and compression member.

With reference to Fig. 5 A, this stroke converting member 40 comprises generally: crankpin 110, and it is positioned at the top of bent axle and with respect to crankshaft eccentric; Eccentric adjusting sleeve 120, it is engaged between the outer circumferential face and connecting rod 33 of crankpin 110 in rotating mode; And be engaged in key member 130 in the crankpin 110.This key member 130 keeps the relative position between crankpin 110 and the eccentric adjusting sleeve 120 when compressor operating.In this stroke converting member 100, eccentric adjusting sleeve 120 is arranged between connecting rod 33 and the crankpin 110 in rotating mode, and its effective eccentricity is changed along with the sense of rotation (forward or reverse) of motor.For the effective eccentricity after keeping changing, key member 130 blocks eccentric adjusting sleeve 120.Thus, in stroke converting member 100, after the sense of rotation of motor changed, the length of stroke of connecting rod and the displacement of piston changed along with the variation of effective eccentricity, make compression volume also change along with sense of rotation thus.Below introduced stroke converting member 100 of the present invention briefly, it has been described in detail below in conjunction with accompanying drawing.

Fig. 5 A and 5B represent the side-looking and the sectional view of double-volume compressor of the present invention respectively, for convenience of description and for the purpose of clear, wherein broken section the parts of the compressor after the assembling.Fig. 6 A～Figure 12 represents each parts individually.

With reference to Fig. 5 A, this crankpin 110 is local hollow, is used for key member 130 is installed to this hollow space in a movable manner.This crankpin 110 also has a pair of key member mating part 111 respect to one another, and has oil duct 112 and oil supply hole 113 in the bottom.

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

auxiliary section

111a and 111b are formed on hollow tubular portion, cause it to be positioned at the vertical plane that comprises crankshaft center line 23a and crankpin axis 110a.Therefore, this key member 130 in

auxiliary section

111a and 111b is subjected to the influence of centrifugal force ' F ', and this centrifugal force ' F ' is along the length direction of key member 130 and in the plane at axle 23a and axle 110a place.This key member 130 is subjected to the leading role of

auxiliary section

111a and 111b and removable under the effect of centrifugal force ' F '.As shown in Figure 6A, in fact

auxiliary section

111a and 111b form through hole.The auxiliary section 111 of this through hole can prevent that key member 130 from coming off when compressor operating.Preferably, shown in Fig. 6 B,

auxiliary section

111a and 111b one of them can be that top from crankpin 110 walls extends to a groove that is easy to key member 130 is installed to the position on the crankpin 110 at least.More preferably be that a 111c of portion is set in the end of auxiliary section, in order to fit key parts 130 stably.

With reference to accompanying drawing 5A, oil groove and oil supply hole 113 in this oil duct 112 and bent axle 23 outer surfaces are connected.This oil supply hole 113 is perpendicular to the elongation line of

auxiliary section

111a and 111b line.When compressor operating, the lubricant oil of compressor bottom is at first by oil groove and oil duct 112, ejects subsequently so that be in operation and supply between the contact surface of parts, is used for preventing component wear and makes the parts smooth running; This lubricant oil also can directly supply in the gap between crankpin 110 and the eccentric adjusting sleeve 120 by oil supply hole 113.Preferably, make the position of crankpin 110 be higher than eccentric adjusting sleeve 120, so that lubricant oil evenly is ejected on the parts from eminence.

Eccentric adjusting sleeve 120 mainly has interior perimeter surface that combines in rotating mode with the outer surface of crankpin 110 and the outer surface that combines in rotating mode with an end of connecting rod 33.More specifically, shown in Fig. 7 A, eccentric adjusting sleeve 120 comprises: the rail portion 121 that forms along the circumference of eccentric adjusting sleeve 120, and the restricted part 122 that is used to limit rail portion 121 tracks.Two

step

123a and 123b are arranged between rail portion 121 and restricted part 122.Shown in Fig. 5 A, when compressor did not move, because at least a portion of key member 130 stretches out and engage with eccentric adjusting sleeve 120, so rail portion 121 made eccentric adjusting sleeve itself to rotate with respect to key member.That is to say that eccentric adjusting sleeve 120 can rotate around crankpin 110 in 121 restricted portions of rail portion that are formed at wherein.Restricted part 122 restriction sleeve and key member 130 the rotations when stopping or moving relative with rail portion 121.In fact, key member 130 is to be stuck in

step

123a and 123b place.

In fact, in eccentric adjusting sleeve 120, rail portion 121 can be play from the top of eccentric adjusting sleeve 120 desired depth, along the cut part of extending circumferentially.Shown in Fig. 5 B and Fig. 7 B, step 123a and 123b are parallel to the plane that comprises crankshaft center line 23a and crankpin axis 110a.That is to say that step 123a and 123b are parallel to the maximum ga(u)ge of eccentric adjusting sleeve and the line between the minimum thickness, so that have different width, and when compressor operating, this line is positioned on the plane that comprises axis 23a and 110a.We can say that perhaps when compressor operating, the plane parallel at step 123a and 123b place is in the plane that comprises axis 23a and 110a simultaneously.Therefore, key member 130 in the same plane can be blocked by step 123a and 123b simultaneously, makes step 123a and 123b in fact form the surface of common contact-key parts 130 thus.Preferably, to leave the distance on the plane that comprises axis 23a and 100a be half of key member 130 thickness " t " for step 123a and 123b.In view of the above, key member 130 can remain on step 123a and 123b place more stably and accurately.On the other hand, step 123a and 123b can have respectively the inclined-plane with respect to axis 23a and 110a place plane inclination several angle.More specifically, step 123c and 123d can form with axis 23a and 110a place plane inclination one angle θ ground simultaneously along the extend radially line of crankpin axis 110a and perpendicular to crankpin axis 110a.And step 123e and 123f can also tilt to restricted part at a certain angle around the crosspoint with inner peripheral surface.Even in these cases, step 123c, 123d, 123e and 123f also have the public point of contact with key member 130 at least, so that can be engaged with each other.In addition, this rail portion 121 not only can be the cut part shown in Fig. 7 A, also shown in Fig. 7 D apart from sleeve 120 top certain distances and along the through hole of extending circumferentially.The rail portion 121 that this through hole forms can keep key member 130 can vertically not break away from.

In addition, with reference to figure 7C, eccentric adjusting sleeve 120 can also be included in the oil supply hole 124 that the certain altitude place forms relatively.This oil supply hole 124 can be with respect to axis 23a and 110a place plane symmetry through hole, and like this, when key member 130 was maintained on the eccentric adjusting sleeve 110, this oil supply hole 124 was connected with oil supply hole 113 in the crankpin.Therefore, when the operation of compressor, no matter sense of rotation is how, always there is one to be communicated with in two oil supply holes 124 with oil supply hole 113, thus make lubricant oil can supply with eccentric adjusting sleeve 120 and connecting rod 33.In addition, form oil groove 124a with certain depth, be used to form around the space of oil supply hole 124 distribute lubrication oil, thereby can easily lubricant oil be supplied with between eccentric adjusting sleeve 120 and the connecting rod 33 around oil supply hole 124.Referring again to Fig. 7 A, eccentric adjusting sleeve 120 can also comprise the seat 125 at each step 123a and 123b place.When key member 130 was maintained by eccentric adjusting sleeve 110, seat 125 held key member 130.In fact this 125 can be groove among step 123a or the 123b, and the part of preferred key member 130 matches with the part of step 123.Owing to have seat 125, therefore key member 130 can remain in the eccentric adjusting sleeve 120 with being stabilized.In addition, owing to have seat 125, be not to contact between key member 130 and the eccentric adjusting sleeve 120, but face contact.Therefore, when compressor operating, even contact repeatedly between key member 130 and the eccentric adjusting sleeve 120, key member 130 and eccentric adjusting sleeve 120 can not concentrated with fatigue because of stress and cause destroying.In addition, shown in Fig. 5 A and Fig. 7 C, can between eccentric adjusting sleeve 120 and bent axle 23, ring-shaped article 126 be set.Owing to be the line contact between ring-shaped article 126 and the eccentric adjusting sleeve 120, therefore can reduce the friction between them effectively, more steady than the rotation of only using eccentric adjusting sleeve 120.

Fig. 5 A, Fig. 5 B and Fig. 8 represent the key member of first preferred embodiment of the invention respectively.As shown in the figure, the key member 130 of first preferred embodiment of the invention comprises substantially: first protuberance 131, even when compressor does not move, also give prominence to certain-lengths from crankpin 110; And second protuberance 132, be used for when compressor operating from crankpin 110 outstanding certain-lengths.This key member 130 also comprises first retainer 133, is used to limit the outstanding length of first protuberance 131.In addition, this key member 130 also comprises elastic component 140, is used for adjusting when compressor stops or moving the position of key member 130.In the present invention, this key member 130 is subjected to centrifugal action and blocks eccentric adjusting sleeve 120 when mobile.As indicated above, especially second protuberance 132 is outstanding and maintain eccentric adjusting sleeve 120 in when operation.For when moving, given prominence to by action of centrifugal force, need make second protuberance 132 identical with the direction of centrifugal force.Therefore, as shown in the figure, when second protuberance, 132 relative positionings during in the outside of bent axle 23 and crankpin 110 radiuses, first protuberance 131 relatively is positioned the inboard of bent axle 23 and crankpin 110 radiuses.In other words, in fact, second protuberance 132 is set in crankpin 110, leaves crankshaft center line 22a, is used to bear big centrifugal force, and relative therewith, 131 of first protuberances are set near center 22a.In addition, in order to block eccentric adjusting sleeve 120 simultaneously when moving, the length of preferred key member 130 is greater than the external diameter of crankpin 110.

More specifically, shown in Fig. 5 A, first protuberance 131 protrude in crankpin 110 and no matter the running state of compressor (stop or being in operation) how always to engage with one of

step

123a and 123b, thereby even when compressor operating, also keep jointing state.For this reason, on second protuberance 132 elastic component 140 is installed, the inwall of itself and crankpin 110 flexibly supports first retainer 133 together.Owing to first retainer 133 of key member 130 stops the outstanding length that defines first protuberance mutually with the inwall of crankpin 110.In order to make operation more stable, the length of preferred first protuberance is at least half of minimum width of step 123a and 123b.In addition, as mentioned above, first protuberance 131 is positioned at bent axle 23 and crankpin 110 inboard radially, and this first protuberance 131 is outstanding towards inboard (being the axis 23a of bent axle) radially all the time.Therefore, this key member 130 is always maintained by at least a portion that is positioned at bent axle 23 radially inner sides relatively of eccentric adjusting sleeve 120.

The projected direction of second protuberance is opposite with first protuberance, so that engage with another step when compressor operating.Like this, first protuberance 131 of key member 130 and second protuberance 132 just engage with eccentric adjusting sleeve 120 simultaneously.Increase and increase gradually along the centrifugal force of key member 130 rotational speed, to overcome the elastic force of elastic component 140 along with bent axle 23.Therefore, second protuberance just moves and gives prominence to along the direction (being the length direction of key member along axis 23a and plane, 110a place) of centrifugal force.In this case, change sense of rotation at compressor and make, eccentric adjusting sleeve 120 just rotates to change eccentricity around crankpin 110.Therefore, in order not hinder eccentric adjusting sleeve 120 rotations, the length of second protuberance 132 should make its end not be projected into the outer circumferential face that exceeds crankpin 110 when compressor does not move.

First and second protuberances 131,132 engage with

step

123a and 123b in turn according to the sense of rotation of bent axle.Because key member 130 is perpendicular to

axis

23a and 110a and be positioned at or the plane at parallel to the axis at least 23a and 110a place, if thereby the thickness of first and second protuberances " t1 " is different with " t2 ", key member 130 is also different with the contacted position of 123b with step 123a so.Therefore, the thickness of first and second protuberances " t1 " should be identical with " t2 ", so that accurately engage with step 123a and 123b.Although key member 130 cross sections in specification of the present invention and accompanying drawing are circular, can adopt any sectional shape that can engage, as square or Hexagon with

step

123a and 123b.

As shown in Figure 9, the contact surface 133a of first retainer 133 can have the shape that matches with the interior perimeter surface of crankpin 100.Therefore, key member 130 can engage closely with crankpin 110, and moves more steady (promptly the centrifugal force of Zeng Jiaing makes that second protuberance 132 is easier to be outstanding) owing to the weight increase makes.Preferably, this first retainer 133 can also comprise recess 133b, is used for stably admitting elastic component 140.In fact such contact surface 133a and recess 133b can increase the operation stability of key member 230 auxiliaryly.Simultaneously, this first retainer 133 can be made with key member 130 integral body, also can be the individual components that is installed on the key member 130.Figure 10 A and 10B have represented the example of first retainer 133 of this independent.

With reference to Figure 10 A, first retainer 133 can comprise the projection 133a that radially extends internally.Therefore, when projection 133a fitted in the circumferential grooves of key member 130 appropriate locations, first retainer 133 just was engaged on the key member 130.Perhaps shown in Figure 10 B, first retainer 133 of simple ring-shaped article can be fixed on the appropriate position of key member 130 by fastening piece.Even the retainer of this independent 133 makes key member 130 also can be installed on the crankpin 130 when two key

member mating part

111a and 111b are through hole.More specifically, the inside by retainer 133 being placed crankpin 110 and by with these key member 130 these through holes of insertion then can be connected this retainer 133 with key member 130.

Simultaneously, as mentioned above, when normal operation, the outstanding length of second protuberance 132 in the key member 130 can be regulated by the elastic force of elastic component 240.But bent axle 23 and crankpin 110 rapid acceleration of the moment when compressor start make key member 130 be subjected to sizable instantaneous centrifugal force.This centrifugal force makes second protuberance 132 excessively outstanding under enough big centrifugal action, thereby causes first protuberance 131 to break away from auxiliary section 111.Therefore, preferably this key member 130 also comprises second retainer 134, is used to limit the length that second protuberance 132 is given prominence to from crankpin 110 when being subjected to centrifugal action.

With reference to Figure 11 A, second retainer 134 can be hollow tubular parts 134a, and these hollow tubular parts 134a is installed on second protuberance 132 in the mode that can move along the length direction of second protuberance 132.In this case, elastic component 140 is installed between the second retainer 134a and second protuberance 132.When key member 130 when the centrifugal force direction moves, the second retainer 134a contacts with the inwall of first retainer 133 and crankpin 110, the outstanding length that prevents first protuberance 133 thus is greater than certain-length.Shown in Figure 11 B, second retainer 134 can be that its thickness is at least greater than the extension 134b of the thickness of second protuberance 133.That is to say that the second retainer 134b among Figure 11 B is actually the longitudinal extension part of first retainer 133.At this moment, elastic component 140 is installed on the outer circumferential face of the second retainer 134b.Perhaps shown in Figure 11 C, second retainer 134 can be the radially extension 134c that second protuberance radially extends to desired thickness, and its shape is in fact similar to first retainer 133.At this moment, elastic component 140 is installed between the inner peripheral surface of the second retainer 134b and crankpin 110.Similar to the version of described first retainer 133 of Figure 10 A and 10B, retainer 134b and 134c can be fixed on the key member 130 with independent parts respectively.

Perhaps, as shown in figure 12, can substitute second retainer 134 with elastic component 140 and come moving of limit key parts 130, more specifically, be moving of restriction second jut 132.For this reason, elastic component 140 has uneven elasticity coefficient, so that the one part of spring has bigger elastic force.Like this, the distortion of elastic component 140 is less relatively when compressor operating, to reduce the outstanding length of second protuberance 132, so that even the outstanding of second protuberance 132 also is subjected to suppressing significantly when instantaneous excessive centrifugal force is applied to it, prevent that thus first protuberance 131 breaks away from from crankpin 110.More preferably, if the elastic force of the part of elastic component 140, can prevent very well that second protuberance 132 is excessively outstanding greater than the maximum centrifugal force of compressor.

With reference to Figure 12, in fact such elastic component 140 comprises first elastic component 141 with predetermined elastic force, and has second elastic component 142 greater than the elastic force of first elastic component 141.This first elastic component 141 contacts with first retainer 133, is used to keep first protuberance 131 outstanding.Similarly, this second elastic component 142 contacts with first elastic component and is supported on the inner peripheral surface of crankpin 110, be used to make first protuberance 131 outstanding and with the first together deformation of elastic component 141.More specifically, as shown in the figure, if elastic component 140 is a form of springs, first elastic component 141 is for having the spring of predetermined diameter so, second elastic component 142 be all the time with first spring that elastic component 141 links to each other and diameter is bigger, this spring is designed to have bigger elasticity coefficient, therefore also has bigger elastic force.As indicated above, the elastic force of preferred second elastic component 142 is used for preventing well that greater than the maximum centrifugal force of compressor second protuberance 142 is too outstanding.That is to say, in this case, have only first elastic component 141 to deform, and second elastic component 142 can not be subjected to centrifugal force and be out of shape.Therefore, similar to second retainer 134, this second elastic component 142 prevents that key member 140 is too mobile.Because elastic component 142 can prevent also that even without second retainer 134 key member 130 breaks away from, and therefore can simplify the structure of key member 130, and key member 130 is installed easily.

In a word, the length of key member 130 grows at least one prearranging quatity than the diameter of crankpin basically, and is installed in the crankpin in a movable manner.Even compressor does not move, at least a portion of key member 130 (i.e. first protuberance) is also by outstanding in the crankpin, and another part of key member 130 (i.e. second protuberance) is subjected to centrifugal action outstanding from crankpin 110 when compressor operating.That is to say that key member 130 is remained at least a portion of eccentric adjusting sleeve 120, though in addition when compressor operating key member 130 also be maintained on the eccentric adjusting sleeve 120.Therefore this key member 130 mainly contacts at multiple spot with eccentric adjusting sleeve 120, and more specifically, when compressor operating, this key member 130 contacts simultaneously with the opposite end that eccentric adjusting sleeve 120 is provided with about the arbitrary center line in its horizontal plane.Finally, this key member 130 makes the crankpin 110 of eccentric adjusting sleeve 120 and rotation along arbitrary sense of rotation of motor positive engagement mutually, prevents that thus eccentric adjusting sleeve 120 and crankpin 110 from moving relative to each other.

Introduce the operation of double-volume compressor of the present invention with reference to the accompanying drawings.Planimetric map when the planimetric map when Figure 13 A and Figure 13 B represent respectively that double-volume compressor of the present invention moves along clockwise direction, Figure 14 A and 14B represent respectively that double-volume compressor of the present invention moves in the counterclockwise direction.

Figure 13 A represents to begin the relative position between the key member 130 and eccentric adjusting sleeve 120 when forward (being clockwise direction) rotates when bent axle.As indicated above, first protuberance 131 is subjected to always protruding in crankpin 110 along crankpin 110 radially inner elastic force effects.Under the state that first protuberance 131 is given prominence to, if bent axle 23 begins rotation along clockwise direction, crankpin, eccentric adjusting sleeve and key member 110,120,130 also begin to be rotated in a clockwise direction around the axis 23a of bent axle.In rotary course, has relative friction forces ' f ' between crankpin 110 and the connecting rod 33 with direction of rotation.Therefore, eccentric adjusting sleeve 120 is subjected to the effect of frictional force ' f ' and rotates in the counterclockwise direction around crankpin 110, blocks first protuberance 131 up to the step 123b of thin-walled side.In case bent axle 23 rotations, because frictional force always produces when bent axle 23 rotates, then the state that blocks between first protuberance 131 and the step 12b also keeps always.At this moment, shown in Figure 13 B, if angular velocity of rotation reaches certain value, key member 130 will be along the action direction of centrifugal force ' F ', and promptly the length direction in axis 23a and plane, 110a place of key member moves under the effect of centrifugal force ' F '.Therefore, second protuberance 132 engages with the step 223a of heavy wall side, and meanwhile, first protuberance is also keeping the contacted state with step 123b.This multiple spot contacts simultaneously and makes key member 130 fully to engage with eccentric adjusting sleeve 120.Therefore, when being rotated in the forward,, can not relatively rotate between crankpin 210 and the eccentric adjusting sleeve 220 even the external force ' P ' that the working fluid after the compression is produced by expanding and other power are transmitted by connecting rod 330 yet.In addition, even produce local running torque, can prevent that also eccentric adjusting sleeve 120 from rotating relative to crankpin 110 at eccentric adjusting sleeve 120 places.In addition, with reference to Figure 13 B, solid line among the figure is partly represented the upper dead center state, and the dotted portion among the figure is represented the lower dead centre state, and eccentric adjusting sleeve 220 is configured to provide the eccentricity of maximum between piston (not shown) that links to each other with connecting rod 33 and crankpin 110 when just changeing.Therefore, piston back and forth, makes compressor of the present invention have maximum compression volume in maximum stroke length Lmax.

Simultaneously, if bent axle 23 begins counter-rotating, i.e. rotation in the counterclockwise direction, produce between crankpin 110 and the connecting rod 33 opposite with sense of rotation, promptly clockwise relative friction forces ' f '.Subsequently, eccentric adjusting sleeve 120 is begun to be rotated in a clockwise direction around crankpin 110a by the position shown in Figure 13 A, engages with first protuberance 131 up to the step 123a of heavy wall side, shown in Figure 14 A.Similarly, when bent axle 23 rotations, keep engaging by frictional force ' f ' between first protuberance 131 and the step 123a.To be rotated in the forward similar, as shown in Figure 14B, if angular velocity of rotation reaches certain value, second protuberance 232 engages with the step 123b of thin-walled side under the effect of centrifugal force ' F ', makes thus to be in the multiple spot contact condition between eccentric adjusting sleeve 120 and the key member 130.Therefore, when counterrotating, even other any power existence that has working fluid to affact the external force ' P ' on the piston and be subjected to when compression also can prevent to relatively rotate between crankpin 110 and the eccentric adjusting sleeve 120.In addition, as shown in Figure 14B, when counterrotating, because eccentric adjusting sleeve 120 is configured to have minimum eccentricity, piston back and forth, makes compressor of the present invention have minimum compression volume in minimal stroke length L min thus.

In a word, eliminated well between the parts that keep eccentricity by key member 130, be the relative movement between crankpin 110 and the eccentric adjusting sleeve 120 that compressor of the present invention can be in free position, i.e. stable operation under the forward or reverse state.

Simultaneously, with reference to Figure 15 A and 15B, eccentric adjusting sleeve 120 has eccentric center of gravity ' G ' because of its structure.That is to say that center of gravity ' G ' is in the heavier side of restricted part 122.When bent axle 23 rotation, centrifugal force ' C ' along the elongation line of line between center of gravity ' G ' and the crankshaft center line 23a and perpendicular to the directive effect of the axis 23a of bent axle 23 on center of gravity ' G '.Because center of gravity ' G ' off-centre, thereby centrifugal force ' C ' produces the moment of rotation ' M ' around crankpin axis 23a.In more detail, as shown in the figure, this running torque ' M ' can be expressed as centrifugal force ' C ' and perpendicular to the product of the long d of the arm of force of crankpin axis 23a.The action direction of this running torque ' M ' is identical with the sense of rotation of bent axle.That is to say that shown in Figure 15 A, when turning clockwise, eccentric adjusting sleeve is owing to center of gravity ' G ' produces clockwise running torque; Shown in Figure 15 B, when being rotated counterclockwise, eccentric adjusting sleeve is owing to center of gravity ' G ' produces anticlockwise running torque.As indicated above, when frictional force ' f ' is tending towards along the direction rotating eccentric sleeve tube 120 opposite with sense of rotation, when eccentric adjusting sleeve 120 engaged with first protuberance 131, running torque ' M ' was tending towards the sense of rotation rotating eccentric sleeve tube 120 towards compressor.Therefore, running torque ' M ' may cause eccentric adjusting sleeve 120 little rotation intermittently, thereby causes eccentric adjusting sleeve 120 and key member 130 to be disengaged.The rotation of eccentric adjusting sleeve 120 hinders the outstanding of second protuberance and blocks.

Second embodiment's key member 230 can prevent the rotation by centrifugal force ' C '/caused eccentric adjusting sleeve 120 of running torque ' M '.Figure 16 A～16C and Figure 17 describe key member 230 in detail.

As shown in the figure, this second embodiment's key member 230 comprises substantially: first protuberance 231 and second protuberance 232, each protuberance all always protrude in crankpin 110 certain-lengths when operation.This second protuberance 232 does not engage with eccentric adjusting sleeve 120 when compressor stops, but just moves when compressor operating and engage with eccentric adjusting sleeve 120.This key member 230 also comprises be used to limit first retainer 233 that it moves on certain orientation.This first retainer, 233 restrictions, second protuberance 232 radially moves inward and limits the outstanding length of second protuberance 232.In addition, similar to first embodiment, elastic component 140 is set in order to adjust the position of key member 230 on key member 230.Shown in before Figure 15 A and 15B, rotate owing to eccentric adjusting sleeve 120 is subjected to centrifugal force ' C ' and running torque ' M ', so key member 130 is difficult to block the part of eccentric adjusting sleeve 120 radially outers.Therefore, preferred second embodiment's key member 230 has the part that engages with the radially outer of eccentric adjusting sleeve 120 when starting compressor moves.For this reason, when first protuberance 231 that will keep outstanding state was positioned at the radial outside of bent axle 23 and crankpin 110,231 of second protuberances were positioned at radially inner side.In other words, rotate in order to prevent eccentric adjusting sleeve 120, first protuberance 231 is configured to the axis 22a away from bent axle in crankpin 110, and relatively, second protuberance 131 is arranged near axis 22a.

In more detail, shown in Figure 16 A, first protuberance 231 has the sufficient length that keeps its outstanding crankpin 110, and as indicated above, and first protuberance 231 is outstanding towards the radial outside of bent axle 23 and crankpin 110 along the direction of the centrifugal force that produces when moving.Therefore, shown in Figure 16 C, first protuberance 231 is further given prominence to towards radial outside owing to centrifugal force when operation, even therefore also keep engaging with eccentric adjusting sleeve 120 when compressor operating.

This second protuberance 232 protrudes in crankpin 210 along the direction opposite with first protuberance 231 under the elastic force effect of elastic component 140.For this reason, elastic component 140 is installed on first protuberance 231 and is flexibly supported this first retainer 233 together in order to the inwall with crankpin 110.First retainer 233 on the key member 130 is stuck on the inwall of crankpin 110, thereby limits the outstanding length of second protuberance 232.Simultaneously, when compressor converted mutarotation veer, this resilient sleeve 120 rotates to change eccentricity around crankpin 110.Therefore, when out of service, bar 120 rotates in the eccentric adjusting sleeve in order not hinder, and should not make second protuberance 232 protrude in crankpin 110, interferes eccentric adjusting sleeve 120 to prevent this second protuberance 232.In more detail, as shown in the figure, this second protuberance 232 has the groove 232a that eccentric adjusting sleeve 130 is passed through.The width of preferred this groove 232a is a bit larger tham the Extreme breadth of eccentric adjusting sleeve 130.This groove 232a allows the end 32b of second protuberance to be positioned at outside the eccentric adjusting sleeve 120.In when operation, increase along with the rotating speed of bent axle 23 and become bigger along centrifugal force ' F ' that key member 230 produced, and become greater than the elastic force of elastic component 140.This second protuberance moves in the effect lower edge of centrifugal force ' F ' centrifugal force direction (length direction along axis 23a and plane, 110a place of key member), is stopped by eccentric adjusting sleeve 120 until the end of the second protuberance 232b, shown in Figure 16 C.Therefore, when compressor operating, first and second protuberances 231,232 of key member 230 engage with eccentric adjusting sleeve 120 simultaneously.

This second embodiment's key member 230 just can be used for double-volume compressor of the present invention under the situation that need not change crankpin 110 and eccentric adjusting sleeve 120.Owing to crankpin 110 and eccentric adjusting sleeve 120 are illustrated, even therefore key member 230 has further feature also no longer to crankpin 110 and the more explanation of eccentric adjusting sleeve 120 dos with reference to Fig. 6 A～Fig. 7 D.

With reference to Figure 18, this first retainer 233 comprises the contact surface 233a that shape matches with the interior perimeter surface of crankpin 110, and preferably has the pit 233b that is suitable for holding elastic component 140.This contact surface 233a and pit 233b help second embodiment's key member 230 stable operations.This first retainer 233 can form with key member 230, also can manufacture independently parts.

When normal operation, outstanding and mobile can the adjusting of first and second protuberances 231,232 by the elastic force of elastic component 140.But as indicated above, key member 230 is easy to break away under instantaneous action of centrifugal force, and particularly second protuberance 232 can not accurately engage with eccentric adjusting sleeve 120.In order to prevent key member 230 irregular operatings, preferably, can further use second retainer 234 to move along its suffered centrifugal force direction in order to limit key parts 230.Shown in Figure 19 A～Figure 19 C, identical among the shape of this second retainer and first embodiment.That is to say, this second embodiment's retainer 234 can be to be installed in hollow part 234a (referring to Figure 19 A) on second retainer 234 in the mode that can move along its length, or the extension 234b (referring to Figure 19 B) of first retainer, 133 length directions, or the extension (referring to Figure 19 C) of the outstanding predetermined thickness of first protuberance, 231 radially outwards.

In addition, identical with first embodiment with reference to Figure 20, second embodiment's key member 230 can adopt the uneven elastic component 140 of elastic force to substitute second retainer 234.As shown in the figure, this elastic component 140 has first elastic component 141 that predetermined elastic force is arranged and elastic force second elastic component 142 greater than first elastic component 141.In fact, this first elastic component 141 is the springs with predetermined diameter, and therefore the spring diameter of second elastic component 142 has bigger elasticity coefficient and elastic force greater than the spring diameter of first elastic component.The elastic force of this second elastic component 141 is used for preventing at all that greater than the maximum centrifugal force of compressor key member 230 from moving excessively.These elastic component 140 limit key parts 230 move along the centrifugal force direction, are used for preventing that key member 230 breaks away from or successfully do not blocking eccentric adjusting sleeve from eccentric adjusting sleeve.In addition, make key member 130 simplify owing to optional feature (for example second retainer 234) can be set, and make key member 130 be easy to install.

The operation of the double-volume compressor of the key member with second embodiment of the invention is described below with reference to accompanying drawings.Figure 21 A and Figure 21 B represent the planimetric map that double-volume compressor of the present invention is rotated in a clockwise direction respectively, and Figure 22 A and Figure 22 B then represent the planimetric map that double-volume compressor of the present invention moves in the counterclockwise direction respectively.

Figure 21 A represents that bent axle begins just to change, the relative position relation when promptly rotating along clockwise direction between key member 130 and the eccentric adjusting sleeve 120.As mentioned above, first protuberance 231 is exceeding crankpin 110 along always being projected under the effect of crankpin 110 radially inner elastic force.Under the state that first protuberance 231 is given prominence to, if bent axle 23 begins to be rotated in a clockwise direction, crankpin, eccentric adjusting sleeve and key member 110,120 and 130 also begin to be rotated in a clockwise direction around the axis 23a of bent axle.In rotary course, produce and direction of rotation, i.e. relative friction forces in the counterclockwise direction ' f ' between crankpin 110 and the connecting rod 33.Therefore, eccentric adjusting sleeve 120 rotates in the counterclockwise direction around crankpin 110 under the effect of frictional force ' f ', up to eccentric adjusting sleeve 120, restricted part 122 is passed the groove 232a of second protuberance more specifically, and the step 123b of thin-walled side is stuck on first protuberance 231.Shown in Figure 23 A, because first protuberance 231 is blocking eccentric adjusting sleeve 120 with respect to the position of bent axle radial outside, therefore with respect to the action of centrifugal force line (perpendicular to axis 23a and 110a, and be positioned at axis 23a and plane, 110a place), the center of gravity of eccentric adjusting sleeve 120 ' G ' is opposite with position of centre of gravity among Figure 15 A.Because the reason of center of gravity ' G ' position, centrifugal force ' C ' has produced the running torque ' M ' of opposite with sense of rotation (counterclockwise).Therefore, running torque ' M ' is with the frictional force ' f ' along same directive effect, and along the direction opposite with sense of rotation, promptly counter clockwise direction rotating eccentric sleeve tube 120 makes the stable engagement between protuberance 231 and the step 123b of winning.Subsequently, shown in Figure 21 B, if rotational angular velocity reaches certain value, key member 130 will be along the direction of centrifugal force ' F ', and promptly the length direction in axis 23a and plane, 110a place of key member moves under the effect of centrifugal force ' F '.Therefore, described with reference to Figure 16 C as mentioned, the end 232b of second protuberance 132 engages with the step 223a of heavy wall side, and meanwhile, first protuberance 131 is also keeping the contacted state with step 123b.As indicated above, because first protuberance 231 keeps stable engagement under the effect of the running torque opposite with sense of rotation ' M ', therefore second protuberance 232 can block eccentric adjusting sleeve 120 reposefully.This multiple spot contacts simultaneously and makes key member 130 fully to engage with eccentric adjusting sleeve 120.Therefore, when being rotated in the forward, even the working fluid after the compression also can prevent relatively rotating between crankpin 210 and the eccentric adjusting sleeve 220 because external force ' P ' and other power that is produced that expands again transmits by connecting rod 330.In addition, even produce local running torque, can prevent that also eccentric adjusting sleeve 120 from rotating relative to crankpin 110 at eccentric adjusting sleeve 120 places.Also have, with reference to Figure 21 B, the solid line among the figure is partly represented the upper dead center state, and the dotted portion among the figure is represented the lower dead centre state, and eccentric adjusting sleeve 220 is configured to provide the eccentricity of maximum when just changeing.Therefore, piston to-and-fro motion in maximum stroke length Lmin, compressor of the present invention has minimum compression volume thus.

If bent axle 23 begins counter-rotating, i.e. rotation in the counterclockwise direction, produce between crankpin 110 and the connecting rod 33 opposite with sense of rotation, i.e. relative friction forces along clockwise direction ' f '.Therefore, eccentric adjusting sleeve 120 begins to pass groove 232a and rotates around curved pin axis 110a in the counterclockwise direction from the position shown in Figure 21 A, up to the step 123a of eccentric adjusting sleeve 120 heavy wall sides with till radially outwards outstanding first protuberance 131 engages, shown in Figure 22 A.Shown in Figure 23 B, identical with the principle that turns clockwise, the center of gravity of eccentric adjusting sleeve ' G ' is opposite with respect to the action of centrifugal force line with position of centre of gravity among Figure 15 B.Therefore, centrifugal force ' C ' has produced the clockwise running torque ' M ' opposite with sense of rotation, and this running torque ' M ' is identical with the action direction of frictional force, and they keep stable engagement between first protuberance 231 and the step 123a together.As described in Figure 22 B, same with positive phase inversion, if angular velocity of rotation reaches certain value, second protuberance 232 engages with the step 123b of thin-walled side under the effect of centrifugal force ' F ', makes thus to be in the multiple spot contact condition between eccentric adjusting sleeve 120 and the key member 130.Identical with situation about turning clockwise, the stable engagement of first protuberance 231 makes second protuberance 232 and eccentric adjusting sleeve 120 smooth engagement.Therefore, when counterrotating, even when compression by working fluid pressure produced affacts external force ' P ' on the piston and other suffered any power exists, also can prevent to relatively rotate between crankpin 110 and the eccentric adjusting sleeve 120.In addition, shown in Figure 22 B, when counterrotating, because eccentric adjusting sleeve 120 is configured to have maximum eccentricity, thereby piston to-and-fro motion in maximum stroke length Lmax, make compressor of the present invention have maximum compression volume thus.

In a word, eliminate relatively moving between crankpin 110 and the eccentric adjusting sleeve 120, make compressor stable operation of the present invention by having used key member 130 very well.In addition, key member 230 prevents that eccentric adjusting sleeve from rotating, and guaranteed reliability of operation thus under the effect of eccentric force ' C ' and running torque ' M '.

On the other hand, in order to prevent second protuberance, 132 unstable joints, proposed eccentric adjusting sleeve 120 above with reference to Figure 15 A and 15B and can further include balancer weight 127, this balancer weight 127 makes the centre-of gravity shift of eccentric adjusting sleeve 120, prevents that key member 130 is disengaged.As indicated above, because center of gravity ' G ' deflection restricted part 122, thereby in rotation subsequently, before key member 130 blocks eccentric adjusting sleeve 120, just produced running torque ' M ' well.For the position of swerve the weight ' G ', need to increase the weight of eccentric adjusting sleeve 120 than light fraction.This balancer weight has the approrpiate wts that is used to be offset center of gravity, and is arranged on the rail portion 121 of the lighter side of eccentric adjusting sleeve.This balancer weight 127 can form with eccentric adjusting sleeve, perhaps can be used as individual components and is installed on the eccentric adjusting sleeve 120.

The eccentric adjusting sleeve 120 that Figure 25 A and 25B represent to have balancer weight 127 respectively is along the planimetric map of the relation of the power that produces when counterclockwise rotating clockwise.

As shown in the figure, preferably this balancer weight 127 can make the center of gravity " G1 " of eccentric adjusting sleeve be displaced on the plane at crankshaft center line 23a and crankpin axis 110a place.Center of gravity " G1 " can make centrifugal force ' C1 ' action direction of the centrifugal force ' F ' of bent axle 23/ crankpin 110 and eccentric adjusting sleeve 120 identical.Therefore, owing between center of gravity " G1 " and crankpin axis 110a, do not have the arm of force, therefore no matter be rotated in a clockwise direction (Figure 25 A) or rotation (Figure 25 B) in the counterclockwise direction, can not produce running torque, and, therefore can prevent from basically to rotate owing to there is not running torque.

In addition, this balancer weight 127 makes the center of gravity ' G2 ' of eccentric adjusting sleeve 120 be displaced to the relative position with plane, crankpin axis 110a place about crankshaft center line 23a from original center of gravity ' G '.Center of gravity ' G2 ' has just produced the running torque ' M2 ' with the direction of rotation of centrifugal force ' C2 ' like this.That is to say, shown in Figure 25 A, when bent axle turns clockwise, center of gravity ' G2 ' has produced anticlockwise running torque ' M2 ', and shown in Figure 25 B, when bent axle was rotated counterclockwise, center of gravity ' G2 ' had produced clockwise running torque ' M2 '.Running torque ' M ' works with frictional force ' f ' one, and eccentric adjusting sleeve 120 is rotated along the direction opposite with sense of rotation.Therefore, first protuberance 131 stably engages with eccentric adjusting sleeve 120, makes second protuberance 132 engage reposefully continuously with eccentric adjusting sleeve 120 thus.

Generally speaking, similar to the key member 230 among second embodiment, balancer weight 127 is owing to the effect of centrifugal force ' C '/running torque ' M ' prevents that eccentric adjusting sleeve 120 and key member 130 are disengaged, and have improved the stability of compressor of the present invention thus.Although only described the content that balancer weight 127 combines with first embodiment's key member 130, this balancer weight 127 also can together be used with second embodiment's key member 230.

Those skilled in the art can carry out various modifications and changes to double-volume compressor of the present invention obviously as can be known under the situation that does not break away from the spirit or scope of the present invention.Therefore, for those fall in claims and the equivalent scope thereof to modification of the present invention and change, the present invention will protect without exception.

Industrial applicibility

Multi-contact between eccentric adjusting sleeve and the key member in running is so that key member is safe Ground blocks crankpin and eccentric adjusting sleeve. Therefore, no matter have inside or external cause, all Can prevent relative motion between eccentric adjusting sleeve and the crankpin, thus so that compressor do not appointing Stable operation in the situation of what exporting change. That is to say, owing to kept fixing eccentricity And obtained fixing compression volume. In addition, also prevent from causing owing to relative motion, Friction loss between crankpin and the eccentric adjusting sleeve. At last, such stable operation is so that double volume The efficient of capacity compressor increases. In addition, can also prevent the noise owing to caused by relative motion, And the service life of elongated component.

In addition, variation has taken place in jammed part between key member and eccentric adjusting sleeve at first, Perhaps the center of gravity of eccentric adjusting sleeve is offset owing to balance is heavy. Therefore, even eccentric bushing Before tube was blocked well by key member, eccentric adjusting sleeve can be in centrifugal force and turning moment yet Effect is lower rotates. Therefore key member can be very well and is stably blocked eccentric adjusting sleeve, Increase thus the stability of compressor.

By the suitably movement of limit key parts under centrifugal action of use elastic component, this Bright compressor can avoid using too much part to realize this function. Therefore, structure of the present invention Make the simplification that becomes in fact, assembling becomes easily, thereby has improved productivity ratio.

Claims

1. double-volume compressor comprises:

Power generating part spare, it comprises the bent axle in reversing motor and this motor of insertion;

Compression member, it comprises cylinder body, the piston in this cylinder body and the connecting rod that links to each other with this piston;

Crankpin, this crankpin is positioned at the top of bent axle, and the eccentric axis of relative bent axle;

Eccentric adjusting sleeve, the interior perimeter surface of this eccentric adjusting sleeve are installed in rotating mode on the outer surface of crankpin, and the outer surface of this eccentric adjusting sleeve is installed to an end of connecting rod in rotating mode;

Key member, it is constructed such that key member remains at least a portion of eccentric adjusting sleeve, and also remains on this eccentric adjusting sleeve when operation, so that all rigidly eccentric adjusting sleeve and crankpin are blocked on all sense of rotation of motor; And

Thus, rearrange eccentric adjusting sleeve by variation and provide different compression volumes with amount of piston displacement, and in fact how the sense of rotation of motor all to prevent crankpin and the relative movement of eccentric adjusting sleeve when moving by key member to change effective eccentricity along with the motor sense of rotation.

2. double-volume compressor as claimed in claim 1, wherein, key member blocks eccentric adjusting sleeve at the multiple spot place.

3. double-volume compressor as claimed in claim 1, wherein, key member locates to block eccentric adjusting sleeve at 2 that are provided with in any direction with respect to center line when operation.

4. double-volume compressor as claimed in claim 1, wherein, the length of key member is greater than the external diameter of crankpin.

5. double-volume compressor as claimed in claim 1, wherein, key member remains at least a portion that relatively is positioned the bent axle radially inner side of eccentric adjusting sleeve.

6. double-volume compressor as claimed in claim 1, wherein, key member comprises:

First protuberance is used for being projected into all the time and exceeds one section predetermined length of crankpin; And

Second protuberance is used for only being projected into when operation exceeding one section predetermined length of crankpin.

7. double-volume compressor as claimed in claim 6, wherein, first protuberance is outstanding to radially inner side all the time.

8. double-volume compressor as claimed in claim 1, wherein, key member prevents the rotation that eccentric adjusting sleeve is subjected to centrifugal force and is taken place by the effect of the running torque of its generation.

9. double-volume compressor as claimed in claim 1, wherein, key member remains at least a portion of eccentric adjusting sleeve, makes that thus the direction of the running torque that eccentric adjusting sleeve produced is opposite with the sense of rotation of bent axle.

10. double-volume compressor as claimed in claim 1, wherein, key member remains at least a portion that relatively is positioned the bent axle radial outside of eccentric adjusting sleeve.

11. double-volume compressor as claimed in claim 1, wherein key member comprises:

First protuberance is used for being projected into all the time and exceeds crankpin; And

Second protuberance is used for being projected into all the time and exceeds crankpin, and remains on the eccentric adjusting sleeve when compressor operating.

12. double-volume compressor as claimed in claim 1, wherein, first protuberance is outstanding towards the bent axle radial outside.

13. double-volume compressor as claimed in claim 11, wherein, second protuberance is projected into and exceeds crankpin, make second protuberance when compressor is static not with the eccentric adjusting sleeve interference.

14. double-volume compressor as claimed in claim 11, wherein, second protuberance comprises and is used for groove that eccentric adjusting sleeve is passed through.

15. double-volume compressor as claimed in claim 1, wherein key member comprises the retainer that moves that is used for the limit key parts that is positioned at crankpin.

16. double-volume compressor as claimed in claim 15, wherein retainer has the contact surface that contacts crankpin that shape and the interior perimeter surface of crankpin match.

17. double-volume compressor as claimed in claim 15, wherein retainer is to be used for first retainer that the limit key parts move along a direction.

18. double-volume compressor as claimed in claim 17, wherein retainer also comprises and is used for second retainer that the limit key parts move in opposite direction.

19. double-volume compressor as claimed in claim 15, wherein key member also comprises elastic component, and this elastic component is used to support key member, makes the running state of key member compressor how all have at least a portion to be projected into all the time and exceeds crankpin.

20. double-volume compressor as claimed in claim 19, wherein elastic component limit key parts moving along a direction.

21. double-volume compressor as claimed in claim 19, wherein the elastic force of elastic component is inhomogeneous.

22. double-volume compressor as claimed in claim 19, wherein the elastic force of the part of elastic component is relatively greater than the elastic force of another part.

23. double-volume compressor as claimed in claim 19, wherein the elastic force of the part of elastic component is greater than centrifugal force that key member produced.

24. double-volume compressor as claimed in claim 19, wherein elastic component comprises:

First elastic component that contacts with key member; And

With second elastic component that perimeter surface in first elastic component and the crankpin contacts respectively, its elastic force is greater than first elastic component.

25. double-volume compressor as claimed in claim 24, wherein the elastic force of second elastic component is greater than the centrifugal force of key member generation.

26. double-volume compressor as claimed in claim 24, wherein first elastic component is the spring with predetermined diameter, and second elastic component is the spring of first elastic component of continuing, and its diameter is greater than first elastic component.

27. double-volume compressor as claimed in claim 1, wherein crankpin comprises a pair of key member mating part respect to one another.

28. double-volume compressor as claimed in claim 27, wherein the key member mating part of crankpin is the through hole on the crankpin wall.

29. double-volume compressor as claimed in claim 27, wherein the key member mating part in the crankpin comprises at least one groove that reaches a position of this wall from the top of crankpin wall.

30. double-volume compressor as claimed in claim 1, wherein eccentric adjusting sleeve comprises:

Along the rail portion that the bearing of trend of eccentric adjusting sleeve main body itself forms, be used to make the protuberance of key member to rotate; And

The restricted part that relative orbit partly forms is used for the rotation of the protuberance of limit key parts.

31. double-volume compressor as claimed in claim 30, wherein the rail portion of eccentric adjusting sleeve is to play the cut part of desired depth along extending circumferentially from the top of eccentric adjusting sleeve.

32. double-volume compressor as claimed in claim 30, wherein the step between rail portion and the restricted part is parallel to the plane at the longitudinal axis place of the longitudinal axis of bent axle and crankpin.

33. double-volume compressor as claimed in claim 30, wherein said step separate a half thickness of key member respectively with the plane at the longitudinal axis place of the longitudinal axis of bent axle and crankpin.

34. double-volume compressor as claimed in claim 30, wherein step with a half thickness of the angled mode tilt key parts in the plane, longitudinal axis place of the longitudinal axis of bent axle and crankpin.

35. double-volume compressor as claimed in claim 1, wherein eccentric adjusting sleeve also comprises the ring-shaped article that is arranged between eccentric adjusting sleeve bottom surface and the bent axle top surface.

36. as the described double-volume compressor in one of claim 1 or 30, wherein eccentric adjusting sleeve also comprises balancer weight, and this balancer weight prevents being disengaged of the eccentric adjusting sleeve that caused because of rotation and key member by the center of gravity of skew eccentric adjusting sleeve before key member blocks eccentric adjusting sleeve well.

37. double-volume compressor as claimed in claim 36, wherein balancer weight prevents that by running torque eccentric adjusting sleeve from rotating.

38. double-volume compressor as claimed in claim 36, wherein balancer weight prevents that eccentric adjusting sleeve from producing running torque.

39. double-volume compressor as claimed in claim 36, wherein balancer weight is positioned on the plane, longitudinal axis place of the longitudinal axis of bent axle and crankpin the center of gravity of eccentric adjusting sleeve.

40. double-volume compressor as claimed in claim 36, wherein balancer weight is rotated this eccentric adjusting sleeve along the direction that eccentric adjusting sleeve is engaged with key member.

41. double-volume compressor as claimed in claim 36, wherein balancer weight produces running torque along the direction opposite with sense of rotation.

42. double-volume compressor as claimed in claim 36, wherein the balancer weight centre-of gravity shift that makes eccentric adjusting sleeve is to the relative position about the plane, longitudinal axis place of the longitudinal axis of bent axle and crankpin.

43. double-volume compressor as claimed in claim 36 wherein is provided with balancer weight on the lighter relatively part of eccentric adjusting sleeve.

44. double-volume compressor as claimed in claim 36, wherein the rail portion at eccentric adjusting sleeve is provided with balancer weight.