CN1329658C - Double-volume compressor - Google Patents

Abstract

A dual capacity compressor. It includes a power part composed of a motor and a crankshaft inserted into the motor; a compression part composed of a cylinder, a piston and a connecting rod; a crank pin located at the upper end of the crankshaft and formed eccentrically; The peripheral surface and the outer peripheral surface that is combined with the rotation of the end of the connecting rod, and rearranged according to the direction of rotation of the motor, thereby changing the effective eccentricity between the crank pin and the connecting rod; The fixing part that holds the eccentric sleeve to the crank pin during clockwise or counterclockwise rotation. The present invention combines the crank pin and the eccentric sleeve by means of a fixing part inserted into the eccentric sleeve, thereby preventing the relative movement between the two, not only reducing friction loss, but also improving the efficiency of the compressor , and eliminate the noise generated during relative rotation and prolong the life of each component.

Description

dual capacity compressor

technical field

The invention relates to a compressor, in particular to a double-capacity compressor capable of changing the compression capacity of the compressor as required.

Background technique

The dual-capacity compressor is a reciprocating compressor that uses a rotatable eccentric sleeve connected to the crankpin of the crankshaft to change the piston stroke and compression capacity according to the rotation direction of the motor and the crankshaft. Dual capacity compressors can adjust the compression capacity according to the required load size. Therefore, it is widely used in many devices that need to compress the working fluid, especially in refrigerators and other household appliances that use refrigeration cycle systems.

US Patent No. 4,236,874 discloses a dual-capacity compressor with such a structure. Fig. 1 is a transverse cross-sectional view of the structure of a prior art dual-capacity compressor. Fig. 2 is a schematic diagram of the working state of the dual-capacity compressor in Fig. 1 . As shown in Fig. 1, the main parts of the dual capacity compressor include the piston 7 inside the cylinder 8, the crankshaft 1, the crankpin 3 formed eccentrically with the center 1a of the crankshaft 1, the eccentric ring 4 combined with the crankpin 3 and the connecting eccentric Ring 4 and connecting rod 6 of piston 7. Both the eccentric ring 4 and the connecting rod 6 rotate around the center 3 a of the crank pin 3 as a rotation center. A release area 9 with a certain length is provided on a certain section of the contact surface between the crank pin 3 and the eccentric ring 4 . The pin 5 connecting the crank pin 3 and the eccentric ring 4 is located in the release area 9 . As shown in Fig. 2, the eccentricity will change with the state of the eccentric ring 4, so the stroke distance of the piston 7 can be adjusted. When a large load is required, the crankshaft 1 rotates clockwise, and when a small load is required, the crankshaft 1 rotates counterclockwise. A in Fig. 2 represents the state where the piston 7 is at the top dead center during clockwise rotation, and B in Fig. 2 represents the state where the piston 7 is at the bottom dead center during clockwise rotation. In both cases, the amount of eccentricity reaches Maximum, so the travel distance Lmax also reaches the maximum value. C in Fig. 2 represents the state where the piston 7 is at the bottom dead center during counterclockwise rotation, and D in Fig. 2 represents the state where the piston 7 is at the top dead center during counterclockwise rotation. In both cases, due to the eccentricity Reach the minimum, so the travel distance Lmin also reaches the minimum value. However, during the above-mentioned working process, when the crank pin 3 and the eccentric ring 4 rotate relatively around the center 1a of the crankshaft 1, a centrifugal force acts on the crank pin 3 and the eccentric ring 4, and the direction of the centrifugal force is the center 1a of the crankshaft 1. and the extension line between the center 3 a of the crank pin 3 and the extension line between the center 1 a of the crankshaft 1 and the center of gravity 4 a of the eccentric ring 4 . Due to the different acting directions of the centrifugal force, states C and D in Fig. 2 are different from states A and B in Fig. 2 . In the states of C and D in Fig. 2, the directions of the respective forces are inconsistent, so that a local moment equal to the vertical distance d between the direction of the centrifugal force and the center 3a of the crank pin 3 multiplied by the centrifugal force is generated on the eccentric ring 4, And the direction of action of this moment is the same as the direction of rotation of the crankshaft 1 . Since the crank pin 3 and the eccentric ring 4 are parts that are separated from each other and can rotate relative to each other, this moment exerts a rotational force along the rotation direction of the crankshaft 1 , thereby squeezing the pin 5 from the crank pin 3 and the eccentric ring 4 . Therefore, as shown by the dotted line in Figure 3, the crank pin 3 and the eccentric ring 4 will move in the direction of rotation, and during the clockwise rotation, the re-expansion pressure P of the working fluid in the cylinder after the compression process will also push the eccentric ring 4. Make the eccentric ring 4 rotate in the direction of rotation of the crankshaft 1 to cause relative rotation between the eccentric ring 4 and the crank pin 3, so that the working process of the compressor will be unstable and the required compression effect will not be obtained. In fact, the pin 5 does not fully fix the crank pin 3 and the eccentric ring 4, so that the above-mentioned relative rotation ensues. Also, whenever the direction of rotation of the compressor is changed, the pin 5 rolls in the release area 9, so its life is shortened due to severe wear on the contact surfaces.

US Patent No. 4,479,419 also discloses a dual capacity compressor utilizing a crank pin, eccentric cam and pin. The pin is attached to an eccentric cam that moves along a track formed on the crank pin when the direction of rotation of the compressor changes. However, as in the case of the aforementioned U.S. Patent No. 4,479,419, the pin cannot fully restrain the crank pin and the eccentric cam, so relative rotation occurs accordingly, making the working process of the compressor unstable, and the desired compression effect cannot be obtained .

Contents of the invention

In order to solve the above-mentioned problems, an object of the present invention is to provide a dual-capacity compressor capable of maintaining a certain amount of eccentricity even when the compressor is rotated in any direction while changing the compression capacity, so that it can operate stably.

In order to achieve the above object, the dual-capacity compressor of the present invention includes a power part composed of a motor that can rotate clockwise or counterclockwise and a crankshaft inserted into the motor; A compression part composed of connecting rods; a crank pin located at the upper end of the crankshaft and deviated from the center of the crankshaft; an inner peripheral surface rotatably combined with the outer peripheral surface of the crank pin and an outer peripheral surface rotatably combined with the end of the connecting rod, and according to The rotation direction of the motor is rearranged, thereby changing the effective eccentricity between the crank pin and the connecting rod; and the eccentric sleeve located in the crank pin, which connects the eccentric sleeve to the crank during the clockwise or counterclockwise rotation of the motor. Fixed parts with pins fully secured.

Said crank pin includes a fixed part receiving part where a movable fixed part can be placed.

When the crank pin is a solid shaft, the shape of the fixed part placement part is a through hole formed along the radial direction of the solid shaft crankpin; when the crank pin is a hollow shaft, the shape of the fixed part placement part is a A pair of mounting holes are formed at corresponding positions in the body; moreover, the mounting part of the hollow crank pin also includes a groove extending from the predetermined position of the wall of the crank pin to the upper end.

The eccentric sleeve includes two grooves extending radially from the inner peripheral surface to the outer peripheral surface respectively, and the two grooves are correspondingly arranged on the extension line passing through the center of the crank pin and the center of gravity of the eccentric sleeve.

The fixed part is located inside the crank pin as a whole when it is at rest, and at least a part of it protrudes outside the crank pin during operation, and then coincides with the eccentric sleeve; the length of the fixed part is smaller than the diameter of the crank pin, and its end face shape is circular One of polygons such as , quadrilateral or hexagon.

The fixing part is a linear pin protruding outside the crank pin along the acting direction of the centrifugal force inside the solid shaft crank pin.

The fixing part includes a first protruding part that can protrude outside the crank pin along the direction of centrifugal force during operation; the protrusion; and a stop member capable of limiting the length of the second protrusion, thereby preventing the second protrusion from protruding outside the crank pin.

The contact surface of the stopper part with the crank pin should be consistent with the inner peripheral surface of the crank pin.

The dual-capacity compressor also includes an elastic member that restores the protruding fixing member to the inside of the crank pin when the operation stops.

When using a straight pin fixing part, the elastic part is inserted into the groove of the eccentric sleeve, or inserted onto the first protrusion of the fixing part.

The dual-capacity compressor of the present invention combines the crank pin and the eccentric sleeve by using a fixing part inserted into the eccentric sleeve, thereby preventing relative movement between the crank pin and the eccentric sleeve, and not only reducing friction loss , and can also improve the efficiency of the compressor, and eliminate the noise generated during relative rotation and prolong the life of each component. The invention has simple structure and easy assembly, so the production efficiency can be improved.

Description of drawings

The dual-capacity compressor of the present invention will be described in detail below in conjunction with the accompanying drawings and specific embodiments. The same structures use the same names and the same symbols.

Fig. 1 is a transverse cross-sectional view of the structure of a prior art dual-capacity compressor.

Fig. 2 is a schematic diagram of the working state of the dual-capacity compressor in Fig. 1 .

Fig. 3 is a schematic diagram of the relative rotation process between the crank pin and the eccentric sleeve during the operation of the dual-capacity compressor in the prior art.

Fig. 4 is a longitudinal sectional view of the structure of the dual-capacity compressor of the present invention.

Fig. 5a is a longitudinal cross-sectional view of a partial structure of a dual-capacity compressor in the first embodiment of the present invention.

Fig. 5b is a transverse sectional view of a partial structure of the dual-capacity compressor in the first embodiment of the present invention.

Fig. 6a and Fig. 6b are transverse cross-sectional views of the working state of some structures when the crankshaft rotates clockwise in the first embodiment of the present invention.

Fig. 7a and Fig. 7b are transverse cross-sectional views of the working state of some structures when the crankshaft rotates counterclockwise in the first embodiment of the present invention.

Fig. 8a is a longitudinal sectional view of part of the structure of the second embodiment of the dual-capacity compressor of the present invention.

Fig. 8b is a cross-sectional view of part of the structure of the second embodiment of the dual-capacity compressor of the present invention.

Fig. 9a is a perspective view of the crank pin in the second embodiment of the dual-capacity compressor of the present invention.

Fig. 9b is a perspective view of the deformed state of the crank pin in Fig. 9a.

Fig. 10 is a transverse cross-sectional view of a deformed state of the fixing part arranged in the crank pin.

Fig. 11a and Fig. 11b are transverse cross-sectional views of the working state of some structures when the crankshaft rotates clockwise in the second embodiment of the present invention.

Fig. 12a and Fig. 12b are transverse cross-sectional views of the working state of some structures when the crankshaft rotates counterclockwise in the second embodiment of the present invention.

Detailed ways

As shown in Fig. 4, the dual-capacity compressor of the present invention is generally divided into a power part 20 located at the lower part of the compressor and generating and transmitting the required power; located at the upper side of the power part 20, and using the provided power to compress the work A fluid compression part 30 ; and a variable stroke part 40 that can connect the power part 20 and the compression part 30 and can change the compression capacity of the compression part 30 during operation. In order to prevent leakage of the refrigerant, components such as the power unit 20 and the compression unit 30 are sealed in the container 11 . Inside the container 11 are installed a plurality of elastic brackets 12 for supporting components. Moreover, a refrigerant suction pipe 13 and a refrigerant discharge pipe 15 are provided at specific positions of the container 11 , and the refrigerant suction pipe 13 and the refrigerant discharge pipe 15 communicate with the inside of the container 11 . The power unit 20 is disposed on the lower side of the bracket 12 and is composed of a motor that generates rotational force from an external power source and includes a stator 21 and a rotor 22 , and a crankshaft 23 . The motor can rotate either clockwise or counterclockwise. The lower part of the crankshaft 23 is inserted into the inside of the rotor 22 to transmit power, and structures such as oil holes or oil grooves are provided for supplying lubricating oil placed on the lower side of the compressor to each driving part of the compressor. The compression part 30 is arranged on the bracket 12 on the upper side of the power part 20 . The compression unit 30 is composed of a driving member that mechanically moves to compress the refrigerant, and devices such as suction and discharge valves that assist the driving member. The driving member and the cylinder 32 forming the compression space also include a piston 31 that reciprocates inside the cylinder 32 for sucking/compressing refrigerant, and a connecting rod 33 that transmits power required for the reciprocating motion to the piston 31 . The valve composed of the cylinder head 34 and the top cover 35 and other related components can provide the cylinder 32 with refrigerant and discharge the compressed refrigerant. The variable stroke portion 40 includes a crank pin eccentrically formed on the upper end of the crankshaft; a rotatable eccentric sleeve installed between the outer peripheral surface of the crank pin and the connecting rod; and a fixing member capable of relatively fixing the crank pin and the eccentric sleeve. That is, in the present invention, the movable fixed part is installed in the crank pin, and its upper part can protrude to the outside of the crank pin due to centrifugal force during operation and be inserted into the eccentric sleeve. When the motor rotates clockwise or counterclockwise, the position of the eccentric sleeve will change accordingly, thereby changing the compression capacity of the compressor.

Example 1

Fig. 5a is a longitudinal cross-sectional view of a partial structure of a dual-capacity compressor in the first embodiment of the present invention. Fig. 5b is a transverse sectional view of a partial structure of the dual-capacity compressor in the first embodiment of the present invention. As shown in Fig. 5a and Fig. 5b, the dual-capacity compressor in the first embodiment of the present invention includes a crank pin 110 with a fixed part placement part 111; the rotating eccentric sleeve 120; and the fixing part 130 placed in the fixing part accommodating part 111. The crank pin 110 is a solid shaft, and an oil passage 112 and an oil supply hole 113 are provided at the lower part thereof. The fixing member receiving portion 111 extends radially through the center 110 a of the solid shaft type crank pin 110 , and further forms a through hole in which the fixing member 130 can be placed. Meanwhile, in order to make the fixing part 130 move flexibly, the diameter of the fixing part 111 should be slightly larger than the diameter of the fixing part 130 . One end of the oil passage 112 is connected to the oil groove formed outside the crankshaft 23 , and the other end is connected to the oil supply hole 113 . During the working process, the lubricating oil stored at the bottom of the compressor passes through the oil tank and the oil passage 112 in turn and enters the contact surface between the components, thereby preventing the wear and tear between the components and making the compressor work more flexibly . Also, lubricating oil can be directly supplied between the crank pin 110 and the eccentric bush 120 through the oil supply hole 113 . In addition, the crank pin 110 is higher than the eccentric bush 120, so that the lubricating oil can be scattered at a high place, so that it can be uniformly supplied to each driving part. The inner peripheral surface of the eccentric sleeve 120 is rotatably engaged with the outer peripheral surface of the crank pin 110 , and its outer peripheral surface is combined with the end of the rotatable connecting rod 33 . The pair of grooves 121 and 122 of the eccentric sleeve 120 are formed by extending radially from the inner peripheral surface to the outer peripheral surface to a certain depth. That is, a pair of grooves 121, 122 are provided via the center of gravity of the eccentric sleeve 120 itself and the corresponding position on the extension line of the center 110a of the crank pin 110, that is to say, the grooves 121, 122 are correspondingly arranged at the maximum thickness of the eccentric sleeve 120 part and minimum thickness part. In this way, during the working process, the crank pin 110 can be fixed by the slots 121, 122 and the fixing member 130, so that the correct maximum and minimum eccentricity can be maintained. More importantly, the grooves 121, 122 and the fixing part receiving part 111 must be aligned in order to insert the fixing part 130 correctly. The fixing part 130 in this embodiment has a linear structure that can be placed in the fixing part accommodating part 111 . When the rotation direction of the compressor is changed, the eccentric sleeve 120 rotates around the crank pin 110 in order to change the eccentricity amount. In order not to hinder the rotation of the eccentric sleeve 120, the length of the fixed part 130 is smaller than the diameter of the crank pin 110, so that any end of the fixed part 130 can not protrude beyond the outer peripheral surface of the crank pin 110 when the working process stops like this. Moreover, in the present invention, the end surface of the fixing member 130 is circular, and it can also be made into a quadrangular or hexagonal shape, as long as it can be inserted into a pair of grooves 121, 122. Due to the above-mentioned structure, the fixed part 130 is located in the crank pin 110 when it is at rest, and is in contact with the eccentric sleeve 120 during operation, that is, at least a part of it protrudes to the outside of the crank pin 110, so as to be in contact with the pair of grooves 121, One of the slots 122 is in contact and its protruding length is limited by the closed ends of the slots 121,122. Moreover, the first embodiment of the present invention further includes an elastic member 140 disposed in the pair of grooves 121, 122, which restores the protruding fixing member 130 to the inside of the crank pin 110 when the operation is stopped.

Fig. 6a and Fig. 6b are transverse cross-sectional views of the working state of some structures when the crankshaft rotates clockwise in the first embodiment of the present invention. Fig. 7a and Fig. 7b are transverse cross-sectional views of the working state of some structures when the crankshaft rotates counterclockwise in the first embodiment of the present invention. Figure 6a shows the relative position between the fixed member 130 and the eccentric sleeve 120 when the crankshaft 23 starts to rotate clockwise. When the crankshaft 23 starts to rotate, the eccentric sleeve 120 between the crank pin 110 and the connecting rod 33 also rotates thereupon. As shown in Fig. 6b, it moves along the acting direction of the centrifugal force F, that is, along the extension line between the crankshaft center 23a and the crankpin center 110a. Accordingly, the fixing member 130 is inserted into the thick-walled side groove 121, so that the crank pin 110 and the eccentric bush 120 can be completely fitted into each other. Therefore, for clockwise rotation, the external force P or other forces generated by the re-expansion of the working fluid after the compression process are transmitted through the connecting rod 33, so that the fixing part can effectively prevent the crank pin 110 and the eccentric sleeve from rotating. 120, and can also prevent the rotation relative to the crank pin 110 due to the local rotational moment generated on the eccentric sleeve 120. Not only that, as shown in Figure 6b, the solid line part in the figure represents the state of the top dead point, and the dotted line part represents the state of the bottom dead point, which is the maximum eccentricity of the eccentric sleeve 120 in the case of clockwise rotation. At this time, The piston reciprocates with the maximum stroke length Lmax, so that the compressor reaches the maximum compression capacity. In addition, the crankshaft 23 needs to stop for a period of time before rotating counterclockwise. At this time, the elastic force will be greater than the centrifugal force, so the elastic member 140 will recover elastically, so that the fixing member 130 returns to the fixing member placement portion 111 of the crank pin 110. Then, the crankshaft 23 and the crank pin 110 integrated with it start to rotate counterclockwise, and at this time, the eccentric sleeve 120 will move counterclockwise between the crank pin 110 and the connecting rod 33, thereby being arranged as shown in FIG. 7a status. Same as above clockwise rotation, when the rotational speed reaches a certain value, as shown in FIG. 7 b , due to the centrifugal force F, the fixing member 130 will protrude, thus matching with the thin-walled side groove 122 . Therefore, the crank pin 110 and the eccentric bush 120 are fixed by the fixing member 130 . Thus, for counterclockwise rotation, the securing member prevents relative movement between the crank pin 110 and the eccentric sleeve 120 even if the working fluid exerts a pressure P on the piston during compression or other forces exist. At this time, as shown in FIG. 7 b , when the eccentric sleeve 120 rotates counterclockwise, the eccentric sleeve 120 will have the minimum eccentricity, so that the compression capacity of the compressor is minimum.

Example 2

Fig. 8a is a longitudinal sectional view of part of the structure of the second embodiment of the dual-capacity compressor of the present invention. Fig. 8b is a cross-sectional view of part of the structure of the second embodiment of the dual-capacity compressor of the present invention. Fig. 9a is a perspective view of the crank pin in the second embodiment of the dual-capacity compressor of the present invention. Fig. 9b is a perspective view of the deformed state of the crank pin in Fig. 9a. Fig. 10 is a transverse cross-sectional view of a deformed state of the fixing part arranged in the crank pin. As shown in Fig. 8a, Fig. 8b, Fig. 9a, Fig. 9b and Fig. 10, the double capacity compressor in the second embodiment of the present invention includes a crank pin 210 with a fixed part placement part 211; installed outside the crank pin 210, and A rotatable eccentric sleeve 220 provided with a pair of grooves 221 , 222 ; and a fixing member 230 placed in the fixing member seating portion 211 . The crank pin 210 is a hollow shaft, and a pair of mounting holes 211a, 211b are correspondingly provided on its wall. The lower part of the crank pin 210 is also provided with the same oil passage 212 and oil supply hole 213 as in the first embodiment. The placement holes 211a, 211b are located on the extension line between the crankshaft center 23a and the crankpin center 210a, and are located in the same plane. Therefore, the fixing member 230 whose two ends can be respectively inserted into the mounting holes 211a, 211b will be affected by the centrifugal force along its own length and acting on the extension line between the crankshaft center 23a and the crankpin center 210a. Moreover, the fixing part 230 can move in the fixing part receiving part 211 . The placement holes 211a and 211b are in the shape of through holes. And as shown in Figure 9b, at least one of the mounting holes 211a, 211b is a mounting groove 211d extending from the upper end of the crank pin 210 wall body to a predetermined position, so that the fixing member 230 can be easily put into the hollow crank pin 210 . Moreover, in order to place the fixing member 230 more safely, a position portion 211c is formed at the end of the receiving groove 211d. The eccentric sleeve 220 is provided with a pair of slots 221 , 222 into which the fixing component 230 can be inserted. The eccentric sleeve 220 is the same as the eccentric sleeve 120 in the first embodiment. As shown in Figure 8b, the fixing part 230 includes a first protrusion 231 that can protrude outside the crank pin 210 during operation; it is located on the reverse extension line of the first protrusion 231, and is always located at the crank pin 210 during operation. the inner second protruding portion 232; and the stop member 233 that can limit the protruding length of the second protruding portion 232. Actually, the first protruding portion 231 is disposed inside the crank pin 210 away from the center 23a of the crankshaft 23 in order to receive the centrifugal force to the maximum. Relatively speaking, the second protrusion 232 adjoins the center 23a of the crankshaft 23 . That is, the first protruding portion 231 can protrude from the fixing part receiving portion 211 to the outside under the centrifugal force generated during the rotation, and then be inserted into any one of the slots 221 , 222 . In order to restore the protruding fixing member 230 when the work is stopped, an elastic member 240 is installed on the first protruding portion 231 . Actually the elastic member 240 is located between the stop member 233 and the inner wall of the crank pin 210 . Moreover, in order not to hinder the rotation of the eccentric sleeve 220 which can change the eccentricity, the length of the first protruding part 231 should be set so that its end does not protrude to the outer peripheral surface of the crank pin 210 when the operation is stopped. In addition, in order to prevent the fixing member 230 from detaching from the crank pin 210 regardless of the working state of the compressor, the second protruding portion 232 is always located in the placement hole 211a. Therefore, the stopper 233 can limit the length of the second protrusion 232 protruding to the outside of the crank pin 210, and the elastic member 240 elastically supports the stopper 233 together with the inner wall of the crank pin 210, so that the direction of the second protrusion 232 can be limited. The crank pin 210 moves in the center direction. As shown in FIG. 10 , the stop member 233 may further include a contact surface 233 a consistent with the inner peripheral surface of the crank pin 210 and a receiving portion 233 b of the elastic member 240 . The contact surface 233a and the receiving portion 233b can make the fixing member 230 work stably. Moreover, the stopper 233 can also be integrally formed with the fixing member 230 .

Fig. 11a and Fig. 11b are transverse cross-sectional views of the working state of some structures when the crankshaft rotates clockwise in the second embodiment of the present invention. Fig. 12a and Fig. 12b are transverse cross-sectional views of the working state of some structures when the crankshaft rotates counterclockwise in the second embodiment of the present invention. As shown in FIG. 11 a , FIG. 11 b , FIG. 12 a and FIG. 12 b , when the crankshaft 23 starts to rotate clockwise, the centrifugal force F will act on the fixing member 230 . When the rotational speed reaches a certain value, the centrifugal force F will overcome the elastic force of the elastic member 240. Therefore, the eccentric sleeve 220 is arranged in a state as shown in FIG. Constraints on the inner peripheral surface of the barrel 220 are then inserted into the thick-walled side groove 221 as shown in FIG. 11b. When rotating counterclockwise, as shown in FIG. 12 a and FIG. 12 b , the first protruding portion 231 is inserted into the thin-walled side groove 222 through the same rotation process as in the clockwise direction. In addition, when the direction of rotation is changed, because the elastic force is greater than the centrifugal force, the elastic member 240 can push the stop member 233 toward the inner wall of the crank pin 210, so that the first protruding portion 231 returns to the fixed member receiving portion 211 of the crank pin 210. . Therefore, the crank pin 210 and the eccentric bush 220 can be completely fixed to each other. Therefore, for clockwise or counterclockwise rotation, the compressor of the present invention can prevent the relative friction between the crank pin 210 and the eccentric sleeve 220 even if the pressure P or other forces exerted by the working fluid on the piston during the compression process exist. movement, while also preventing relative movement between the crank pin 210 and the eccentric sleeve 220 when a local rotational moment is generated in the eccentric sleeve 220 . In this way, the compressor of the present invention can maintain the maximum and minimum compression capacity under any working state, and can work stably.

Claims (16)

1, a kind of double-volume compressor comprises by clockwise rotating the motor that also can rotate counterclockwise and being inserted into the power part (20) that the bent axle (23) on the motor is formed; The press part of forming by piston (31) that is provided with in the cylinder (32), cylinder (32) and the connecting rod (33) that links to each other with piston (31) (30); Be positioned at the upper end portion of bent axle (23) and depart from the crank pin (110) that the center (23a) of bent axle (23) forms; Have with the outer circumferential face of crank pin (110) can rotate the inner peripheral surface that combines and and the outer circumferential face of the end rotation combination of connecting rod (33), and rearrange according to the sense of rotation of motor, change between crank pin (110) and the connecting rod (33) the effectively eccentric adjusting sleeve (120) of offset thus; It is characterized in that: described double-volume compressor also comprises and is positioned at crank pin (110), at motor clockwise direction or the fixed component (130) that counterclockwise eccentric adjusting sleeve (120) and crank pin (110) is completely fixed in the rotation process.

2, double-volume compressor according to claim 1 is characterized in that: described crank pin (110) comprises that the fixed component that can place mobile fixed component (130) lays portion (111).

3, double-volume compressor according to claim 2 is characterized in that: at crank pin (110) is under the real axis situation, and the shape that fixed component is laid portion (111) is the through hole that the radial direction along real axis type crank pin (110) forms.

4, double-volume compressor according to claim 2, it is characterized in that: at crank pin (210) is under the hollow shaft situation, and the shape that fixed component is laid portion (211) is a pair of placed hole (211a, 211b) that opposite position forms in crank pin (210) wall body.

5, double-volume compressor according to claim 4 is characterized in that: the fixed component of described hollow type crank pin (210) is laid portion (211) and is also comprised the groove (211d) that extends to the upside end from crank pin (210) wall body institute fixed position.

6, double-volume compressor according to claim 1 is characterized in that: described eccentric adjusting sleeve (220) comprises two grooves (221,222) that radially extend to outer circumferential face from inner peripheral surface respectively.

7, double-volume compressor according to claim 6 is characterized in that: described two grooves (221,222) are arranged on the elongation line of process crank pin (210) center (210a) and eccentric adjusting sleeve (220) center of gravity (220a) accordingly.

8, double-volume compressor according to claim 1, it is characterized in that: integral body was positioned at crank pin (110) when described fixed component (130) was static, and at least a portion is projected into crank pin (110) outside in the course of the work, and then and eccentric adjusting sleeve (120) coincide.

9, double-volume compressor according to claim 8 is characterized in that: the length of described fixed component (130) is less than the diameter of crank pin (110).

10, double-volume compressor according to claim 8 is characterized in that: the end surface shape of described fixed component (130) is a kind of in the polygonals such as circular, quadrilateral or Hexagon.

11, double-volume compressor according to claim 8 is characterized in that: described fixed component (130) is for being projected into the outside straight line type pin of crank pin (110) along the action of centrifugal force direction in real axis type crank pin (110).

12, double-volume compressor according to claim 8 is characterized in that: described fixed component (230) comprises in the course of the work can be projected into outside first protuberance (231) of crank pin (210) along the action of centrifugal force direction; In the reverse formation of first protuberance (231), and be positioned at second protuberance (232) of placed hole (211a) in the course of the work all the time; With the length that can limit second protuberance (232), thereby prevent that second protuberance (232) is projected into the outside stop component (233) of crank pin (210).

13, double-volume compressor according to claim 12 is characterized in that: described stop component (233) upward should be consistent with the inner peripheral surface of crank pin (210) with the surface of contact of crank pin (210).

14, double-volume compressor according to claim 1 is characterized in that: described double-volume compressor also comprises allows outstanding fixed component (230) reset into the inner elastic member (240) of crank pin (210) when work stops.

15, double-volume compressor according to claim 14 is characterized in that: when using the fixed component (130) of straight line type pin, elastic member (140) are inserted in the groove (121,122) of eccentric adjusting sleeve (120).

16, double-volume compressor according to claim 14 is characterized in that: described elastic member (240) is inserted on first protuberance (231) of fixed component (230).

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