Compressor structure

A compressor structure includes a vane rotor and a cylinder eccentrically disposed around the vane rotor. The vane rotor has a vane impeller. The vane impeller is in tangential contact with the cylinder to define an eccentric crescent vane chamber. A vane is radially slidably received in the vane impeller. An outward extending top end of the vane tightly abuts against the inner circumferential wall of the vane chamber, whereby the vane chamber is partitioned into an intake section and a compression exhaustion section. When the vane rotor rotates, the vane is driven to drive the cylinder to complete gas compression operation. When rotating, the vane is simply swung at a fixed position of the cylinder, the friction of the compressor can be lowered. The communication of the gas outlet is regulated so that the compression ratio of the compressed gas exhausted from the compressor can be changed.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates generally to a compressor structure, and more particularly to a compressor structure, which can reduce the frictional wear between the vane impeller and the inner circumference of the vane chamber. Moreover, the compression ratio of the compressor can be adjusted as necessary and the compressor can be switched between different compression ratios or diverse functions such as a pump. Therefore, the compressor structure has highly practical value.

2. Description of the Related Art

As shown inFIG.1, a conventional rotary vane compressor mainly includes a cylinder7and a vane rotor8. The cylinder7is formed with an internal vane chamber71with a circular cross section. A gas outlet72and a gas inlet73are disposed on a circumference of the vane chamber71in communication with outer side. The vane rotor8is eccentrically disposed in the vane chamber71between the gas outlet72and the gas inlet73near one side of the gas outlet72and one side of the gas inlet73. Multiple vanes80are radially telescopically disposed on outer circumference of a vane impeller81of the vane rotor8. Each vane80has an outward extending end801, which always abuts against an inner wall710of the vane chamber71. In a preferred embodiment, the cylinder7is retained in a main body70.

In operation, when the vanes80pass through the gas inlet73, the gas entering the vane chamber71through the gas inlet73between two adjacent vanes80is gradually pushed toward the gas outlet72. The capacity of the vane chamber71between two adjacent vanes80is gradually reduced so that the gas passing through the vane chamber71between two adjacent vanes80is compressed into high-pressure gas. Thereafter, the gas passes through the gas outlet72to be guided out, whereby the air compression operation is completed.

However, in operation of the above compressor, the vanes80and the vane impeller81always frictionally slide against the inner wall710of the vane chamber71. This leads to continuous wear loss between the vanes80and the vane impeller81and the inner wall710of the vane chamber71. As a result, not only a great amount of energy is lost, but also high heat is generated due to friction, it is hard to dissipate the heat so that the use performance and durability and lifetime of the product are seriously affected.

In the above arrangement, the gas outlet72and the gas inlet73of the vane chamber71have fixed positions so that in operation of the vanes80and the vane impeller81, the vanes80and the vane impeller81will both apply frictional force to the fixed contact portion7101of the inner wall710of the vane chamber71. The longer the compressor is used, the more apparent the denting extent caused by the wear of the fixed contact portion7101is. In operation, when the vanes80pass through the dented portion, the vanes80will jump or shake. This seriously affects the airtightness and quietness during the operation process and should be improved.

Furthermore, the conventional rotary vane compressor structure simply has gas compression function and can only compress air by fixed compression ratio without possibility of easy regulation or change of the compression ratio. This seriously limits the practical application range provided by the compressor.

It is therefore tried by the applicant to provide a compressor structure to eliminate the shortcomings existing in the conventional rotary vane compressor.

SUMMARY OF THE INVENTION

It is therefore a primary object of the present invention to provide a compressor structure including a vane rotor and a cylinder eccentrically disposed around the vane rotor and pivotally rotatably disposed on a main seat. The vane rotor has a vane impeller. A circumferential wall of the vane impeller is in tangential contact with an inner circumferential wall of the cylinder to define an axial partitioning line and form an eccentric crescent vane chamber in the cylinder. A radial vane slot is formed on the circumference of the vane impeller of the vane rotor. A vane is slidably received in the vane slot. An outward extending top end of the vane has vane pivotally connecting sections, which are securely pivotally connected with two sides of the inner circumferential wall of the cylinder, whereby the top end of the vane tightly abuts against (or is inlaid in) the inner circumferential wall of the cylinder to partition the interior of the vane chamber into an intake section and a compression exhaustion section. The intake section is in communication with a gas inlet. The compression exhaustion section is in communication with a gas outlet. When the vane rotor rotates, the vane is driven by the vane rotor. At the same time, the vane pivotally connecting sections of the vane drive the cylinder to rotate with the vane rotor so as to take gas from the gas inlet into the vane chamber. After compressed, the gas is exhausted from the gas out let to complete gas compression operation. When the cylinder is driven by the vane to rotate, the vane pivotally connecting sections of the vane are limited by the eccentrically rotational track of the cylinder relative to the vane rotor so that the vane simply tightly abuts against (or is inlaid in) a fixed position of the inner circumferential wall of the cylinder and swings about the fixed position. Therefore, during the compression process, the vane will not be retracted back into the vane slot due to excessively great pressure of the internal gas to make a gap. In addition, the vane will not frictionally contact any other part of the inner circumferential wall of the vane chamber. Also, the vane rotor is eccentrically tangential to the cylinder and rotated along therewith so that the friction between the vane rotor and the cylinder in each cycle of rotation is simply equivalent to the sliding friction of the difference between the circumferential lengths of the vane rotor and the cylinder in contact with each other. This can effectively reduce the wear of the components of the entire compressor and the loss of energy.

In the above compressor structure, two support bodies are respectively disposed on two lateral sides of the main seat. At least one automatic adjustment assembly is disposed between the support bodies and the main seat. The automatic adjustment assembly is used to make the inner circumferential wall of the cylinder always tightly abut against the circumferential wall of the vane impeller of the vane rotor so as to automatically adjust and eliminate the gap between the inner circumferential wall of the cylinder and the circumferential wall of the vane impeller of the vane rotor.

In the above compressor structure, in the case that the gas outlet is disposed on the cylinder, an out-guiding hole can be disposed on one side of the main seat to set up the overlapping position of the gas out let and the out-guiding hole in rotation of the cylinder. The initial overlapping position is exactly the compression ratio setting of the gas exhausted from the compressor. Alternatively, in the case that the gas outlet is disposed on the vane rotor, the gas outlet is in communication with at least one gas exhaustion port on a rotor shaft of the vane rotor via a gas exhaustion passage inside the vane rotor. A shaft end gas exhaustion control assembly is assembled with an end section of the rotor shaft with the gas exhaustion port. At least one out-guiding notch is disposed on the shaft end gas exhaustion control assembly so as to set up the overlapping position of the gas exhaustion port of the rotor shaft and the out-guiding notch of the shaft end gas exhaustion control assembly in rotation of the vane rotor. The initial overlapping position is exactly the compression ratio setting of the gas exhausted from the compressor.

In the above compressor structure, in the case that the gas outlet is disposed on the cylinder, a compression ratio regulation assembly can be additionally disposed between the out-guiding hole of the main seat and the gas outlet. Alternatively, in the case that the gas outlet is disposed on the vane rotor in communication with a gas exhaustion port on a rotor shaft, a compression ratio regulation assembly can be additionally disposed between the out-guiding notch of the shaft end gas exhaustion control assembly and the gas exhaustion port. The compression ratio regulation assembly has a regulation opening corresponding to the out-guiding hole or the out-guiding notch. When the compression ratio regulation assembly is operated to regulate the compression ratio, the initial overlapping position of the gas outlet and the out-guiding hole or the out-guiding notch can be adjusted and changed so as to change the timing for the gas outlet and the out-guiding hole or the out-guiding notch to communicate with each other and exhaust the gas. Accordingly, the effect of changing the exhaustion compression ratio of the compressed gas of one single compressor can be achieved.

In the above compressor structure, the shaft end gas exhaustion control assembly is composed of an end cap seat and an out-guiding notch control ring cap with an opening. A rotor shaft socket is formed at a center of the end cap seat and sealedly capped around the end section of the first rotor shaft corresponding to the position where the gas exhaustion port is formed. At least one through hole is formed on the end cap seat in communication with outer side and corresponding to the rotor shaft socket. A central hole is formed at a center of the rotor shaft socket through the end cap seat. An annular groove is formed on the other side of the end cap seat concentrically around the central hole and spaced from the central hole. A rim of the open end of the out-guiding notch control ring cap is inlaid in the annular groove. The rim of the out-guiding notch control ring cap that is inlaid in the annular groove is formed with at least one annular rail. At least one notch segment is disposed on the annular rail. Each notch segment has a notch part. The annular rail corresponds to the through hole and is positioned in the same axial position as the through hole. When the out-guiding notch control ring cap operates, each notch segment will pass through the through hole. Each time period for each notch segment to pass through the through hole just corresponds to one-cycle rotation of the vane rotor. Therefore, in one-cycle rotation of the out-guiding notch control ring cap, the corresponding number of the rotational cycles of the vane rotor is equivalent to the number of the notch segments set on the out-guiding notch control ring cap. Accordingly, the compression extent of the gas exhausted from the compressor is the set compression ratio of the notch segment passing through the through hole. Therefore, the operation of the compressor can be switched between the notch segments with different set compression ratios. In the case that the notch segment is set without compression, the entire notch segment is a notch. Under such circumstance, the compressor will functionally serve as a pump. Therefore, the compressor structure of the present invention can provide another special application.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Please refer toFIGS.2to7. According to a first embodiment, the compressor structure of the present invention includes a vane rotor1, a cylinder2and a main seat3. The vane rotor1has a cylindrical vane impeller10. A first rotor shaft11and a second rotor shaft12are respectively disposed at two ends of a center of the vane impeller10. In addition, a radial vane slot13is formed on the vane impeller10. At least one of the first rotor shaft11and the second rotor shaft12is formed with an internal ventilation passage131in communication with the vane slot13. At least one of the first rotor shaft11and the second rotor shaft12is connected to an external power supply via a transmission member15(such as a gear or a belt pulley) for driving the vane rotor1to rotate. A radially slidable vane14is received in the vane slot13. The vane14has an outward extending end extending out of the vane slot13. The outward extending end of the vane14is formed with vane pivotally connecting sections141. In this embodiment, the vane pivotally connecting sections141are two vane protruding shafts laterally protruding from two sides of the vane14.

The cylinder2is eccentrically disposed around the vane rotor1. The cylinder2is composed of a cylindrical cylinder main body20and a cylinder cap body21. The cylinder main body20is formed with an internal concentric cylindrical vane chamber202. The vane chamber202has an opening201on one side. The vane chamber202has an inner circumferential wall203. A circumference of the vane impeller10is tangential to the inner circumferential wall203of the vane chamber202at an axial partitioning line X to define a crescent vane chamber capacity space. The vane pivotally connecting sections141can be pivotally connected with two sides of the inner circumferential wall203of the vane chamber202, whereby a top end of the vane14tightly abut against the inner circumferential wall203of the vane chamber202(the cylinder main body20) along an axial vane contact line Y. In addition, on the circumferential wall of the cylinder main body20immediately in adjacency to two sides of the axial vane contact: line Y are formed a gas outlet204in an advancing direction of the vane14and a gas inlet205in a direction reverse to the advancing direction of the vane14. The gas outlet204and the gas inlet205are respectively positioned in different axial positions of the cylinder main body20. A shaft hole206is formed at a center of a sidewall of the cylinder main body20distal from the opening201. In addition, a vane pivotally connected section207is disposed on the sidewall immediately in adjacency to the inner circumferential wall203of the vane chamber202.

The opening201of the cylinder main body20is sealed by the cylinder cap body21. The cylinder cap body21is formed with a subsidiary shaft hole211corresponding to the shaft hole206of the cylinder main body20and a subsidiary vane pivotally connected section212corresponding to the vane pivotally connecting section207of the cylinder main body20. The vane pivotally connecting sections141of the vane14are respectively pivotally connected with the vane pivotally connecting section207and the subsidiary vane pivotally connected section212.

The main seat3is composed of a main seat main body30and a main seat subsidiary body31. A circular cylinder receiving chamber301is formed on one side of the main seat main body30, which side faces the cylinder2. The cylinder receiving chamber301has an opening300and serves to receive a lateral end of the cylinder main body20proximal to the gas outlet204. The other lateral end of the cylinder main body20proximal to the gas inlet205is exposed to outer side of the cylinder receiving chamber301. A shaft seat302is disposed at a center of a sidewall of the main seat main body30distal from the opening300. The shaft seat302is eccentric from a rotational center of the vane rotor1. The shaft seat203can be pivotally fitted in the shaft hole206of the cylinder main body20, whereby the cylinder main body20can pivotally rotate around the shaft seat302. In addition, an eccentric shaft hole303is formed on the shaft seat302of the main seat main body30. The cylinder receiving chamber301has a circular inner circumferential wall3011. An out-guiding hole305is formed between the inner circumferential wall3011and an outer wall304of the main seat main body30and positioned in adjacency to the axial partitioning line X.

A main seat subsidiary body31is disposed on one side of the cylinder receiving chamber301of the main seat main body30and directed to the cylinder2. The main seat subsidiary body31is spaced from the main seat main body30by the cylinder2. A subsidiary shaft seat311is disposed on one side of the main seat subsidiary body31corresponding to the shaft seat302of the main seat main body30, which sides faces the cylinder receiving chamber301. In addition, a subsidiary eccentric shaft hole312is formed on the subsidiary shaft seat311corresponding to the eccentric shaft hole303of the main seat main body30. The subsidiary shaft seat311can be pivotally fitted in the subsidiary shaft hole211, whereby the cylinder cap body21can pivotally rotate around the subsidiary shaft seat311.

It can be known from the above structural assembling relationship that the cylinder2is pivotally rotatable with the shaft seat302of the main seat main body30and the subsidiary shaft seat311of the main seat subsidiary body31serving as two rotary shafts on two sides. In order to make the cylinder2tightly rotate within the main seat3in a balanced state, assembling supports are disposed between the main seat main body30and the main seat subsidiary body31to securely assemble the main seat main body30and the main seat subsidiary body31with each other. As shown inFIG.2, in this embodiment, four connection supports306are disposed on the main seat main body30. Each connection support306is formed with a threaded hole3061. The main seat subsidiary body31is formed with four subsidiary body threaded holes313in positions corresponding to the four threaded holes3061. Accordingly, screws can be locked through the subsidiary body threaded holes313into the threaded holes3061of the connection supports306so as to securely assemble the main seat main body30and the main seat subsidiary body31with each other. In addition, a hollow section307is defined between the main seat main body30and the main seat subsidiary body31, whereby the gas inlet205is exposed to outer side through the hollow section307. The main seat main body30and the main seat subsidiary body31can be securely assembled by various other means, which will not be redundantly described hereinafter.

Please refer toFIGS.2to7. When the vane rotor1, the cylinder2and the main seat3are assembled with each other, the cylinder2is disposed in the cylinder receiving chamber301of the main seat3with the shaft seat302and the subsidiary shaft seat311of the main seat3pivotally fitted in the shaft hole206and the subsidiary shaft hole211. The first rotor shaft11and the second rotor shaft12of the vane rotor1are rotatably fitted in the eccentric shaft hole303and the subsidiary eccentric shaft hole312. The vane chamber202of the cylinder2is eccentrically positioned around the vane rotor1. The circumferential wall of the vane impeller10of the vane rotor1is in tangential contact with the inner circumferential wall203of the vane chamber202at the axial partitioning line X. In addition, the top end of the vane14cooperatively tightly abut against the inner circumferential wall203of the vane chamber202along the axial vane contact line Y. Accordingly, a compression exhaustion section2021in communication with the gas outlet204is formed on a front side of the vane14in a rotational advancing direction of the vane14and an intake section2022in communication with the gas inlet205is formed on a rear side of the vane14in a direction reverse to the rotational advancing direction of the vane14.

When the external power supply via the transmission member15drives the second rotor shaft12to make the vane rotor1rotate, the vane14in the vane slot13of the vane rotor1is driven and rotated along with the rotation of the vane rotor1. At this time, the vane pivotally connecting sections141of the vane14drive the vane pivotally connected section207and the subsidiary vane pivotally connected section212of the cylinder2, whereby the cylinder2is rotated around the shaft seat302and the subsidiary shaft seat311of the main seat3in the same rotational direction as the vane rotor1. However, the rotational axis of the cylinder2is eccentric from the rotational axis of the vane rotor1. At the same time, under the limitation of the pivotal connection track of the cylinder2, which is eccentrically rotated relative to the vane rotor1, the vane14is reciprocally telescopically slid within the vane slot13along with the rotation of the vane rotor1. When the vane14is reciprocally telescopically slid within the vane slot13, the vane14is swung with its top end always tightly abutting against a fixed position of the inner circumferential wall203of the cylinder2. Therefore, during the compression process, the vane14will not be retracted back into the vane slot13due to excessively great pressure of the internal gas to make a gap and lead to insufficient gas density.

In the above operation and driving process, when the vane14and the cylinder2are moved to the position as shown inFIG.6, the axial vane contact line Y defined by the vane14just coincides with the axial partitioning line X. Under such circumstance, the space of the vane chamber202, (that is, the intake section2022) rearward clockwise from the axial vane contact line Y defined by the vane14to the axial partitioning line X is minimal, while the space of the vane chamber202, (that is, the compression exhaustion section2021) forward counterclockwise from the axial vane contact line Y defined by the vane14to the axial partitioning line X is maximal. At this time, the compression travel is in an initial zeroed state. When the vane rotor1further (counterclockwise) rotates, the axial vane contact line Y defined by the vane14passes over the axial partitioning line X. Thereafter, the intake section2022is gradually enlarged, (that is, the gas is continuously taken in) and the compression exhaustion section2021is gradually minified from the aforesaid maximal state, (that is, the gas is continuously compressed) until the gas outlet204of the cylinder2reaches the position as shown inFIG.7. At this time, the gas outlet204is gradually in communication with the out-guiding hole305of the main seat3, whereby the compressed gas in the compression exhaustion section2021starts to be exhausted from the out-guiding hole305until the axial vane contact line Y defined by the vane14again coincides with the axial partitioning line X. Accordingly, the gas intake, compression and exhaustion travels are accomplished step by step. That is, when the axial vane contact line Y defined by the vane14coincides with the axial partitioning line X, the intake section2022is equal to the space of the entire vane chamber202(the largest space) and the compression exhaustion section2021is minimal and the compressed gas in the compression exhaustion section2021is just totally exhausted. The transition between the intake travel and the compression travel is a start of new compression circulation. Accordingly, the compression circulation is repeated to achieve the effect of a compressor.

In a preferred embodiment, in order to achieve better contact sealing effect between the vane14and the cylinder20, the top end of the vane14tightly abut against the inner circumferential wall203of the cylinder main body20along the axial vane contact line Y. Alternatively, the top end of the vane14can be inlaid in the cylinder main body20as shown inFIG.8. The top end of the vane14abetween the two vane pivotally connecting sections141ais inlaid in a vane inlay channel207aof the cylinder main body20ato define an axial vane contact arc Z.

Please now refer toFIGS.9to11. According to a second embodiment, the compressor structure of the present invention includes a vane rotor1, a cylinder2, a main seat3, a support body assembly4and an automatic adjustment assembly5. The vane rotor1, the cylinder2and the main seat3are substantially identical to the first embodiment and are only different from the first embodiment in that two ends of an outer periphery of the main seat main body30are respectively formed with two guide slopes308and two ends of an outer periphery of the main seat subsidiary body31are respectively-formed with two guide slopes314for cooperatively assembling with the support body assembly4and the automatic adjustment assembly5. In addition, the eccentric circular shaft hole303and the subsidiary eccentric circular shaft hole312of the first embodiment are replaced with an eccentric elliptic shaft hole3030and a subsidiary eccentric elliptic shaft hole3120(as shown by the phantom lines ofFIG.11). The second embodiment is based on the first embodiment and the support body assembly4and the automatic adjustment assembly5are additionally assembled with the first embodiment to form the second embodiment.

The support body assembly4is composed of a first support body40and a second support body41respectively disposed on outer sides of the main seat main body30and the main seat subsidiary body31. Each of the first and second support bodies40,41is formed with a rotor shaft end hole401,411respectively corresponding to the eccentric elliptic shaft hole3030and the subsidiary eccentric elliptic shaft hole3120of the main seat3. Accordingly, the first rotor shaft11and the second rotor shaft12of the vane rotor1can be passed through the eccentric elliptic shaft hole3030and the subsidiary eccentric elliptic shaft hole3120and pivotally fitted in the rotor shaft end holes401,411, whereby the vane rotor1is pivotally rotatably supported on the support body assembly4.

A periphery of the first support body40and a periphery of the second support body41are formed with lateral bent edges402,412directed to the main seat main body30and the main seat subsidiary body31. The lateral bent edges402,412define openings403,413. Lateral perforations404,414are respectively formed on the lateral bent edges402,412in positions corresponding to the guide slopes308,314of the main seat3.

The automatic adjustment assembly5can be mounted at the lateral perforations404,414of the lateral bent edges402,412. The automatic adjustment assembly5is disposed on two lateral sides of the support body assembly4for adjusting and eliminating the gap between the circumferential wall of the vane impeller10of the vane rotor1and the inner circumferential wall203of the vane chamber202, which gap is produced due to wear in operation. The eccentric elliptic shaft hole3030of the main seat main body30and the subsidiary eccentric elliptic shaft hole3120of the main seat subsidiary body31are formed as elongated elliptic holes in adaptation to the installation of the automatic adjustment assembly5. The direction of the long axis of the elongated elliptic hole corresponds to the displacement direction of the gap between the circumferential wall of the vane impeller10of the vane rotor1and the inner circumferential wall203of the vane chamber202, which is adjusted by the automatic adjustment assembly5. Moreover, the short axis of the elongated elliptic hole is equal to the diameter of the first rotor shaft11and the second rotor shaft12of the vane rotor, whereby the track of the gap can be stably adjusted.

In this embodiment, the automatic adjustment assembly5has a shaft rod51, two fastening members52,53and an elastic adjustment member54. The two fastening members52,53are respectively passed through the lateral perforations404,414of the two symmetrical lateral bent edges402,412and fitted on the shaft rod51toward each other. A rear end of the shaft rod51is formed with a self-tapping threaded section511. A tail end of the self-tapping threaded section511is formed with a polygonal cross-sectional section512. The elastic adjustment member54includes a self-tapping nut541screwed on the self-tapping threaded section511, a tail-end retainer member542securely fitted on the polygonal cross-sectional section512and a torque spring543assembled between the self-tapping nut541and the tail-end retainer member542by a preset torque. Two ends of the torque spring543are respectively fixed on the self-tapping nut541and the tail-end retainer member542, whereby by means of the automatically elastically twisting effect of the self-tapping nut541of the elastic adjustment member54, the two fastening members52,53can automatically get close to the main seat main body30and the main seat subsidiary body31. In this case, fastening slopes521,531of the two fastening members52,53can get close to the main seat main body30and the main seat subsidiary body31to force the guide slopes308,314of the main seal3from two sides, whereby the fastening slopes521,531always apply a lifting force to the guide slopes308,314. Under such circumstance, the main seat3is forced to drive the cylinder2to move in a direction toward the circumferential wall of the vane impeller10of the vane rotor1so as to tightly attach to the circumferential wall of the vane impeller10. Therefore, the gap between the circumferential wall of the vane impeller10and the inner circumferential wall203of the vane chamber202, which gap is produced due to wear can be automatically adjusted and eliminated.

Please now refer toFIG.12. According to a third embodiment, the compressor structure of the present invention includes a vane rotor1, a cylinder2, a main seat3, a support body assembly4and an automatic adjustment assembly5, which are assembled in the same manner as the second embodiment. The third embodiment further includes a compression ratio regulation assembly6. The compression ratio regulation assembly6includes a regulation rod61and a regulation member62. The regulation member62is pivotally rotatably fitted between the outer circumference of the cylinder2and the cylinder receiving chamber301of the main seat3. A driven section621and a regulation opening622are disposed on an outer circumference of the regulation member62. The driven section621can be multiple teeth uniformly arranged in a row. The regulation opening622keeps partially overlapping with the out-guiding hole305of the main seat3.

The regulation rod61extends from outer side into the main seat3. An end section of the regulation rod61is formed with a driving sect ion611engaged with the driven section621. The driving section611is an outer thread, which can be engaged with the driven section621(teeth arranged in a row). In a preferred embodiment, one end of the regulation rod61is exposed to outer side of the main seat3and additionally connected with an electronic mechanism capable of driving the regulation rod61to rotate so as to achieve strength-saving and fast operation function.

In the above structure, an operator can drive the regulation rod61to rotate from outer side. The driving section611of the regulation rod61is engaged with the driven section621of the regulation member62so that the regulation member62can be rotated clockwise or counterclockwise to change the overlapping start posit ion of the regulation opening622and the out-guiding hole305so as to adjust the timing for the gas outlet204of the cylinder2to guide out the compressed gas. Accordingly, the compression ratio of the output gas can be real-time adjusted.

Please now refer toFIGS.13to17, which show a fourth embodiment of the compressor structure of the present invention. The fourth embodiment is based on the second embodiment and is different from the second embodiment in that the gas outlet204is alternatively disposed on the vane rotor1instead of the circumferential wall of the cylinder main body20and the gas is exhausted through the first rotor shaft11. In addition, the out-guiding hole305originally disposed on the main seat main body30for controlling the gas compression ratio in the second embodiment is replaced with a shaft end gas exhaustion control assembly90for controlling the exhaustion of the compressed gas through the first rotor shaft11. Except the above two modifications, the other structure, assembly and operation of the fourth embodiment are identical to the second embodiment. Therefore, the fourth embodiment of the compressor structure of the present invention includes a vane rotor1, a cylinder2, a main seat3, a support body assembly4, an automatic adjustment assembly5and a shaft end gas exhaustion control assembly90. The vane rotor1of the fourth embodiment is substantially identical to the vane rotor1of the second embodiment and is only different from the vane rotor1of the second embodiment in that a gas exhaustion passage16is additionally formed inside the vane rotor1. One end of the gas exhaustion passage16is in communication with a gas outlet161formed at a junction between the vane impeller10and the vane slot13in the advancing direction of the vane14. The other end of the gas exhaustion passage16is in communication with a gas exhaustion port162formed on the first rotor shaft11instead of the gas out let204of the second embodiment to provide the same function. In addition, the cylinder2of the fourth embodiment is different from the cylinder2of the second embodiment in that the gas outlet204of the second embodiment is eliminated. The other structures of the fourth embodiment are all identical to the second embodiment.

In this embodiment, the shaft end gas exhaustion control assembly90is disposed on outer side of the first support body40(or the second support body41) of the support body assembly4. A rotor shaft socket901is formed at a center of the shaft end gas exhaustion control assembly90. The rotor shaft socket901is sealedly capped on an end section of the first rotor shaft11(or the second rotor shaft12) with the gas exhaustion port162. A part of a circumference of the rotor shaft socket901is formed with an out-guiding notch902in communication with a gas exhaustion port903formed on the shaft end gas exhaustion control assembly90in communication with outer side of the shaft end gas exhaustion control assembly90for exhausting the gas.

The gas exhaustion port162at the end section of the first rotor shaft11of the fourth embodiment provides the same function in compressor operation as the gas outlet204of the second embodiment. Also, the out-guiding notch902of the shaft end gas exhaustion control assembly90of the fourth embodiment provides the same function in compressor operation as the out-guiding hole305of the second embodiment. In operation of the compressor of the fourth embodiment, the compressed air goes from the gas outlet161of the vane rotor1through the gas exhaustion passage16to be exhausted to outer side from the gas exhaustion port162of the end section of the first rotor shaft11. When the gas exhaustion port162of the end section of the first rotor shaft11starts to overlap with the out-guiding notch902of the shaft end gas exhaustion control assembly90(with reference toFIGS.16and16A), the compressed air goes through the out-guiding notch902to be exhausted to outer side of the compressor from the gas exhaustion port903.

Please now refer toFIG.17. According to the above structure, a compression ratio regulation assembly904can be additionally fitted between inner circumference of the rotor shaft socket901of the shaft end gas exhaustion control assembly90and outer circumference of the first rotor shaft11. The compression ratio regulation assembly904has a regulation opening9041in the moving path of the gas exhaustion port162. A drive mechanism (not shown) is used to drive the compression ratio regulation assembly904to rotate and make the regulation opening9041change the overlapping position with the out-guiding notch902so as to change the liming for the gas exhaustion port162to guide out the air. Accordingly, in the precondition that the shaft end gas exhaustion control assembly90is not replaced, the same operation effect of adjustment of air compression ratio can be achieved. The compression ratio regulation assembly904has the same function as the compression ratio regulation assembly6of the third embodiment (with reference toFIG.12).

Please now refer toFIGS.18to22, which show a fifth embodiment of the compressor structure of the present invention. The fifth embodiment is based on the fourth embodiment and is different from the fourth embodiment in that the first rotor shaft11of the vane rotor1additionally has a connection section Ml and a linking member112fit ted on the connect ion sect ion111. Moreover, the shaft end gas exhaustion control assembly90of the fourth embodiment is replaced with a shaft end gas exhaust ion control assembly91. Except the above two modifications, the other structure, assembly and operation of the fifth embodiment are identical to the fourth embodiment. Therefore, the fifth embodiment of the compressor structure of the present invention includes a vane rotor1, a cylinder2, a main seat3, a support body assembly4, an automatic adjustment assembly5and a shaft end gas exhaustion control assembly91.

In this embodiment, the shaft end gas exhaustion control assembly91is composed of an end cap seat911and an out-guiding notch control ring cap912with an opening. The end cap seat911is disposed on outer side of the first support body40(or the second support body41) of the support body assembly4. A rotor shaft socket9111is formed on an inner side of the end cap seat911for fitting with the end section of the first rotor shaft11(or the second rotor shaft12). A central hole9112is formed at a center of the rotor shaft socket9111through the end cap seat911for the connection section111of the end section of the first rotor shaft11to extend through. In addition, an annular groove9113is formed on the end cap seat911concentrically around the central hole9112. A subsidiary linking member9114(such as a linking gear) is disposed between the central hole9112and the annular groove9113. The subsidiary linking member9114(linking gear) is connected (engaged) with the linking member112(driving gear). In addition, a first through hole9115is formed on the end cap seat911. The through hole9115passes through the annular groove9113in communication with the rotor shaft socket911.

A rim of the open end of the out-guiding notch control ring cap912is inlaid in the annular groove9113of the end cap seat911. A driven section9121(such as an inner toothed ring) is annularly disposed on an inner circumferential wall of the out-guiding notch control ring cap912. The driven section9121(inner toothed ring) is connected (engaged) with the subsidiary linking member9114(linking gear), whereby the out-guiding notch control ring cap912can via the linking member112(driving gear) first drive the subsidiary linking member9114(linking gear) and then indirectly drive the driven section9121to pivotally rotate. In this embodiment, the rim of the out-guiding notch control ring cap912that is inlaid in the annular groove9113is formed with a first annular rail9122. A first notch segment91221and a second notch segment91222are disposed on the first annular rail9122. In addition, the first annular rail9112and the first through hole9115of the end cap seat911are positioned in the same axial position. When the out-guiding notch control ring cap912is driven by the linking member112to pivotally rotate, the first notch segment91221and the second notch segment91222on the first annular rail9122will both pass through the first through hole9115to overlap and communicate with the first through hole9115.

In the operation of the compressor, each time period for each of the first notch segment91221and the second notch segment91222to pass through the first through hole9115just corresponds to one-cycle rotation of the compressor. Therefore, one-cycle rotation of the first annular rail9122is equivalent to two-cycle rotation of the vane rotor1. In addition, the rotation is transmitted through the subsidiary linking member9114so that the rotational direction of the first annular rail9112is reverse to the rotational direction of the vane rotor1, that is, in operation, the ratio of the rotational speed of the linking member112(driving gear) to the rotational speed of the driven section9121(inner toothed ring) is 2:1. In the case that there are three notch segments disposed on the first annular rail9122, the ratio of the rotational speed of the linking member112to the rotational speed of the driven section9121is 3:1, and so on.

In operation of the fifth embodiment of the compressor structure of the present invention, the compressed air of the vane chamber202goes from the gas outlet161of the vane rotor1through the gas exhaustion passage16and the gas exhaustion port162of the end section of the first rotor shaft11into the interval space defined between the first rotor shaft11and the rotor shaft socket9111of the end cap seat911. Then the compressed air goes through the first annular rail9122in the annular groove9113to be exhausted to outer side in a direction to the first through hole9115. In the case that any notch part of the notch segments on the first annular rail9122overlaps and communicates with the first through hole9115, the compressed gas is exhausted out of the compressor. If not, the compressor is situated at an air compression stage.FIG.21Ashows that the compressor is situated at an initial compression stage, wherein the corresponding operation of the first notch segment91221starts.FIG.21Bshows that the compressor enters a final gas compression stage. During the operation period from the initial compression stage ofFIG.21Ato this stage, the first notch segment91221passes through the first through hole9115, but no notches overlap and communicate therewith. However, after that, the notch part of the first notch segment91221is about to overlap and communicate with the first through hole9115to enter the compression exhaustion state.FIG.21Cshows that the compressor starts to enter the exhaustion completion stage. During the period from the stage ofFIG.21Bto the stage ofFIG.21C, the notch part of the first notch segment91221overlaps and communicates with the first through hole9115to exhaust the compressed air. After the exhaustion is completed, the first notch segment91221finishes the corresponding compression operation. At the same time, the second notch segment91222starts to enter the corresponding operation.FIGS.21D and21Eshow that the compressor is situated at the operation corresponding to the second notch segment91222. The second notch segment91222is entirely a notch in communication with the first through hole9115so that the compressor is situated in an uncompressed state, in which the gas is continuously exhausted so that the compressor serves as a pump, it can be known from the contents ofFIG.21AandFIG.21Ethat the contents of the two drawings are totally identical to each other. This means that the stage of completion of the operation of the second notch segment91222is exactly the next initial operation stage of the first notch segment91221. Accordingly, the compressor is continuously alternately switched between operations to continuously circularly operate.

The aforesaid first annular rail9122has two notch segments. However, the gas is all exhausted from the first through hole9115so that it is uneasy to distinguish the exhausted gas for respective use. Therefore, the first notch segment91221and the second notch segment91222of the first annular rail9122of the out-guiding notch control ring cap912can be dismantled into the out-guiding notch control ring cap922as shown inFIG.22. That is, the first notch segment91221of the original first annular rail9122is dismantled into a corresponding first notch segment92221of a first annular rail9222and the second notch segment91222of the original first annular rail9122is dismantled into a corresponding first notch segment92231of a second annular rail9223. In addition, the end cap seat911is replaced with an end cap seat921. The end cap seat921is formed with a first through hole9215identical to and corresponding to the original first through hole9115and an additional second through hole9216. The other structures of the end cap seat921are all identical to those of the end cap seat911. Accordingly, the gas exhausted from the first notch segment92221of the first annular rail9222is exhausted from the first through hole9215, while the gas exhausted from the first notch segment92231of the second annular rail9223is exhausted from the second through hole9216to facilitate successive application. In the case that the first annular rail9122is formed with three notch segments, the first annular rail9122can be dismantled into three corresponding annular rails, and so on.

The fourth and fifth embodiments are both based on the structure of the second embodiment. In the case that it is unnecessary to automatically adjust and eliminate the gap between the circumferential wall of the vane impeller10and the inner circumferential wall203of the vane chamber202, which gap is produced due to wear, both the fourth and fifth embodiments can be alternatively based on the structure of the first embodiment and the shaft end gas exhaustion control assemblies90,91,92can be alternatively disposed on outer side of the main seat main body30(or main seat subsidiary body31) of the main seat3. Except that the support body assembly4and the automatic adjustment assembly5are omitted, all the other structures and operations are identical to those of the first embodiment and thus will not be redundantly described hereinafter.

In conclusion, the compressor structure of the present invention can truly reduce the wear extent of the vane and the inner wall of the vane chamber and lower energy loss. Moreover, by means of operating the additionally disposed compression ratio regulation assembly, the compression ratio of the compressor can be easily adjusted. In addition, the compressor structure of the present invention has the function of switching the compression ratio stage by stage. The present invention is inventive and advanced. The above embodiments are only used to illustrate the present invention, not intended to limit the scope thereof. Many modifications of the above embodiments can be made without departing from the spirit of the present invention.