Patent Publication Number: US-2023136689-A1

Title: Pump with variable suction/discharge amount and drive device composed of the pump and driving method thereof

Description:
BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The present invention relates generally to a pump with variable suction/discharge amount and a drive device composed of the pump and a driving method thereof, and more particularly to a rotary vane pump composed of a fixed wall member, a movable wall member, a movable vane chamber sleeve and a vane rotor. The rotary vane pump has a vane chamber, which is extendable/retractable in an axial direction of the vane rotor. Accordingly, the capacity of the vane chamber is variable to form the pump with variable suction/discharge amount. In addition, at least two pumps with variable suction/discharge amount can be assembled in communication with each other to form an active/passive drive device. Moreover, in the principle that the driving force and the load resistance must be balanced, during the operation process, the drive device can automatically adjust the rotational speed ratio between the active pump and the passive pump as a transmission drive device. 
     2. Description of the Related Art 
     The conventional pumps can be generally classified into two major types, that is, the pump with constant suction/discharge amount and the pump with variable suction/discharge amount. The pump with variable suction/discharge amount has wider application range and thus is popularly employed in relevant industries. With respect to the structural form, the pump with variable suction/discharge amount can be further classified into two types, that is, piston-type pump with variable suction/discharge amount and rotary vane pump with variable suction/discharge amount. The piston-type pump with variable suction/discharge amount generally has a rotary swash plate with variable angle. In rotation, the swash plate sequentially pushes multiple piston-type cylinder blocks arranged substantially in parallel to each other.  FIG.  1    shows a conventional rotary vane pump with variable suction/discharge amount. The rotary vane pump mainly includes a vane rotor  10  disposed in a cam ring  11  inside the pump  1 . An eccentric amount adjustment member  12  is disposed on one side of the cam ring  11  to push the cam ring  11  and adjust the eccentric amount of the eccentric amount adjustment member  12  to the vane rotor  10 . The eccentric amount is adjustable so that the fluid receiving space between the vane rotor  10  and the cam ring  11  can be modulated so as to vary the suction/discharge amount of the pump. 
     However, the cam ring  11  is mounted in the pump  1  so that the adjustable displacement amount is limited within the fixed space of the housing of the pump. The size of the internal space of the housing directly affects and restricts the radial sizes of the pump body and all the components. As a result, when it is necessary to manufacture different products with maximal suction/discharge amount, the commonality of the components of the different pumps with different suction/discharge amounts is quite low. Therefore, it is necessary redesign numerous components of each new pump with maximal suction/discharge amount and manufacture the molds for molding the components. As a result, the manufacturing cost is greatly increased. In addition, in operation, in case the distance between the suction side and the discharge side of the pump is relatively long, then the pressure difference between the suction side and the discharge side will be excessively great. Under such circumstance, the reciprocal radial extension/retraction displacement amount of the respective vanes may be too large. This will lead to ill affection of vibration or collision noise. 
     SUMMARY OF THE INVENTION 
     It is therefore a primary object of the present invention to provide a novel rotary vane pump with variable suction/discharge amount to solve the above problems existing in the conventional pump with variable suction/discharge amount. The vane chamber of the pump is extendable/retractable in an axial direction of the vane rotor to modulate the capacity of the vane chamber. Accordingly, the unit circulation suction/discharge amount of the fluid in the pump can be increased/decreased with the axial change of the space of the vane chamber. Therefore, when it is necessary to manufacture different pumps with different suction/discharge amounts, the radial specifications of the respective components are in conformity with each other so that the community in use of the components is enhanced and the manufacturing and material costs of different pumps with suction/discharge amounts are greatly lowered. Moreover, when the requirement for the maximal suction/discharge amount of the pump is increase, it is only necessary to modify the axial size of the pump and the relevant components without enlarging the radial size of the vane chamber to increase the pressure difference between the suction side and the discharge side in the vane chamber. Also, the radial extending/retracting travel of the vane will not be elongated due to the increase of the radial size of the vane chamber. Therefore, in operation, the noise made by the reciprocal extension/retraction of the vane can be effectively lowered. 
     It is a further object of the present invention to provide a transmission drive device composed of at least two pumps with variable suction/discharge amount. The two pumps are oppositely arranged. The fluid suction passage of one of the two pumps is in communication with the fluid discharge passage of the other of the two pumps to form a closed driving loop for the active pump to drive the passive pump. During the driving operation process of the loop, when a difference value exists between the driving force of the active pump and the load resistance of the passive pump, the difference value pushes and acts on the extendable/retractable vane chamber of the vane chamber body, whereby the capacity of the vane chamber of the active pump and the capacity of the vane chamber of the passive pump are automatically extended/retracted and modulated until the driving force applied to the fluid in the active pump and the load resistance pushed by the fluid in the passive pump are balanced. Also, in the condition that the fluid suction/discharge amount per unit time of the active pump and the fluid suction/discharge amount per unit time of the passive pump are nearly equal to each other, the capacities of the vane chambers and the rotational speeds of the active pump and the passive pump are automatically adjusted to be in inverse proportion to each other so as to balance the operation. Therefore, when the driving force or the load resistance changes, the rotational speed ratio of the active pump and the passive pump is automatically adjusted according to the change of the driving force and the load resistance so as to achieve the object of smooth transmission driving. 
     To achieve the above and other objects, the pump with variable suction/discharge amount of the present invention includes a vane chamber body and a vane rotor disposed in the vane chamber body. The vane chamber body is at least composed of a fixed wall member, a movable wall member and a movable vane chamber sleeve, which define a vane chamber. The vane rotor has an impeller disposed in the vane chamber. At least one vane is disposed on the impeller. The movable wall member and the movable vane chamber sleeve are displaceable in an axial direction of the vane rotor relative to the fixed wall member, whereby the vane chamber is extendable/retractable in the axial direction of the vane rotor to increase/decrease the capacity of the vane chamber. 
     In the above pump with variable suction/discharge amount, the number of the vanes is less than or equal to the number of the eccentric vane chamber sections. 
     In the above pump with variable suction/discharge amount, one single vane is disposed on the impeller and the vane chamber has at least one eccentric vane chamber section. 
     In the above pump with variable suction/discharge amount, the vane chamber has multiple eccentric vane chamber sections and multiple vanes are disposed on the impeller in adaptation to the multiple eccentric vane chamber sections. 
     In the above pump with variable suction/discharge amount, two rotor shaft ends of the vane rotor are respectively disposed on two support bodies corresponding to the two rotor shaft ends. At least one of the rotor shaft ends is externally connected with a driving member for receiving power or bearing load. 
     In the above pump with variable suction/discharge amount, the fixed wall member has a fixed wall seat sleeve and a fixed wall end face. The fixed wall end face is disposed at one end of the fixed wall seat sleeve and normal to the axis of the vane rotor, whereby the fixed wall end face can tightly attach to an end face of the impeller of the vane rotor normal to the axial direction of the vane rotor. 
     In the above pump with variable suction/discharge amount, the fixed wall member is fitted on a base seat of the support body (at one end). 
     The base seat has a fixed wall end boss. The fixed wall end boss is fully plugged in a fixed wall hole formed at a center of the fixed wall end face, whereby a boss end face of the fixed wall end boss and the fixed wall end face together form a fixed wall face and the fixed wall face can tightly attach to an end face of the vane rotor normal to the axial direction of the vane rotor. An eccentric rotor shaft hole is formed on the fixed wall end boss. A shaft end of the vane rotor is pivotally fitted in the eccentric rotor shaft hole. 
     In the above pump with variable suction/discharge amount, at least two fluid suction/discharge passages are formed in the vane rotor. One end of each suction/discharge passage, which end is directed to the vane chamber, is in communication with a suction side and a discharge side of the vane of the vane rotor. One end of each suction/discharge passage, which end is distal from the suction side and the discharge side, is in communication with at least one of two rotor shaft ends of the vane rotor. 
     In the above pump with variable suction/discharge amount, a fluid suction/discharge port member is pivotally fitted on and assembled with the rotor shaft end in communication with the suction/discharge passages, whereby the rotor shaft end can pivotally rotate in the fluid suction/discharge port member, while the fluid suction/discharge port member is disposed on a support body (at one end) and keeps stationary. 
     In the above pump with variable suction/discharge amount, the suction/discharge passages extend to the same rotor shaft end. The suction/discharge passages respectively communicates with a central section and a non-central section of the rotor shaft end and connecting with outer side directly via a suction/discharge passage disposed on at least one of the base seat and the support body. 
     In the above pump with variable suction/discharge amount, the movable wall member is fitted around and assembled with the vane rotor, whereby the movable wall member can slide on an outer circumference of the impeller in the axial direction of the vane rotor, the movable vane chamber sleeve being fitted around the fixed wall member and the impeller to synchronously axially slide with the movable wall member. 
     In the above pump with variable suction/discharge amount, a retainer member is assembled between the movable wall member and the movable vane chamber sleeve so as to keep the movable wall member and the movable vane chamber sleeve attach to and assemble with each other, whereby the movable wall member and the movable vane chamber sleeve can synchronously slide in the axial direction of the vane rotor. 
     In the above pump with variable suction/discharge amount, the movable wall member has a movable wall face. The movable wall face tightly attaches to vane chamber sleeve end face of the movable vane chamber sleeve distal from the fixed wall member. A fitting hole is formed at a center of the movable wall member, which is axially slidable to fit around the impeller. An inner wall of the fitting hole is formed with a vane receiving slot corresponding to the vane of the impeller, whereby the vane can slide into the vane receiving slot. 
     In the above pump with variable suction/discharge amount, the vane chamber inside the movable vane chamber sleeve is defined between the movable vane chamber sleeve, the fixed wall end face of the fixed wall member, the movable wall face of the movable wall member and the vane rotor. The impeller occupying a part of the vane chamber and the remaining space of the vane chamber forms at least one eccentric vane chamber section eccentric to the axis of the vane rotor. 
     In the above pump with variable suction/discharge amount, the vane has a vane top edge distal from the vane rotor. The vane top edge tightly attaches to the inner wall of the vane chamber and is slidable relative to the inner wall of the vane chamber in at least one of the axial and circumferential directions of the vane rotor. 
     In the above pump with variable suction/discharge amount, a sealing block is disposed at inter-contacting sections of the vane, the movable wall member and the movable vane chamber sleeve to avoid any gap between the inter-contacting sections of the vane, the movable wall member and the movable vane chamber sleeve, whereby the fluid in the vane chamber is prevented from leaking. 
     In the above pump with variable suction/discharge amount, an operation fluid is output and input into the vane chamber in a closed loop, at least one of the movable wall member and the movable vane chamber sleeve being displaceable relative to the fixed wall member, whereby the capacity of the vane chamber is changeable and the output amount and input amount of the operation fluid pushed by the rotating vane rotor to pass the vane chamber per unit time are variable with the change of the capacity of the vane chamber, whereby the vane rotor can provide power transmission at different rotational speeds according to the change of the capacity of the vane chamber. 
     In the above pump with variable suction/discharge amount, in the push transfer process of the sole operation fluid, the pressure in the vane chamber is changed, the change amount of the pressure pushing and acting between the movable wall member, the movable vane chamber sleeve, the vane rotor and the fixed wall member, whereby at least the movable wall member and the fixed wall member are displaced relative to each other. 
     In the above pump with variable suction/discharge amount, an external forcing member applies a push force to at least one of the movable wall member and the movable vane chamber sleeve to forcedly at least make the movable wall member and the fixed wall member displace relative to each other. 
     In the above pump with variable suction/discharge amount, a transmission drive device composed of the above pump with variable suction/discharge amount of the present invention is composed of at least two pumps with variable suction/discharge amount. The two pumps with variable suction/discharge amount are oppositely arranged. One of the two pumps with variable suction/discharge amount is set a active pump, while the other of the two pumps with variable suction/discharge amount is set a passive pump, a driving loop being formed between the active pump and the passive pump. 
     In the above transmission drive device, at least one of a same-direction displacement connection member and a synchronous displacement connection member is drivingly connected between at least one of the movable wall member and the movable vane chamber sleeve of the active pump and the movable wall member and the movable vane chamber sleeve of the passive pump. 
     In the above transmission drive device, a displacement resistant member is additionally arranged in at least one of the increasing direction of the capacity of the vane chamber of the active pump and the decreasing direction of the capacity of the vane chamber of the passive pump. 
     In the above transmission drive device, each of the active pump end and the passive pump end has at least four-time vanes and a number of eccentric vane chamber sections, which number is more than or equal to the number of the vanes. The angle phase of each vane in the vane chamber corresponding to the eccentric vane chamber section is 180-degree different from the angle phase of at least another vane in the vane chamber in a complementary relationship. 
     In the above transmission drive device, each the four-time eccentric vane chamber sections are integrally formed in one single pump with variable suction/discharge amount. 
     In the above transmission drive device, each eccentric vane chamber sections are formed in each independent pump with variable suction/discharge amount. 
     In the above transmission drive device, the transmission drive device has at least two active pumps and a common engagement member is engaged between the two active pumps to synchronously drive the two active pumps. 
     In the above transmission drive device, the transmission drive device has at least two active pumps and a common engagement member is engaged around the two active pumps to synchronously drive the two active pumps. 
     In the above transmission drive device, the transmission drive device has at least two active pumps and at least two passive pumps. At least one of the active pumps and the passive pumps is assembled and connected in an array. 
     In the above transmission drive device, the transmission drive device has at least two active pumps and at least two passive pumps. At least one of the active pumps and the passive pumps is linearly assembled and connected. 
     In the above transmission drive device, the transmission drive device has at least two active pumps and at least two passive pumps. At least one of the active pumps and the passive pumps is serially assembled and connected in the form of a string. 
     In the above transmission drive device employing the pump with variable suction/discharge amount of the present invention, an operation fluid is output and input into the vane chamber in a closed loop, at least one of the movable wall member and the movable vane chamber sleeve being displaceable relative to the fixed wall member, whereby the capacity of the vane chamber is changeable and the output amount and input amount of the operation fluid pushed by the rotating vane rotor to pass the vane chamber per unit time are variable with the change of the capacity of the vane chamber, whereby the vane rotor can provide power transmission at different rotational speeds according to the change of the capacity of the vane chamber. 
     In the above transmission drive device, in the push transfer process of the sole operation fluid, the pressure in the vane chamber is changed, the change amount of the pressure pushing and acting between the movable wall member, the movable vane chamber sleeve, the vane rotor and the fixed wall member, whereby at least the movable wall member and the fixed wall member are displaced relative to each other. 
     In the above driving method, an external forcing member applies a push force to at least one of the movable wall member and the movable vane chamber sleeve to forcedly at least make the movable wall member and the fixed wall member displace relative to each other. 
     The driving method employing the pump with variable suction/discharge amount of the present invention includes steps of:
         (1) making the transmission drive device operate and producing a difference value between the driving force of the active pump and the load resistance born by the passive pump;   (2) automatically extending/retracting and modulating the capacity of the vane chamber of the active pump and the capacity of the vane chamber of the passive pump due to the push of the difference value between the driving force and load resistance; and   (3) in the condition that the fluid suction/discharge amount per unit time of the active pump and the fluid suction/discharge amount per unit time of the passive pump are nearly equal to each other, making the driving force applied to the fluid in the active pump equal to the load resistance of the fluid in the passive pump so as to achieve balanced operation and automatically adjusting the capacity of the vane chamber of the active pump and the capacity of the vane chamber of the passive pump and the rotational speeds of the active pump and the passive pump to make the active pump and the passive pump operate in inverse proportion to each other, whereby when the action between the driving force and the load resistance changes, the capacity of the vane chamber of the active pump and the capacity of the vane chamber of the passive pump and the rotational speed ratio therebetween are automatically adjusted so as to achieve balanced driving between the driving force and the load resistance in operation.       

     In the above driving method, in operation of the driving loop, the driving force of the active pump rotates the vane rotor to drive the vane to apply a push pressure to the movable vane chamber sleeve, the fixed wall face of the fixed wall member and the movable wall face of the movable wall member positioned on the discharge side of the vane in the eccentric vane chamber section of the active pump and the vane face of the vane, the movable vane chamber sleeve, the fixed wall face and the movable wall face positioned on the suction side of the vane in the eccentric vane chamber section of the passive pump. On the other hand, at the same time, after pushed, a vacuum sucking force is applied to the movable vane chamber sleeve, the fixed wall face and the movable wall face positioned on the suction side of the vane in the eccentric vane chamber section of the active pump and the vane face of the vane, the movable vane chamber sleeve, the fixed wall face and the movable wall face positioned on the discharge side of the vane in the eccentric vane chamber section of the passive pump. After the movable wall face bears the push pressure or the vacuum sucking force, the movable wall member and the movable vane chamber sleeve tightly attaching thereto are synchronously axially moved. Two sides of the vane in the passive pump are respectively double-affected by the push pressure and the vacuum sucking force in the same direction and passive, whereby the vane rotor is passive to rotate and output power to the load end of the passive pump. 
     In the above driving method, in case the area of the movable wall face of the movable wall member on the discharge side of the vane in the eccentric vane chamber section of the active pump is larger than the area of the movable wall face of the movable wall member on the suction side of the vane in the eccentric vane chamber section of the passive pump, the movable wall member and the movable vane chamber sleeve of the active pump gradually axially displace in a direction away from the fixed wall face of the fixed wall face to enlarge the axial space of the eccentric vane chamber section. At the same time, a sucking force is applied to the suction side of the vane of the passive pump, whereby the movable wall member and the movable vane chamber sleeve of the passive pump are sucked to axially displace in a direction toward the fixed wall face. Also, in case the area of the movable wall face on the suction side of the vane in the eccentric vane chamber section of the active pump is smaller than the area of the movable wall face on the discharge side of the vane in the eccentric vane chamber section of the passive pump, the vane of the active pump sweeps to produce vacuum sucking force on the suction side. A greater vacuum sucking force is applied to the movable wall face in the passive pump with larger area, whereby the movable wall member and the movable vane chamber sleeve of the active pump displace in a direction away from the fixed wall face and the movable wall member and the movable vane chamber sleeve of the passive pump displace in a direction toward the fixed wall face. Reversely, when the sizes of the areas of the movable wall faces on the discharge side and the suction side of the vanes respectively in the eccentric vane chamber sections of the active pump and the passive pump are compared with each other to be on the contrary to the above, the movable wall member and the movable vane chamber sleeve of the active pump and the passive pump displace in a direction reverse to the above direction. The same-direction displacement connection member is connected between the active pump and the passive pump so that along with the driving of the vane of the active pump. The liquid phase fluid applues a push force to the vane face on the suction side of the vane in the passive pump to gradually push the passive pump and the load end thereof so that the driving loop of the active pump and the passive pump will gradually start to operate. 
     In the above driving method, the active pump assembly with multiple eccentric vane chamber sections is connected with the passive pump assembly with multiple eccentric vane chamber sections. The sums of the areas of the movable wall faces respectively on two sides of the vanes in the eccentric vane chamber sections of the active pump and the passive pumps are equal to each other, whereby the driving force of the active pump assembly is balanced with the load resistance of the passive pump assembly and the sums of the areas of the movable wall faces on the discharge sides and the suction sides of the active pump assembly and the passive pump assembly are equal to each other. Also, the angle phases of the vanes respectively positioned in the eccentric vane chamber sections is arranged in a corresponding complementary relationship, whereby during any operation process, the active pump assembly and the passive pump assembly always has a vane face for bearing the power to provide driving effect. 
     In the above driving method, in operation of the closed driving loop of at least one of the active pump assembly and the passive pump assembly, when the driving force and the load resistance are varied, the total capacity and rotational speed of the active pump and the total capacity and rotational speed of the passive pump are automatically adjusted to make the driving force and the load resistance automatically achieve a balanced state. The rotational speed ratio of the active pump and the passive pump is automatically modulated according to the change of the driving force and the load resistance. 
     The present invention can be best understood through the following description and accompanying drawings, wherein: 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG.  1    is a sectional view of a conventional pump with variable suction/discharge amount, showing the structure thereof; 
         FIG.  2    is a perspective exploded view of a first preferred embodiment of the present invention; 
         FIG.  3    is a perspective partially assembled view of the first preferred embodiment of the present invention according to  FIG.  2   ; 
         FIG.  4    is a sectional assembled view of the first preferred embodiment of the present invention according to  FIG.  2   , showing that the space of the vane chamber is relatively smaller than the space of the vane chamber of  FIG.  4 - 1   ; 
         FIG.  4 - 1    is a sectional assembled view of the first preferred embodiment of the present invention according to  FIG.  2   , showing that the space of the vane chamber is relatively larger than the space of the vane chamber of  FIG.  4   ; 
         FIG.  5    is a sectional assembled view of the first preferred embodiment of the present invention according to  FIG.  2   , showing that a forcing mechanism is used to drive the movable wall member; 
         FIG.  6    is a sectional assembled view of the first preferred embodiment of the present invention according to  FIG.  2   , showing that the suction passage and discharge passage respectively communicate with outer side via two shaft ends of the vane rotor; 
         FIG.  7    is a sectional assembled view of the first preferred embodiment of the present invention according to  FIG.  2   , showing that a active pump is assembled with a passive pump, wherein a same-direction displacement connection member is connected between at least one of the movable wall member and the movable vane chamber sleeve of the active pump and the passive pump; 
         FIG.  7 - 1    is a sectional assembled view of the first preferred embodiment of the present invention according to  FIG.  2   , showing that two active pumps are assembled with two passive pumps, wherein a same-direction displacement connection member is connected between at least one of the movable wall member and the movable vane chamber sleeve of the active pump and the passive pump; 
         FIG.  7 - 2    is a sectional assembled view of the first preferred embodiment of the present invention according to  FIG.  2   , showing that four active pumps are assembled with four passive pumps, wherein a synchronous displacement connection member is connected between at least one of the movable wall member and the movable vane chamber sleeve of the active pump and the passive pump; 
         FIG.  7 - 3    is a sectional assembled view of the first preferred embodiment of the present invention according to  FIG.  7   , wherein a displacement resistant member is additionally arranged in the increasing direction of the capacity of the vane chamber of the active pump and a same-direction displacement connection member is connected between at least one of the movable wall member and the movable vane chamber sleeve of the active pump and the passive pump; 
         FIG.  7 - 4    is a sectional assembled view of the first preferred embodiment of the present invention according to  FIG.  7   , wherein a displacement resistant member is additionally arranged in the decreasing direction of the capacity of the vane chamber of the passive pump and a same-direction displacement connection member is connected between at least one of the movable wall member and the movable vane chamber sleeve of the active pump and the passive pump; 
         FIG.  8    is a sectional assembled view of the first preferred embodiment of the present invention according to  FIG.  2   , wherein two pumps are assembled to form a active pump end and a common engagement member is engaged between the two pumps to synchronously drive the two pumps; 
         FIG.  8 - 1    is a sectional assembled view of the first preferred embodiment of the present invention according to  FIG.  2   , wherein four pumps are assembled in an array to form a active pump end and a common engagement member is positioned at the center of the array and engaged with the four pumps to synchronously drive the four pumps; 
         FIG.  8 - 2    is a sectional assembled view of the first preferred embodiment of the present invention according to  FIG.  2   , wherein four pumps are assembled in an array to form a active pump end and a common engagement member is positioned around the array and engaged with the four pumps to synchronously drive the four pumps; 
         FIG.  8 - 3    is a sectional assembled view of the first preferred embodiment of the present invention according to  FIG.  2   , wherein four pumps are assembled to form a linearly arranged active pump end; 
         FIG.  8 - 4    is a sectional assembled view of the first preferred embodiment of the present invention, wherein after the forms of a shaft end and the fluid suction port member and the fluid discharge port member are changed, four pumps are serially assembled to form a stringed active pump end; 
         FIG.  9    is a perspective exploded view of a second preferred embodiment of the present invention; 
         FIG.  10    is a perspective partially assembled view of the second preferred embodiment of the present invention according to  FIG.  9   ; 
         FIG.  11    is an axially sectional assembled view of the second preferred embodiment of the present invention according to  FIG.  9   ; 
         FIG.  12    is a radially sectional assembled view of the second preferred embodiment of the present invention according to  FIG.  11   , which is taken along line A-A; and 
         FIG.  13    is a sectional assembled view of the second preferred embodiment of the present invention according to  FIG.  10   , wherein a active pump is assembled with a passive pump. 
     
    
    
     REFERENCE NUMBERS OF DRAWINGS 
     
         
           1  pump 
           10  vane rotor 
           101  active pump 
           102  passive pump 
           11  cam ring 
           12  eccentric amount adjustment member 
           2  vane chamber body 
           204  fixed wall face 
           21  fixed wall member 
           211  fixed wall seat sleeve 
           212  fixed wall end face 
           213  fixed wall hole 
           22  movable wall member 
           221  movable wall face 
           222  fitting hole 
           2221  vane receiving slot 
           23  movable vane chamber sleeve 
           230  vane chamber 
           2301 ,  2303  eccentric vane chamber section 
           2302  vane chamber sleeve end face 
           3  vane rotor 
           30  impeller 
           301  end face 
           31  vane 
           311  vane top edge 
           33  first rotor shaft 
           34  second rotor shaft 
           341  first suction/discharge ports 
           342  second suction/discharge ports 
           343  first suction/discharge passages 
           344  second suction/discharge passages 
           345  shaft center 
           346  shaft non-center 
           35  fluid suction/discharge port member 
           351  first suction/discharge passage 
           352  second suction/discharge passage 
           36  transmission member 
           37  sealing block 
           4  first support body; 
           40  second support body; 
           41  base seat 
           410 ,  4100  suction/discharge passage 
           411  fixed wall end boss 
           4110  boss end face 
           412  shaft hole 
           5  retainer member 
           6 ,  60 ,  61 ,  62  common engagement member 
           8  external forcing member 
           80  same-direction displacement connection member 
           800  synchronous displacement connection member 
           9 ,  90  displacement resistant member 
       
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     Please refer to  FIGS.  2  to  4   . The present invention is mainly composed of a vane chamber body  2 , a vane rotor  3 , a first support body  4  and a second support body  40 . The vane chamber body  2  is at least composed of a fixed wall member  21 , a movable wall member  22  and a movable vane chamber sleeve  23 . The movable wall member  22  and the movable vane chamber sleeve  23  are movable in an axial direction of the vane rotor  3  and displaceable relative to the fixed wall member  21 . At least one vane chamber  230  is defined between the fixed wall member  21 , the movable wall member  22  and the movable vane chamber sleeve  23 . When the movable wall member  22  and the movable vane chamber sleeve  23  are moved in the axial direction of the vane rotor  3  and displaced relative to the fixed wall member  21 , the capacity of the vane chamber  230  is changed. 
     According to the above principle, in a first embodiment of the present invention (as shown in  FIGS.  2  to  5   ), the fixed wall member  21  has two parts of fixed wall seat sleeve  211  and fixed wall end face  212 . The fixed wall end face  212  is disposed at one end of the fixed wall seat sleeve  211  and normal to the axis of the vane rotor  3 . A fixed wall hole  213  is formed at a center of the fixed wall end face  212 . The fixed wall seat sleeve  211  of the fixed wall member  21  is capped on a base seat  41  having a fixed wall end boss  411 . The fixed wall end boss  411  is tightly fully plugged in the fixed wall hole  213 , whereby a boss end face  4110  of the fixed wall end boss  411  and the fixed wall end face  212  together form a fixed wall face  204 . In a preferred structural form, the base seat  41  can be detachably disposed on the first support body  4  or integrally securely formed on the first support body  4 . 
     The vane rotor  3  has at least one impeller  30  and at least one vane  31  assembled with the impeller  30 . The vane  31  is radially slidable and extendable/retractable. The impeller  30  has an end face  301  normal to the axis vane rotor  3 . The end face  301  can tightly attach to the fixed wall face  204 . The vane rotor  3  has a first rotor shaft  33 , which can be pivotally fitted in an eccentric rotor shaft hole  412  formed on the base seat  41 . The first rotor shaft  33  is further passed through the first support body  4  to externally connect with a transmission member  36  for receiving power or bearing a load. The vane rotor  3  further has a second rotor shaft  34 , in which a first suction/discharge port  341  and a second suction/discharge port  342  are formed. A first suction/discharge passage  343  and a second suction/discharge passage  344  are formed in the vane rotor  3  respectively in communication with the first and second suction/discharge ports  341 ,  342 . The first and second suction/discharge passages  343 ,  344  respectively extend to further communicate with a suction side and a discharge side on two sides of the vane  31  into communication with the vane chamber  230 . The second rotor shaft  34  can be directly pivotally disposed on the second support body  40 . Alternatively, as shown in  FIGS.  2  to  5   , a fluid suction/discharge port member  35  can be first fitted on the second rotor shaft  34  and then the fluid suction/discharge port member  35  is disposed on the second support body  40 . The fluid suction/discharge port member  35  has a first suction/discharge passage  351  and a second suction/discharge passage  352 . The second rotor shaft  34  is pivotally fitted in the fluid suction/discharge port member  35  and rotated relative to the fluid suction/discharge port member  35 . Therefore, with the fluid suction/discharge port member  35  serving as a fluid connection interface (as shown in  FIGS.  4  and  5   ), the first and second suction/discharge ports  341 ,  342  of the second rotor shaft  34  can correspondingly communicate with the first and second suction/discharge passages  351 ,  352  of the fluid suction/discharge port member  35 , whereby the first and second suction/discharge ports  341 ,  342  and the internal fluid passages of the second rotor shaft  34  can be converted from an original rotating state into a stationary state. Accordingly, in continuous operation of the vane rotor  3 , the first and second suction/discharge ports  341 ,  342  and the internal fluid passages of the second rotor shaft  34  can keep in connection with an external fluid input source and an external fluid output source. The first and second suction/discharge passages  343 ,  344  in the vane rotor  3  can have various forms in addition to the above form. For example, as shown in  FIG.  6   , the first and second suction/discharge passages  343 ,  344  can communicate with outer side via the first and second rotor shafts  33 ,  34  of the vane rotor  3 . Alternatively, as shown in  FIG.  11   , the first and second suction/discharge passages  343 ,  344  can respectively communicate with a shaft center  345  and shaft non-center  346  of the second rotor shaft  34  and then connect with the outer side directly via a suction/discharge passage  410  and a suction/discharge passage  4100  disposed on the base seat  41  and/or the first support body  4 . 
     The movable wall member  22  is fitted around the vane rotor  3  and is axially slidable to fit around the impeller  30 . The movable wall member  22  has a movable wall face  221 . The movable wall face  221  is tightly attached to a vane chamber sleeve end face  2302  of the movable vane chamber sleeve  23 , which faces the movable wall member  22 . A fitting hole  222  is formed at a center of the movable wall member  22 , which is axially slidable to fit around the impeller  30 . An inner wall of the fitting hole  222  is formed with a vane receiving slot  2221  corresponding to the vane  31 . The vane  31  can slide into the vane receiving slot  2221 , whereby when the movable wall member  22  relatively axially approaches the fixed wall member  21 , more part of the vane  31  can slide into the vane receiving slot  2221 . The vane chamber  230  is defined in the movable vane chamber sleeve  23 . The vane chamber  230  can axially slide to fit around the fixed wall member  21  and the impeller  30 . The vane chamber  230  is defined between the movable vane chamber sleeve  23 , the fixed wall end face  212 , the movable wall face  221  and the vane rotor  3 . The impeller  30  occupies a part of the vane chamber  230 . The remaining space of the vane chamber  230  forms at least one eccentric vane chamber section  2301  eccentric to the axis of the vane rotor  3 . The vane  31  has a vane top edge  311  distal from the vane rotor  3 . The vane top edge  311  tightly attaches to the inner wall of the vane chamber  230  and is axially and/or circumferentially slidable relative to the inner wall of the vane chamber  230 . In addition, proper sealing and leakproof members can be disposed between the contacting sections of the vane  31  and the inner wall of the vane chamber  230  and between the tightly attaching or relatively displacing sections of the fixed wall member  21 , the movable wall member  22 , the movable vane chamber sleeve  23  and the vane rotor  3  so as to prevent the fluid in the operating vane chamber  230  from leaking through the aforesaid sections. Especially, at the inter-contacting sections of the vane top edge  311  of the vane  31 , the movable wall member  22  and the movable vane chamber sleeve  23 , the curve of the configuration of the vane top edge  311 , the cross-sectional curve of the vane receiving slot  2221  of the movable wall member  22 , into which the vane top edge  311  can slide and the curve of the inner wall of the vane chamber  230  of the movable vane chamber sleeve  23  in contact with the vane top edge  311  are different from each other. Therefore, minor gaps exist between the inter-contacting sections of the vane top edge  311  of the vane  31 , the movable wall member  22  and the movable vane chamber sleeve  23 . As a result, in operation, the vane chamber  230  cannot be fully closed. In order to solve this problem, a sealing block  37  is disposed on the vane top edge  311 , which can tightly attach to the vane top edge  311  to synchronously slide with the vane  31 . The sealing block  37  is further restricted in the intersection path of the vane receiving slot  2221  of the movable wall member  22  and the outer edge of the inner wall of the vane chamber  230  of the movable vane chamber sleeve  23 . Accordingly, in operation, the sealing block  37  always seals the inter-contacting sections of the vane top edge  311 , the vane receiving slot  2221  and the outer edge of the inner wall of the vane chamber  230  and blocks the gaps to achieve good sealing and leakproof effect. A retainer member  5  can be assembled between the movable wall member  22  and the movable vane chamber sleeve  23  so as to keep the movable wall member  22  and the movable vane chamber sleeve  23  attach to and assemble with each other, whereby the movable wall member  22  and the movable vane chamber sleeve  23  can synchronously axially slide. (The retainer member  5  can have various structural forms and will not be redundantly described hereinafter). 
     According to the above assembled structure, in operation, when the vane rotor  3  drives the vane  31  to sweep within the eccentric vane chamber section  2301 , the fluid on the forward side of the sweeping direction of the vane  31  is compressed and discharged as a discharge side. The fluid positioned on the other side of the vane  31  is sucked in as a suction side. In addition, the eccentric vane chamber section  2301  is eccentric to the axis of the vane rotor  3  so that the area of the fixed wall face  204  per unit angle, which the vane  31  sweeps over in the eccentric vane chamber section  2301 , will continuously change along with the rotation of the vane rotor  3 . This phenomenon is equivalent to that the intersection area of the movable wall face  221  on two sides of the vane  31  and the interior of the eccentric vane chamber section  2301  and the suction/discharge amount of the fluid on two sides of the vane  31  will both change along with the change of the sweeping position of the vane  31 . Also, the space of the eccentric vane chamber section  2301 , which is occupied by the vane  31 , is relatively changed. This leads to some difference between the fluid amount discharged from the discharge side of the vane  31  and the fluid amount sucked into the suction side of the vane  31 . Moreover, under the forced push of an external forcing member  8  (as shown in  FIG.  5   ) or under the action of the differences between the flow amount of the operation fluid and the pressure, the movable wall member  22  in association with the movable vane chamber sleeve  23  is fitted on the vane rotor  3  and the fixed wall seat sleeve  211  to relatively axially displace. When the movable wall face  221  gradually axially gets close to the fixed wall face  204 , the available suction/discharge capacity of the eccentric vane chamber section  2301  is relatively gradually reduced. Reversely, when the movable wall face  221  gradually axially moves away from the fixed wall face  204 , the available suction/discharge capacity of the eccentric vane chamber section  2301  is gradually increased. Accordingly, a pump with variable suction/discharge amount, which is axially extendable/retractable to change the suction/discharge amount of the vane chamber  230 , is formed. 
     Accordingly, the above pump with variable suction/discharge amount can be applied to and assembled with a closed loop. The closed loop outputs and inputs an operation fluid to the vane chamber  230  and the external forcing member  8  forcedly pushes the pump to transfer the operation fluid. In the transfer process of the operation fluid, the pressure in the vane chamber  230  is changed. The change amount of the pressure acts between at least one of the movable wall member  22  and the movable vane chamber sleeve  23  and the fixed wall member  21 , whereby the movable wall member  22  and/or the movable vane chamber sleeve  23  and the fixed wall member  21  displace relative to each other so as to change capacity of the vane chamber  230 . Accordingly, the output amount and input amount of the operation fluid pushed by the rotating vane rotor  3  to pass the vane chamber  230  per unit time are variable with the change of the capacity of the vane chamber  230 , whereby the vane rotor  3  can provide power transmission at different rotational speeds according to the change of the capacity of the vane chamber  230 . 
     As shown in  FIG.  7   , two pumps with variable suction/discharge amount of the present invention are oppositely arranged in communication with each other. The suction port and discharge port of the first suction/discharge passage  351  and second suction/discharge passage  352  of the two oppositely arranged pumps are in communication with each other. Accordingly, in case the pump of the two oppositely arranged pumps on the left side of the drawing is set a active pump  101 , while the pump on the right side is set a passive pump  102  and the discharge passage of the active pump  101  is in communication with the suction passage of the passive pump  102 , the fluid discharged from the discharge passage of the active pump  101  can enter the suction passage and the suction side of the vane  31  of the passive pump  102 . Reversely, in case the discharge passage of the passive pump  102  is in communication with the suction passage of the active pump  101 , the fluid on the discharge side of the vane  31  of the passive pump  102  is discharged from the discharge passage and then flows back to the suction passage and the suction side of the vane  31  of the active pump  101 , whereby the vane chambers and the entire suction and discharge passages of the active pump  101  and the passive pump  102  form a close loop for the active pump  101  to drive the passive pump  102 . In addition, a same-direction displacement connection member  80  is connected between at least one of the movable wall member  22  and the movable vane chamber sleeve  23  of the active pump  101  and the passive pump  102 , whereby the movable wall member  22  and the movable vane chamber sleeve  23  of the active pump  101  and the passive pump  102  can move together in the same axial direction. In operation of the closed loop of the active pump  101 , in case the employed fluid is a liquid phase fluid and the total volume of the liquid is constant, then the liquid phase fluid on the discharge side in the eccentric vane chamber section  2301  of the active pump  101  will be pushed by the vane  31  of the rotating vane rotor  3  to the suction side of the passive pump  102 . Relatively, the liquid phase fluid on the discharge side in the eccentric vane chamber section  2301  of the passive pump  102  will be pushed by the vane  31  of the rotating vane rotor  3  to the suction side of the active pump  101 . Accordingly, a complete liquid phase fluid driving loop of the active pump and the passive pump is formed. In operation of the driving loop, the driving force of the active pump  101  rotates the vane rotor  3  to drive the vane  31  to apply a push pressure to the movable vane chamber sleeve  23 , the fixed wall face  204  and the movable wall face  221  positioned on the discharge side of the vane  31  in the eccentric vane chamber section  2301  of the active pump  101  and the vane face of the vane  31 , the movable vane chamber sleeve  23 , the fixed wall face  204  and the movable wall face  221  positioned on the suction side of the vane  31  in the eccentric vane chamber section  2301  of the passive pump  102 . On the other hand, after pushed, a vacuum sucking force is applied to the movable vane chamber sleeve  23 , the fixed wall face  204  and the movable wall face  221  positioned on the suction side of the vane  31  in the eccentric vane chamber section  2301  of the active pump  101  and the vane face of the vane  31 , the movable vane chamber sleeve  23 , the fixed wall face  204  and the movable wall face  221  positioned on the discharge side of the vane  31  in the eccentric vane chamber section  2301  of the passive pump  102 . The direction of the push pressure or vacuum sucking force applied to the movable vane chamber sleeve  23  is normal to the axial moving direction of the movable vane chamber sleeve  23  so that the push pressure or vacuum sucking force cannot directly make the movable vane chamber sleeve  23  displace. The fixed wall face  204  is fixed and unmovable. Therefore, during the driving process, only the movable wall face  221  will bear the push pressure or vacuum sucking force to make the movable wall member  22  axially move. At the same time, the movable vane chamber sleeve  23  is passive to tightly attach to the movable wall member  22  and synchronously axially move. Two sides of the vane  31  in the passive pump  102  are respectively double-affected by the push pressure and the vacuum sucking force in the same direction, whereby the vane  31  is passive to drive and rotate the vane rotor  3  so as to output power to the load end of the passive pump  102 . At the beginning of the driving process, the passive pump  102  is situated in a stationary state. The vane rotor  3  of the active pump  101  starts to be rotated under the driving force, whereby the liquid phase fluid on the discharge side of the vane  31  starts to be pushed and compressed. At this time, in case the area of the movable wall face  221  on the discharge side of the vane  31  in the eccentric vane chamber section  2301  of the active pump  101  is larger than the area of the movable wall face  221  on the suction side of the vane  31  in the eccentric vane chamber section  2301  of the passive pump  102 , due to that the larger the forced area is, the greater the push pressure applied to the forced area is and due to that a load force is applied to the vane  31  of the passive pump  102 , then the movable wall member  22  and the movable vane chamber sleeve  23  of the active pump  101  will gradually axially displace in a direction away from the fixed wall face  204  to enlarge the axial space of the eccentric vane chamber section  2301 . At the same time, a sucking force is applied to the suction side of the vane  31  of the passive pump  102 , whereby the movable wall member  22  and the movable vane chamber sleeve  23  of the passive pump  102  are sucked to axially displace in a direction toward the fixed wall face  204 . At this time, the area of the movable wall face  221  on the suction side of the vane  31  in the eccentric vane chamber section  2301  of the active pump  101  is smaller than the area of the movable wall face  221  on the discharge side of the vane  31  in the eccentric vane chamber section  2301  of the passive pump  102 . Therefore, after the vane  31  of the active pump  101  sweeps, the vacuum sucking force applied to the suction side of the vane  31  provides greater sucking driving force for the movable wall face  221  in the passive pump  102  with larger area. As a result, the movable wall member  22  and the movable vane chamber sleeve  23  of the active pump  101  will displace in a direction away from the fixed wall face  204 . The movable wall member  22  and the movable vane chamber sleeve  23  of the passive pump  102  will displace in a direction toward the fixed wall face  204 . Similarly, when the sizes of the areas of the movable wall faces  221  on the discharge side and the suction side of the vane  31  are compared with each other to be on the contrary to the above, the movable wall member  22  and the movable vane chamber sleeve  23  of the active pump  101  and the passive pump  102  will displace in a direction reverse to the above direction. During the operation process of the closed loop, the movable wall member  22  and the movable vane chamber sleeve  23  will continuously reciprocally axially displace as aforesaid until the liquid phase fluid originally on the suction side of the vane  31  of the active pump  101  and the liquid phase fluid originally in the passage of the discharge side of the vane  31  of the passive pump  102  are passive and circulated and switched to be respectively on the discharge side of the vane  31  of the active pump  101  and in the passage of the suction side of the vane  31  of the passive pump  102 . In addition, after switched, the volume of the liquid phase fluid in the passage has become larger than the sum of the allowable modulated maximal capacity on the discharge side of the vane  31  of the active pump  101  and the suction side of the vane  31  of the passive pump  102  by means of axial displacement. The same-direction displacement connection member  80  is connected between the active pump  101  and the passive pump  102  and the liquid is uncompressible so that along with the driving of the vane  31  of the active pump  101 , the vane face on the suction side of the vane  31  in the passive pump  102  will entirely bear the push force of the liquid phase fluid to gradually push and the passive pump  102  and the load end thereof. Therefore, the active/passive pump closed loop will gradually start to operate. 
     Therefore, in application of the transmission drive device composed of the above components, in case the closed loop outputs and inputs an operation fluid to the respective vane chambers  230  of the active pump  101  and the passive pump  102 , by means of the forced push of the external forcing member  8  or the change amount of the pressure applied to the interior of the vane chamber  230  by the operation fluid during the push and transfer process, the push acts between at least one of the movable wall member  22  and the movable vane chamber sleeve  23  and the fixed wall member  21 , whereby the movable wall member  22  and/or the movable vane chamber sleeve  23  and the fixed wall member  21  displace relative to each other so as to change the capacity of the vane chamber  230 . Accordingly, the active pump  101  and the passive pump  102  can make the rotational speeds of the corresponding vane rotors  3  in inverse proportion to each other respectively according to the change of the capacity of the corresponding vane chambers  230  to provide power transmission. 
     During the operation process of the active/passive pump loop, the movable wall members  22  and the movable vane chamber sleeves  23  of the active pump  101  and the passive pump  102  will continuously reciprocally axially displace. Therefore, the driving force applied to the vane  31  of the passive pump  102  by the active pump  101  will be interrupted. As a result, the rotation of the passive pump  102  will be undulated. Moreover, in the above embodiment, each of the active pump and the passive pump has one single vane chamber and one single vane. In case at the beginning of actuation of the passive pump, the vane of the passive pump is positioned in a position where the vane is right fully inlaid in the vane rotor, there is no vane face in the passive pump to bear the driving force. Under such circumstance, the active pump is situated in an invalid idling state and cannot apply any driving force to the passive pump. As a result, the entire loop will idle. In order to avoid the above condition of undulated operation or idling of the loop, as shown in FIG.  7 - 1 , two active pumps  101  (or a active pump  101  with two eccentric vane chamber sections  2301 ) can be coupled with two passive pumps  102  (or a passive pump  102  with two eccentric vane chamber sections  2301 ). Alternatively, as shown in  FIG.  7 - 2   , four active pumps  101  (or a active pump  101  with four eccentric vane chamber sections  2301 ) can be coupled with four passive pumps  102  (or a passive pump  102  with four eccentric vane chamber sections  2301 ). After more active pumps and passive pumps are assembled with each other, the sums of the areas of the movable wall faces  221  on two sides of the vane  31  in the eccentric vane chamber sections  2301  are approximately or nearly equal to each other. Accordingly, the driving force of the assembly of multiple active pumps is temporarily balanced with the load resistance of the assembly of multiple passive pumps. Under such circumstance, the sums of the areas of the movable wall faces  221  on the discharge side and the suction side of the assembly of the active pumps and the passive pumps are approximately equal to each other. This can effectively improve the above condition of undulated operation. Also, due to that the multiple pumps are assembled, the angle phases of the respective vanes  31  positioned in the eccentric vane chamber sections  2301  can be arranged in a complementary relationship. Therefore, during any operation process, the assembly of the active pumps and the passive pumps always has a vane face for bearing the power without invalidate idling phenomenon of the loop. Therefore, the entire driving process can be smoother and more stable. 
     According to the above active/passive pump driving loop, especially the structural form composed of four active pumps  101  and four passive pumps  102  coupled therewith as shown in  FIG.  7 - 2   , the angle phase of each vane  31  positioned in the vane chamber  230  has another symmetrical vane  31  with an angle phase 180-degree different from the vane  31  as a complementary vane. Therefore, in the assembly of the four active pumps  101  and the four passive pumps  102 , the sum of the areas of the movable wall faces  221  corresponding to the discharge side of the vane  31  in the eccentric vane chamber sections  2301  is nearly equal to the sum of the areas of the movable wall faces  221  corresponding to the suction side of the vane  31  in the eccentric vane chamber sections  2301 . This is equivalent to that the discharge amount of the liquid phase fluid in the assembly of the four active pumps  101  and the four passive pumps  102  is nearly equal to the suction amount of the liquid phase fluid in the assembly of the four active pumps  101  and the four passive pumps  102 . Accordingly, the entire loop can continuously stably operate. In the case that the driving force of the four active pumps  101  is unchanged, while the load of the four passive pumps  102  is increased, the sweeping speed of the vanes  31  of the four passive pumps  102  will be reduced. Under such circumstance, the liquid phase fluid will accumulate on the suction sides of the vanes  31  of the four passive pumps  102  to apply a capacity-enlarging push force to the movable wall faces  221 . In addition, the amount of the liquid phase fluid flowing from the discharge sides of the vanes  31  of the four passive pumps  102  back to the suction sides of the vanes  31  of the four active pumps  101  is reduced to apply a vacuum sucking force to the movable wall faces  221 . The sum of the areas of the movable wall faces  221  on the discharge side of the vane  31  in the eccentric vane chamber sections  2301  is nearly equal to the sum of the areas of the movable wall faces  221  on the suction side of the vane  31  in the eccentric vane chamber sections  2301  so that the total force applied to the movable wall faces  221  of the four active pumps  101  is nearly equal to the total force applied to the movable wall faces  221  of the four passive pumps  102 . Under the action of the capacity-enlarging push force of the four passive pumps  102  and the vacuum sucking force of the four active pumps  101 , the movable wall members  22  and the movable vane chamber sleeves  23  of the four active pumps  101  displace in a direction toward the fixed wall faces  204  to minify the total capacity of the four active pumps  101 . At the same time, the movable wall members  22  and the movable vane chamber sleeves  23  of the four passive pumps  102  displace in a direction away from the fixed wall faces  204  to enlarge the total capacity of the four passive pumps  102 . Therefore, the four active pumps  101  must circularly input the power many times so as to drive the four passive pumps  102  to circularly output the power one time. This is similar to a downshift driving effect in power transmission. Reversely, in the case that the driving force of the four active pumps  101  is unchanged, while the load of the four passive pumps  102  is reduced, all the above operation conditions are totally reversed. That is, the four active pumps  101  only need to circularly input the power one time for driving the four passive pumps  102  to circularly output the power many times. This is similar to an upshift driving effect in power transmission. It can be known from the aforesaid that in the operation of the closed driving loop composed of the four active pumps  101  and the four passive pumps  102 , when the driving force and the load resistance change, the respective total capacities of the four active and passive pumps can be automatically adjusted so that the driving force and the load resistance can be automatically balanced with each other. Therefore, the drive device can smoothly automatically modulate the transmission according to the change of the driving force and the load resistance. 
     As shown in  FIGS.  7 ,  7 - 1 ,  7 - 2 ,  7 - 3  and  7 - 4   , in the condition that the suction/discharge amount per unit time of the active pump  101  and the suction/discharge amount per unit time of the passive pump  102  are nearly equal to each other, a same-direction displacement connection member  80  or a synchronous displacement connection member  800  is drivingly connected between the movable wall member  22  or the movable vane chamber sleeve  23  of the active pump  101  and the passive pump  102 . An external force is applied to the same-direction displacement connection member  80  or the synchronous displacement connection member  800  to push the same so as to force the movable wall member  22  or the movable vane chamber sleeve  23  of the active pump  101  and the passive pump  102  to respectively same-direction or synchronously reversely displace away from or toward the corresponding fixed wall faces  204 . Accordingly, it can be ensured that the increase amount or the decrease amount of the capacity of the vane chamber of the active pump  101  is nearly equal to or right equal to the decrease amount or the increase amount of the capacity of the vane chamber of the passive pump  102 . In addition, a displacement resistant member  9  and a displacement resistant member  90  (such as a spring) can be additionally arranged in the increasing direction of the capacity of the vane chamber of the active pump  101  of  FIG.  7 - 3    and the decreasing direction of the capacity of the vane chamber of the passive pump  102  of  FIG.  7 - 4   . Accordingly, the displacement resistant member  9  and the displacement resistant member  90  can provide an internal preload resistance against the rotational speed ratio automatic regulation effect achieved between the active pumps  101  and the passive pumps  102 . Under such circumstance, the actually required input driving force needs to be slightly greater than the actually externally added load resistance. This preset balancing condition provides a forced downshift effect as a transmission mechanism. 
       FIG.  8    shows an integrated structure of a drive device composed of two pumps connected with each other as an assembly unit. A common engagement member  6  is engaged between the two pumps to synchronously drive the two pumps.  FIG.  8 - 1    shows an integrated structure of a drive device composed of four pumps as an assembly unit. A common engagement member  60  is engaged between the four pumps to synchronously drive the four pumps. According to the phase difference between the positions of the vanes  31  of the respective pumps in the drawings, it can be found that the suction/discharge timing between the respective pumps are just complementary to the increase/decrease of the suction/discharge amounts. Therefore, the suction/discharge amounts are equal to each other at every time point and the state is stabilized. In operation, this avoids the undulated unstable phenomenon during the driving process due to the difference between the fluid suction/discharge amounts. In addition,  FIG.  8 - 2    shows a drive device composed of four pumps arranged in an array as an assembly unit according to  FIG.  8 - 1   .  FIG.  8 - 2    is simply different from  FIG.  8 - 1    in that a common engagement member  61  is positioned around the respective pumps and engaged with the pumps to drive the pumps. This achieves a similar synchronously driving effect. Moreover,  FIG.  8 - 3    shows a linearly arranged driving mode. A common engagement member  62  is engaged between each two adjacent pumps to linearly connect the respective pumps.  FIG.  8 - 4    shows a stringed driving mode. The respective pumps are coaxially or nearly coaxially serially connected. 
     Please further refer to  FIGS.  9  to  12   , which show a second embodiment of the present invention. The second embodiment also mainly includes a fixed wall member  21 , a movable wall member  22  and a movable vane chamber sleeve  23  defining a vane chamber  230  having variable capacity with multiple eccentric vane chamber sections  2303 . A vane rotor  3  with multiple vanes  31  is arranged in the vane chamber  230 . The number and configuration of the vanes  31  correspond to the number and configuration of the eccentric vane chamber sections  2303 . Accordingly, a pump with variable suction/discharge amount, which can provide many times of suction/discharge operations in one single operation cycle is achieved. In principle, the number of the vanes  31  should be less than or equal to the number of the eccentric vane chamber sections  2303  so as to prevent the suction passage and the discharge passage appear in the same eccentric vane chamber section  2303  at the same time and communicate with each other to deteriorate the driving performance of the pump. 
     The second embodiment is most obviously different from the first embodiment in that the movable vane chamber sleeve  23  of the second embodiment can only axially displace relative to the vane rotor  3 , while failing to synchronously rotate with the vane rotor  3 . The suction/discharge passages  343 ,  344  of the second embodiment can be disposed on the suction side and the discharge side of the vane  31  of the impeller  30  of the vane rotor  3  as in the first embodiment.  FIG.  13    shows that the multi-vane pump with variable suction/discharge amount shown in  FIGS.  9  to  12    is assembled in accordance with the assembling mode of  FIG.  7   , that is, the discharge passage of the active pump  101  is in communication with the suction passage of the passive pump  102 , while the suction passage of the active pump  101  is in communication with the discharge passage of the passive pump  102 . Accordingly, as the pump of the first embodiment, a closed loop is formed between the active pump  101  and the passive pump  102  for the active pump  101  to drive the passive pump  102 . By means of the vane chamber  230  with multiple eccentric vane chamber sections  2303  and variable capacity, in operation of the closed loop, when the force difference between the driving force of the active pump  101  and the load resistance of the passive pump  102  changes, under the action of the force difference, the capacities of the eccentric vane chamber sections  2303  can be automatically modulated to a temporary balanced state after the force difference disappears. At this time, the rotational speed between the active pump  101  and the passive pump  102  is in inverse proportion to the capacity of the eccentric vane chamber sections  2303  after automatically modulated, whereby the closed loop assembly between the active pump  101  and the passive pump  102  becomes a transmission drive device capable of automatically modulating rotational speed ratio. In addition, in the second embodiment, the assembly of the active pump and the passive pump with multiple vanes  31  and multiple eccentric vane chamber sections  2303  can provide a driving force as the assembly of the multiple active pumps and the multiple passive pumps each having one single vane and one single eccentric vane chamber section as shown in  FIGS.  7 - 1  and  7 - 2   . Therefore, the second embodiment can provide stable driving effect and obviously has very high utility and value in industries. 
     According to the above design of the pump with variable suction/discharge amount of the present invention, in the condition that the original radial size is not increased, the pump with variable suction/discharge amount can truly effectively achieve the modulation function for the suction/discharge amount. The pump with variable suction/discharge amount of the present invention not only can effectively improve the shortcomings of the conventional pumps with variable suction/discharge amount, but also can be assembled to form a drive device capable of automatically modulating the rotational speed ratio between the pumps. The pump with variable suction/discharge amount of the present invention is indeed inventive and has high practical value. 
     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.