Patent Description:
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> shows a conventional rotary vane pump with variable suction/discharge amount. The rotary vane pump mainly includes a vane rotor <NUM> disposed in a cam ring <NUM> inside the pump <NUM>. An eccentric amount adjustment member <NUM> is disposed on one side of the cam ring <NUM> to push the cam ring <NUM> and adjust the eccentric amount of the eccentric amount adjustment member <NUM> to the vane rotor <NUM>. The eccentric amount is adjustable so that the fluid receiving space between the vane rotor <NUM> and the cam ring <NUM> can be modulated so as to vary the suction/discharge amount of the pump.

However, the cam ring <NUM> is mounted in the pump <NUM> 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.

<CIT> discloses a rotary motor or pump of the radial vane type for hydraulic gears comprising a case, a drum therein fixed to a shaft, a bipartite annular working space surrounding said drum, axially adjustable separating members subdividing the working space, and an axially adjustable sleeve in said annular working space and turning with the drum.

<CIT> discloses a vane cell pump or vane cell motor with a lifting ring and rotor arranged therein and with vanes arranged in radial guide slots of the rotor, which slide against the lifting ring at least during rotor rotation, and pressure zones and suction zones provided between the lifting ring and the rotor. The rotor projects beyond the lifting ring in the axial and radial direction on at least one end face of the lifting ring and the guide slots are also contained in at least a partial area of the projecting rotor part and the vanes project into these extended guide slots.

<CIT> discloses a variable displacement sliding vane pump/hydraulic motor comprising a housing which forms an eccentric chamber and a contiguous concentric chamber and contains a fluid inlet port and a fluid outlet port, a sliding wall which sits slideably inside said eccentric chamber and which contains a rotor chamber which is concentric with said concentric chamber, a rotor assembly comprising a hub which fits rotatably inside said concentric chamber and a rotor which fits rotatably inside said rotor chamber, and which contains a plurality of radial slots, a shaft which is attached concentrically to said rotor assembly, a plurality of sliding vanes which slideably fit into said radial slots in said rotor assembly, tensioning means which impress said sliding vanes outward in radial direction, lateral tensioning means which impress said sliding vanes in a direction parallel to the center line of said rotor assembly, end plates which enclose the ends of said housing to prevent fluid loss therefrom, and a means to slideably position said sliding wall within said eccentric chamber.

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.

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 and assembled with the fluid discharge passage of the other of the two pumps to form a closed active/passive drive loop. 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 operation condition that the fluid suction amount and the fluid discharge amount of the active pump and the passive pump are nearly equal to each other in any instant, the capacities of the vane chambers and the rotational speeds between the active pump and the passive pump are automatically balanced and adjusted to be in inverse proportion to each other so as to achieve the object of stable 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 chamber has at least one eccentric vane chamber section therein. The vane rotor has an impeller disposed in the vane chamber. At least one vane is disposed on the impeller. One side of the vane is a suction side, while the other side is a discharge side. 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 fixed wall member has a fixed wall end face. The fixed wall end face is disposed at one end of the fixed wall member. The fixed wall member is capped on a base seat of a support body. The fixed wall end face can be tightly attached to an end face of the impeller of the vane rotor normal to the axial direction of the vane rotor. The movable vane chamber sleeve can be fitted on the fixed wall member around the vane rotor. The movable wall member is formed with vane receiving slots. The number of the vane receiving slots is equal to the number of the vanes. A fitting hole is formed at a center of the movable wall member. The fitting hole of the movable wall member is fitted on the impeller of the vane rotor. The vanes on the impeller can slide within the vane receiving slots of the movable wall member. The movable wall member is tightly attached to the movable vane chamber sleeve and can synchronously move in the axial direction of the vane rotor with the movable vane chamber sleeve to change the capacity of the vane chamber. A rotor shaft end of the vane rotor passes through the fixed wall member. At least one of the rotor shaft ends is pivotally supported on a support body and at least one of the rotor shaft ends outward outputs power or bears power.

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, at least two suction/discharge passage openings are disposed on the impeller of the vane rotor. At least one of the suction/discharge passage openings is in communication with the suction side of the vane. At least one of the suction/discharge passage openings is in communication with the discharge side of the vane. Both the suction/discharge passage openings are in communication with outer side of the vane chamber.

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 seal the gap between the inter-contacting sections of the three parts (the vane top edge, 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, at least one pump with variable suction/discharge amount is connected and assembled to form a drive device with variable suction/discharge amount. In the drive device with variable suction/discharge amount, the sum of the areas of the movable wall faces on the suction sides of all the vanes contained in the eccentric vane chamber sections is equal to the sum of the areas of the movable wall faces on the discharge sides of all the vanes contained in the eccentric vane chamber sections.

In the above pump with variable suction/discharge amount, at least one pump with variable suction/discharge amount is connected and assembled to form a drive device with variable suction/discharge amount. In the drive device with variable suction/discharge amount, each pump has a four-time number of vanes and a number of eccentric vane chamber sections, which number is more than or equal to the number of the vanes. In the drive device with variable suction/discharge amount, each vane has another vane, the angle phase of which is <NUM>-degree different from the angle phase of the vane, that is, the vane and the other vane have a complementary relationship.

In the above pump with variable suction/discharge amount, at least one pump with variable suction/discharge amount is connected and assembled to form an active pump and at least one pump with variable suction/discharge amount are connected and assembled to form a passive pump. The active pump and the passive pump are further connected with each other to form an active/passive closed loop as a transmission drive device.

In the above transmission drive device, the sum of the areas of the movable wall faces on the suction sides of all the vanes contained in the eccentric vane chamber sections of the active pump and the passive pump is equal to the sum of the areas of the movable wall faces on the discharge sides of all the vanes contained in the eccentric vane chamber sections of 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 connected between at least one of the movable wall member and the movable vane chamber sleeve of the active pump and at least one of 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, the active pump is composed of multiple pumps with variable suction/discharge amount and all the pumps with variable suction/discharge amount are synchronously driven by a common engagement member. The passive pump is also composed of multiple pumps with variable suction/discharge amount and all the pumps with variable suction/discharge amount are synchronously driven by a common engagement member.

In the driving method employing the above drive device with variable suction/discharge amount, in a closed loop, at least one pumps with variable suction/discharge amount are assembled to form a drive device. A fluid is input into the vane chamber of the drive device. The input fluid pushes one side of the vane in the vane chamber to drive the vane rotor to rotate. At the same time, the fluid on the other side of the vane in the vane chamber is pushed out of the vane chamber by the vane to form a driving loop. The movable wall member and the movable vane chamber sleeve of the drive device are synchronously displaced in the axial direction of the vane rotor relative to the fixed wall member so as to change the capacity of the vane chamber of the drive device. Therefore, the amount of the fluid discharged from the vane chamber and the amount of the fluid sucked into the vane chamber are changed each time the vane rotor rotates by one circle. In addition, under the requirement that constant amount of fluid flows per unit time, when the capacity of the vane chamber is enlarged, the rotational speed of the vane rotor is slowed down, while when the capacity of the vane is minified, the rotational speed of the vane rotor is increased. That is, the rotational speed of the vane rotor is in inverse proportion to the capacity of the vane chamber after changed.

In the above driving method of the above drive device with variable suction/discharge amount, at least one of the movable wall member and the movable vane chamber sleeve in the drive device is forcedly pushed by an external force to make the movable wall member and the movable vane chamber sleeve synchronously displace in the axial direction of the vane rotor.

In the above driving method of the above transmission drive device, one of the pumps is set an active pump, while the other of the pumps is set a passive pump. The active pump and the passive pump are assembled to form a closed driving loop. The amount of the fluid in the closed loop is constant and unchanged. When the capacity of the vane chamber of the active pump is increased, the capacity of the vane chamber of the passive pump is reversely decreased. Therefore, in the condition that a constant amount of fluid flows within the closed loop per unit time, the rotational speed of the vane rotor of the active pump is slowed down, while the rotational speed of the vane rotor of the passive pump is increased. The rotational speed of the vane rotor of the active pump is in inverse proportion to the rotational speed of the vane rotor of the passive pump. Reversely, when the capacity of the vane chamber of the active pump is decreased, the capacity of the vane chamber of the passive pump is increased. In the condition that a constant amount of fluid flows within the closed loop per unit time, the rotational speed of the vane rotor of the active pump is increased, while the rotational speed of the vane rotor of the passive pump is slowed down. The rotational speed of the vane rotor of the active pump is also in inverse proportion to the rotational speed of the vane rotor of the passive pump.

In the above driving method of the above transmission drive device, at least one of the movable wall member and the movable vane chamber sleeve in the active pump and the passive pump are forcedly pushed by an external force to make the movable wall members and the movable vane chamber sleeves of the active pump and the passive pump synchronously displace in the axial direction of the vane rotor. The displacement distance of the movable wall member and the movable vane chamber sleeve of the active pump is equal to the displacement distance of the movable wall member and the movable vane chamber sleeve of the passive pump.

In the above driving method of the above transmission drive device, the amount of the fluid in the closed loop is constant and unchanged so that the capacity of the vane chamber of the active pump and the capacity of the vane chamber of the passive pump are synchronously changed in a complementary relationship. That is, when the movable wall member and the movable vane chamber sleeve of the active pump synchronously displace in the axial direction of the vane rotor toward the fixed wall member to minify the capacity of the vane chamber, the movable wall member and the movable vane chamber sleeve of the passive pump synchronously displace in the axial direction of the vane rotor away from the fixed wall member to enlarge the capacity of the vane chamber. The displacement distance of the movable wall member and the movable vane chamber sleeve of the active pump is equal to the displacement distance of the movable wall member and the movable vane chamber sleeve of the passive pump. Reversely, when the movable wall member and the movable vane chamber sleeve of the active pump synchronously displace in the axial direction of the vane rotor away from the fixed wall member to enlarge the capacity of the vane chamber, the movable wall member and the movable vane chamber sleeve of the passive pump synchronously displace in the axial direction of the vane rotor toward the fixed wall member to minify the capacity of the vane chamber. The displacement distance of the movable wall member and the movable vane chamber sleeve of the active pump is equal to the displacement distance of the movable wall member and the movable vane chamber sleeve of the passive pump.

The driving method employing the above transmission drive device includes steps of:.

The present invention can be best understood through the following description and accompanying drawings, wherein:.

Please refer to <FIG>. The present invention is mainly composed of a vane chamber body <NUM>, a vane rotor <NUM>, a first support body <NUM> and a second support body <NUM>. The vane chamber body <NUM> is at least composed of a fixed wall member <NUM>, a movable wall member <NUM> and a movable vane chamber sleeve <NUM>. A vane chamber <NUM> is formed in the movable vane chamber sleeve <NUM>. The capacity space of the vane chamber <NUM> is defined between the fixed wall member <NUM>, the movable wall member <NUM> and the movable vane chamber sleeve <NUM>. The movable wall member <NUM> and the movable vane chamber sleeve <NUM> are synchronously displaceable in an axial direction of the vane rotor <NUM> relative to the fixed wall member <NUM> so as to change the capacity of the space of the vane chamber <NUM>.

According to the above principle, in a first embodiment of the present invention (as shown in <FIG>), the fixed wall member <NUM> has a fixed wall seat sleeve <NUM> and a fixed wall end face <NUM>. The fixed wall end face <NUM> is disposed at one end of the fixed wall seat sleeve <NUM>. A fixed wall hole <NUM> is formed at a center of the fixed wall end face <NUM>. A base seat <NUM> is disposed on the support body <NUM>. A fixed wall end boss <NUM> is disposed on the base seat <NUM>. A boss end face <NUM> is disposed at one end of the fixed wall end boss <NUM>. A rotor shaft hole <NUM> is formed on the boss end face <NUM>. The fixed wall member <NUM> can be capped on the fixed wall end boss <NUM> of the base seat <NUM> via the fixed wall hole <NUM>, whereby the fixed wall end boss <NUM> is tightly fully plugged in the fixed wall hole <NUM> and the boss end face <NUM> and the fixed wall end face <NUM> together form a fixed wall face <NUM>.

The vane rotor <NUM> has at least one impeller <NUM> and at least one vane <NUM> assembled with the impeller <NUM>. The vane <NUM> is radially slidable and extendable/retractable. The impeller <NUM> has an end face <NUM> normal to the axis vane rotor <NUM>. The end face <NUM> can tightly attach to the fixed wall face <NUM>. The vane rotor <NUM> has a first rotor shaft end <NUM>, which is passed through the fixed wall face <NUM> and pivotally fitted in the rotor shaft hole <NUM> of the base seat <NUM>. The first rotor shaft end <NUM> is further passed through the first support body <NUM> to externally connect with a transmission member <NUM> for receiving power or bearing a load. The vane rotor <NUM> further has a second rotor shaft end <NUM>, in which a first suction/discharge port <NUM> and a second suction/discharge port <NUM> are formed. A first suction/discharge passage <NUM> and a second suction/discharge passage <NUM> are formed in the vane rotor <NUM> respectively in communication with the first and second suction/discharge ports <NUM>, <NUM>. The first and second suction/discharge passages <NUM>, <NUM> respectively extend to further communicate with a suction side and a discharge side on two sides of the vane <NUM> to form suction/discharge passage openings in communication with the vane chamber <NUM>. The second rotor shaft end <NUM> can be directly pivotally disposed on the second support body <NUM>. Alternatively, as shown in <FIG>, a fluid suction/discharge port member <NUM> can be first fitted on the second rotor shaft end <NUM> and then the fluid suction/discharge port member <NUM> is disposed on the second support body <NUM>. The fluid suction/discharge port member <NUM> has a first suction/discharge passage <NUM> and a second suction/discharge passage <NUM>. The second rotor shaft end <NUM> is pivotally fitted in the fluid suction/discharge port member <NUM> and rotated relative to the fluid suction/discharge port member <NUM>. Therefore, with the fluid suction/discharge port member <NUM> serving as a fluid connection interface (as shown in <FIG> and <FIG>), the first and second suction/discharge ports <NUM>, <NUM> of the second rotor shaft end <NUM> can correspondingly communicate with the first and second suction/discharge passages <NUM>, <NUM> of the fluid suction/discharge port member <NUM>, whereby the first and second suction/discharge ports <NUM>, <NUM> and the internal fluid passages of the second rotor shaft end <NUM> can be converted from an original rotating state into a stationary state. The first and second suction/discharge passages <NUM>, <NUM> in the vane rotor <NUM> can have various forms in addition to the above form. For example, as shown in <FIG>, the first and second suction/discharge passages <NUM>, <NUM> can communicate with outer side via the first and second rotor shaft ends <NUM>, <NUM> of the vane rotor <NUM>. Alternatively, in the second embodiment of the present invention shown in <FIG>, the first and second suction/discharge passages <NUM>, <NUM> can respectively communicate with a shaft center <NUM> and shaft non-center <NUM> of the second rotor shaft end <NUM> and then connect with the outer side directly via a suction/discharge passage <NUM> and a suction/discharge passage <NUM> disposed on the base seat <NUM> and/or the first support body <NUM>.

An end face of the movable wall member <NUM> has a movable wall face <NUM>. A fitting hole <NUM> is formed at a center of the movable wall face <NUM>, which passes through the movable wall member <NUM>. An end face of the movable vane chamber sleeve <NUM> has a vane chamber sleeve end face <NUM> in the vane chamber <NUM> of the movable vane chamber sleeve <NUM>. The vane chamber <NUM> of the movable vane chamber sleeve <NUM> can be fitted on the fixed wall seat sleeve <NUM> of the fixed wall member <NUM>, whereby the movable vane chamber sleeve <NUM> can slide along the outer circumferences of the fixed wall seat sleeve <NUM> and the impeller <NUM> of the vane rotor <NUM>. The fitted hole <NUM> of the movable wall member <NUM> is fitted on the impeller <NUM> of the vane rotor <NUM>. In addition, an inner wall of the fitting hole <NUM> is formed with a vane receiving slot <NUM> corresponding to the position where the vane <NUM> is assembled on the impeller <NUM>, whereby the vane <NUM> can extend and slide into the vane receiving slot <NUM>. On the impeller <NUM>, the movable wall face <NUM> of the movable wall member <NUM> is tightly attached to the vane chamber sleeve end face <NUM> of the movable vane chamber sleeve <NUM>, whereby the movable wall member <NUM> and the movable vane chamber sleeve <NUM> can synchronously move in the axial direction of the vane rotor <NUM> so as to change the capacity space of the vane chamber <NUM>. When the movable wall member <NUM> relatively axially gets close to the fixed wall member <NUM>, more part of the vane <NUM> can slide into the vane receiving slot <NUM> to reduce the capacity space of the vane chamber <NUM>. Reversely, when the movable wall member <NUM> relatively axially moves away from the fixed wall member <NUM>, less part of the vane <NUM> slide into the vane receiving slot <NUM> to enlarge the capacity space of the vane chamber <NUM>. The interior of the vane chamber <NUM> is defined between the movable vane chamber sleeve <NUM>, the fixed wall face204, the movable wall face <NUM> and the vane rotor <NUM>. The impeller <NUM> occupies a part of the vane chamber <NUM>. The remaining space of the vane chamber <NUM> forms at least one eccentric vane chamber section <NUM> eccentric to the axis of the vane rotor <NUM>. The vane <NUM> has a vane top edge <NUM> distal from the vane rotor <NUM>. The vane top edge <NUM> tightly attaches to the inner wall of the vane chamber <NUM> and is axially and/or circumferentially slidable relative to the inner wall of the vane chamber <NUM>. In addition, proper sealing and leakproof members can be disposed between the contacting sections of the vane <NUM> and the inner wall of the vane chamber <NUM> and between the tightly attaching or relatively displacing sections of the fixed wall member <NUM>, the movable wall member <NUM>, the movable vane chamber sleeve <NUM> and the vane rotor <NUM> so as to prevent the fluid in the operating vane chamber <NUM> from leaking through the aforesaid sections. Especially, at the inter-contacting sections of the vane top edge <NUM> of the vane <NUM>, the movable wall member <NUM> and the movable vane chamber sleeve <NUM>, the curve of the configuration of the vane top edge <NUM>, the cross-sectional curve of the vane receiving slot <NUM> of the movable wall member <NUM>, into which the vane top edge <NUM> can slide and the curve of the inner wall of the vane chamber <NUM> of the movable vane chamber sleeve <NUM> in contact with the vane top edge <NUM> are different from each other. Therefore, minor gaps exist between the inter-contacting sections of the vane top edge <NUM> of the vane <NUM>, the movable wall member <NUM> and the movable vane chamber sleeve <NUM>. As a result, in operation, the vane chamber <NUM> cannot be fully closed. In order to solve this problem, a sealing block <NUM> is disposed on the vane top edge <NUM>, which can tightly attach to the vane top edge <NUM> to synchronously slide with the vane <NUM>. The sealing block <NUM> is further restricted in the intersection path of the vane receiving slot <NUM> of the movable wall member <NUM> and the outer edge of the inner wall of the vane chamber <NUM> of the movable vane chamber sleeve <NUM>. Accordingly, in operation, the sealing block <NUM> always seals the inter-contacting sections of the vane top edge <NUM>, the vane receiving slot <NUM> and the outer edge of the inner wall of the vane chamber <NUM> and blocks the gaps to achieve good sealing and leakproof effect. A retainer member <NUM> can be assembled between the movable wall member <NUM> and the movable vane chamber sleeve <NUM> so as to keep the movable wall member <NUM> and the movable vane chamber sleeve <NUM> attach to and assemble with each other, whereby the movable wall member <NUM> and the movable vane chamber sleeve <NUM> can synchronously axially slide. (The retainer member <NUM> can have various structural forms and will not be redundantly described hereinafter).

According to the above assembly structure, in operation, when the vane rotor <NUM> drives the vane <NUM> to sweep within the eccentric vane chamber section <NUM>, the fluid on the forward side of the sweeping direction of the vane <NUM> is compressed and discharged as a discharge side. After swept, a vacuum sucking force is produced on the other side of the vane <NUM> to suck in the fluid to form a suction side. The movable wall member <NUM> is fitted on the impeller <NUM> of the vane rotor <NUM> and the movable vane chamber sleeve <NUM> is fitted on the fixed wall seat sleeve <NUM>. The movable wall member <NUM> and the movable vane chamber sleeve <NUM> can synchronously displace in the axial direction of the vane rotor <NUM>. When the movable wall face <NUM> gradually axially gets close to the fixed wall face <NUM>, the available suction/discharge capacity of the eccentric vane chamber section <NUM> is relatively gradually reduced. Reversely, when the movable wall face <NUM> gradually axially moves away from the fixed wall face <NUM>, the available suction/discharge capacity of the eccentric vane chamber section <NUM> 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 <NUM>, is formed.

Accordingly, the above pump with variable suction/discharge amount can be applied to and assembled in a fluid closed loop. An external force (forcing member <NUM> as shown in <FIG>) forcedly pushes the pump to transfer the fluid. In the transfer process of the fluid, the pressure in the vane chamber <NUM> is changed. The pushing force acts on at least one of the movable wall member <NUM> and the movable vane chamber sleeve <NUM>, whereby the movable wall member <NUM> and the movable vane chamber sleeve <NUM> displace toward or away from the fixed wall member <NUM> so as to change the capacity of the space of the vane chamber <NUM>. Accordingly, the output amount and input amount of the fluid pushed by the rotating vane rotor <NUM> to pass the vane chamber <NUM> per unit time are variable with the change of the capacity of the vane chamber <NUM>, whereby the vane rotor <NUM> can provide power transmission at different rotational speeds according to the change of the capacity of the vane chamber <NUM>, to form a transmission drive device with variable suction/discharge amount.

As shown in <FIG>, 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 <NUM> and second suction/discharge passage <NUM> 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 an active pump <NUM>, while the pump on the right side is set a passive pump <NUM> and the discharge passage of the active pump <NUM> is in communication with the suction passage of the passive pump <NUM>, the fluid on the discharges side of the vane <NUM> of the active pump <NUM> is discharged from the discharge passage of the active pump <NUM> to enter the suction passage and the suction side of the vane <NUM> of the passive pump <NUM>. Reversely, in case the discharge passage of the passive pump <NUM> is in communication with the suction passage of the active pump <NUM>, the fluid on the discharge side of the vane <NUM> of the passive pump <NUM> is discharged from the discharge passage and then flows back to the suction passage and the suction side of the vane <NUM> of the active pump <NUM>, whereby the vane chambers and the entire suction and discharge passages of the active pump <NUM> and the passive pump <NUM> form a close loop for the active pump <NUM> to drive the passive pump <NUM>. In addition, a same-direction displacement connection member <NUM> is connected between at least one of the movable wall member <NUM> and the movable vane chamber sleeve <NUM> of the active pump <NUM> and the passive pump <NUM>, whereby the movable wall member <NUM> and the movable vane chamber sleeve <NUM> of the active pump <NUM> and the passive pump <NUM> can move together in the same axial direction. In operation of the active/passive closed loop, 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 <NUM> of the active pump <NUM> will be pushed by the vane <NUM> of the rotating vane rotor <NUM> to the suction side of the passive pump <NUM>. Relatively, the liquid phase fluid on the discharge side in the eccentric vane chamber section <NUM> of the passive pump <NUM> will be pushed by the vane <NUM> of the rotating vane rotor <NUM> to the suction side of the active pump <NUM>. 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 <NUM> rotates the vane rotor <NUM> to drive the vane <NUM> to apply a push pressure to the movable vane chamber sleeve <NUM>, the fixed wall face <NUM> and the movable wall face <NUM> positioned on the discharge side of the vane <NUM> in the eccentric vane chamber section <NUM> of the active pump <NUM> and the vane face of the vane <NUM>, the movable vane chamber sleeve <NUM>, the fixed wall face <NUM> and the movable wall face <NUM> positioned on the suction side of the vane <NUM> in the eccentric vane chamber section <NUM> of the passive pump <NUM>. At the same time, after the vane <NUM> of the active pump <NUM> pushes and sweeps the eccentric vane chamber section <NUM>, a vacuum sucking force is produced. Therefore, a drawing sucking force is applied to the movable vane chamber sleeve <NUM>, the fixed wall face <NUM> and the movable wall face <NUM> positioned on the suction side of the vane <NUM> in the eccentric vane chamber section <NUM> of the active pump <NUM> and the vane face of the vane <NUM>, the movable vane chamber sleeve <NUM>, the fixed wall face <NUM> and the movable wall face <NUM> positioned on the discharge side of the vane <NUM> in the eccentric vane chamber section <NUM> of the passive pump <NUM>. The direction of the push pressure or vacuum sucking force applied to the movable vane chamber sleeve <NUM> is right normal to the axial moving direction of the movable vane chamber sleeve <NUM> so that the push pressure or vacuum sucking force cannot directly make the movable vane chamber sleeve <NUM> displace. The fixed wall face <NUM> is fixed and unmovable. Therefore, during the driving process, only the movable wall face <NUM> will bear the push pressure or the drawing vacuum sucking force to make the movable wall member <NUM> axially move. Also, the movable vane chamber sleeve <NUM> with the movable wall member <NUM> is driven to synchronously axially move toward or away from the fixed wall face <NUM>. At this time, the suction side of the vane <NUM> in the passive pump <NUM> is pushed by the push pressure, while the discharge side is drawn by the vacuum sucking force. Therefore, under the action of double application forces in the same direction, the vane <NUM> is driven to drive and rotate the vane rotor <NUM> so as to output power to the load end of the passive pump <NUM>.

At the beginning of the driving process, the passive pump <NUM> is situated in a stationary state. The vane rotor <NUM> of the active pump <NUM> starts to be rotated under the driving force, whereby the liquid phase fluid on the discharge side of the vane <NUM> starts to be pushed and compressed. At this time, in case the area of the movable wall face <NUM> on the discharge side of the vane <NUM> in the eccentric vane chamber section <NUM> of the active pump <NUM> is larger than the area of the movable wall face <NUM> on the suction side of the vane <NUM> in the eccentric vane chamber section <NUM> of the passive pump <NUM>, due to that the larger the forced area is, the greater the push pressure applied to the forced area is and due to that the vane <NUM> of the passive pump <NUM> is supported by the load resistance at this time, the pressure pushes the movable wall face <NUM> of the active pump <NUM> with larger forced area. Accordingly, the movable wall member <NUM> and the movable vane chamber sleeve <NUM> of the active pump <NUM> gradually displace away from the fixed wall face <NUM> in the axial direction of the vane rotor <NUM> to enlarge the axial space of the eccentric vane chamber section <NUM>. At the same time, a sucking force is applied to the suction side of the vane <NUM> of the passive pump <NUM>, whereby the movable wall member <NUM> and the movable vane chamber sleeve <NUM> of the passive pump <NUM> are sucked to axially displace in a direction toward the fixed wall face <NUM>. At this time, the area of the movable wall face <NUM> on the suction side of the vane <NUM> in the eccentric vane chamber section <NUM> of the active pump <NUM> is smaller than the area of the movable wall face <NUM> on the discharge side of the vane <NUM> in the eccentric vane chamber section <NUM> of the passive pump <NUM>. Therefore, after the vane <NUM> of the active pump <NUM> sweeps, the vacuum sucking force applied to the suction side of the vane <NUM> provides greater sucking driving force for the movable wall face <NUM> in the passive pump <NUM> with larger area. As a result, the movable wall member <NUM> and the movable vane chamber sleeve <NUM> of the active pump <NUM> will displace in a direction away from the fixed wall face <NUM>. The movable wall member <NUM> and the movable vane chamber sleeve <NUM> of the passive pump <NUM> will displace in a direction toward the fixed wall face <NUM>. Similarly, when the sizes of the areas of the movable wall faces <NUM> on the discharge side and the suction side of the vane <NUM> are compared with each other to be on the contrary to the above, the movable wall member <NUM> and the movable vane chamber sleeve <NUM> of the active pump <NUM> and the passive pump <NUM> will displace in a direction reverse to the above direction. During the operation process of the closed loop, the movable wall member <NUM> and the movable vane chamber sleeve <NUM> will continuously reciprocally displace in the aforesaid axial direction of the vane rotor <NUM> until the liquid phase fluid originally on the suction side of the vane <NUM> of the active pump <NUM> and the liquid phase fluid originally in the passage of the discharge side of the vane <NUM> of the passive pump <NUM> are driven and circulated and switched to be respectively on the discharge side of the vane <NUM> of the active pump <NUM> and in the passage of the suction side of the vane <NUM> of the passive pump <NUM>. In addition, after switched, in case 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 <NUM> of the active pump <NUM> and the suction side of the vane <NUM> of the passive pump <NUM> by means of the displacement due to that the same-direction displacement connection member <NUM> is connected between the active pump <NUM> and the passive pump <NUM> and the liquid is uncompressible, along with the driving of the vane <NUM> of the active pump <NUM>, the vane face on the suction side of the vane <NUM> in the passive pump <NUM> will entirely bear the push force of the liquid phase fluid to gradually push and the passive pump <NUM> and the load end thereof. Therefore, the active /passive closed loop will gradually start to operate.

Therefore, in application of the fluid closed loop composed of the above components, the external forcing member <NUM> forcedly pushes at least one of the movable wall member <NUM> and the movable vane chamber sleeve <NUM>. Alternatively, by means of the push pressure and the drawing effect of the vacuum sucking force produced in the respective vane chambers <NUM> of the active pump <NUM> and the passive pump <NUM>,the movable wall member <NUM> and the movable vane chamber sleeve <NUM> displace toward or away from the fixed wall member <NUM> so as to change the capacity of the vane chamber <NUM>. Accordingly, the respective capacities of the vane chambers of the active pump <NUM> and the passive pump <NUM> are in inverse proportion to the rotational speeds of the vane rotors <NUM> thereof. In addition, the increase/decrease changes of the capacities of the vane chambers of the active pump <NUM> and the passive pump <NUM> are complementary to each other so that the rotational speeds of the vane rotors <NUM> of the active pump <NUM> and the passive pump <NUM> are in inverse proportion to each other.

During the operation process of the active/passive pump loop, the movable wall members <NUM> and the movable vane chamber sleeves <NUM> of the active pump <NUM> and the passive pump <NUM> will continuously reciprocally displace in the axial direction of the vane rotor <NUM>. Therefore, the rotation of the passive pump <NUM> will be undulated. Moreover, in the above embodiment, each of the active pump <NUM> and the passive pump <NUM> has one single eccentric vane chamber section <NUM> and one single vane <NUM>. In case at the beginning of actuation of the passive pump <NUM>, the vane <NUM> of the passive pump <NUM> is situated in a state that the vane <NUM> is right fully inlaid in the vane rotor <NUM>, there is no vane face of the vane <NUM> in the passive pump <NUM> to bear the driving force. Under such circumstance, the active pump <NUM> is situated in an invalid idling state and cannot apply any driving force to the passive pump <NUM>. 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>, two active pumps <NUM> composed of pumps with variable suction/discharge amount (or an active pump <NUM> with two eccentric vane chamber sections <NUM>) can be coupled with two passive pumps <NUM> composed of pumps with variable suction/discharge amount (or a passive pump <NUM> with two eccentric vane chamber sections <NUM>). Alternatively, as shown in <FIG>, four active pumps <NUM> composed of pumps with variable suction/discharge amount (or an active pump <NUM> with four eccentric vane chamber sections <NUM>) can be coupled with four passive pumps <NUM> composed of pumps with variable suction/discharge amount (or a passive pump <NUM> with four eccentric vane chamber sections <NUM>). Therefore, multiple pumps with variable suction/discharge amount can be assembled to form an active pump <NUM> or multiple pumps with variable suction/discharge amount can be assembled to form a passive pump <NUM>. The sum of the areas of the movable wall faces <NUM> on the suction sides of all the eccentric vane chamber sections in each active pump <NUM> is extremely approximate to or equal to the sum of the areas of the movable wall faces <NUM> of the discharge sides in all the eccentric vane chamber sections in each passive pump <NUM>. Accordingly, at any moment of the operation process of the active pump <NUM> and the passive pump <NUM>, the sum of the capacities of the suction sides always keeps extremely approximate to or equal to the sum of the capacities of the discharge sides. Therefore, the above condition of undulated operation can be effectively improved. Also, the vane <NUM> in each pump with variable suction/discharge amount has another symmetrical vane <NUM>, which is <NUM>-degree different from the vane <NUM> and complementary to the vane <NUM>. Therefore, in operation, there is always at least one vane <NUM> extending out of the vane rotor <NUM> so that after assembled, in operation of transmission drive device of the active pump <NUM> and the passive pump <NUM>, there is always a vane face of the vane <NUM> for bearing the power without invalidate idling phenomenon of the loop. Therefore, a smoother and more stable transmission driving effect is achieved.

The above the active pump <NUM> and the passive pump <NUM> are composed of multiple pumps. The active pump and the passive pump are assembled to form the active/passive drive loop. Especially, <FIG> shows an active/passive loop form composed of four active pumps <NUM> and four passive pumps <NUM> coupled and assembled therewith. In practical arrangement, the sum of the areas of the movable wall faces <NUM> corresponding to the suction sides in all the eccentric vane chamber sections <NUM> is nearly equal to the sum of the areas of the movable wall faces <NUM> corresponding to the discharge sides in all the eccentric vane chamber sections <NUM>. This is equivalent to that the discharge amount of the liquid phase fluid in the assembly of the four active pumps <NUM> and the four passive pumps <NUM> is nearly equal to the suction amount of the liquid phase fluid in the assembly of the four active pumps <NUM> and the four passive pumps <NUM>. Accordingly, the entire loop can continuously stably operate. In the case that the driving force of the active pumps <NUM> is unchanged, while the load of the passive pumps <NUM> is increased, the sweeping speed of the vanes <NUM> of the passive pumps <NUM> will be reduced. Under such circumstance, the liquid phase fluid will accumulate on the suction sides of the vanes <NUM> of the passive pumps <NUM> to apply a capacity-enlarging push force to the movable wall faces <NUM>. In addition, the amount of the liquid phase fluid flowing from the discharge sides of the vanes <NUM> of the passive pumps <NUM> back to the suction sides of the vanes <NUM> of the active pumps <NUM> is reduced to apply a vacuum sucking force to the movable wall faces <NUM> of the active pump <NUM>. The sum of the areas of the movable wall faces <NUM> on the discharge side of the vane <NUM> in the eccentric vane chamber sections <NUM> is nearly equal to the sum of the areas of the movable wall faces <NUM> on the suction side of the vane <NUM> in the eccentric vane chamber sections <NUM> so that the total force applied to the movable wall faces <NUM> of the active pumps <NUM> is nearly equal to the total force applied to the movable wall faces <NUM> of the passive pumps <NUM>. Under the action of the capacity-enlarging push force of the passive pumps <NUM> and the vacuum sucking force of the active pumps <NUM>, the movable wall members <NUM> and the movable vane chamber sleeves <NUM> of the active pumps <NUM> displace in a direction toward the fixed wall faces <NUM> to minify the total capacity of the active pumps <NUM>. At the same time, the movable wall members <NUM> and the movable vane chamber sleeves <NUM> of the passive pumps <NUM> displace in a direction away from the fixed wall faces <NUM> to enlarge the total capacity of the passive pumps <NUM>. Therefore, the active pumps <NUM> must circularly input the power many times so as to drive the passive pumps <NUM> 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 active pumps <NUM> is unchanged, while the load of the passive pumps <NUM> is reduced, all the above operation conditions are totally reversed. That is, the active pumps <NUM> only need to circularly input the power one time for driving the passive pumps <NUM> 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 active pumps <NUM> and the passive pumps <NUM>, when the driving force and the load resistance change, the respective total capacities of the active <NUM> and the passive pumps <NUM> can be automatically adjusted so that the driving force and the load resistance can be automatically balanced with each other to form a drive device, which can automatically modulate the transmission.

As shown in <FIG>, <FIG>, <FIG>, <FIG> and <FIG>, in the condition that the suction/discharge amount per unit time of the active pump <NUM> and the suction/discharge amount per unit time of the passive pump <NUM> are nearly equal to each other, a same-direction displacement connection member <NUM> or a synchronous displacement connection member <NUM> is drivingly connected between the movable wall member <NUM> or the movable vane chamber sleeve <NUM> of the active pump <NUM> and the passive pump <NUM>. An external force is applied to the same-direction displacement connection member <NUM> or the synchronous displacement connection member <NUM> to push the same so as to force the movable wall member <NUM> or the movable vane chamber sleeve <NUM> of the active pump <NUM> and the passive pump <NUM> to respectively same-direction or synchronously reversely displace away from or toward the corresponding fixed wall faces <NUM>. Accordingly, it can be ensured that the increase amount or the decrease amount of the capacity of the vane chamber of the active pump <NUM> 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 <NUM>. In addition, a displacement resistant member <NUM> and/or a displacement resistant member <NUM> (such as a spring) can be additionally arranged in the increasing direction of the capacity of the vane chamber of the active pump <NUM> of <FIG> and the decreasing direction of the capacity of the vane chamber of the passive pump <NUM> of <FIG>. Accordingly, the displacement resistant member <NUM> and the displacement resistant member <NUM> can provide an internal preload resistance against the rotational speed ratio automatic regulation effect achieved between the active pumps <NUM> and the passive pumps <NUM>. 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> shows an integrated structure of a drive device composed of two pumps connected with each other as an assembly unit. A common engagement member <NUM> is engaged between the two pumps to synchronously drive the two pumps. <FIG> shows an integrated structure of a drive device composed of four pumps as an assembly unit. A common engagement member <NUM> is engaged between the four pumps to synchronously drive the four pumps. According to the phase difference between the positions of the vanes <NUM> 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 amount and the discharge amount. Therefore, the suction amount and the discharge amount are equal to each other at every time point and the operation is stabilized. In operation, this avoids the undulated unstable phenomenon during the driving process due to the difference between the fluid suction amount and the fluid discharge amount. In addition, <FIG> shows a drive device composed of four pumps arranged in an array as an assembly unit according to <FIG>. <FIG> is simply different from <FIG> in that a common engagement member <NUM> is positioned around the respective pumps and engaged with the pumps to drive the pumps. This achieves a similar synchronously driving effect. Moreover, <FIG> shows a linearly arranged driving mode. A common engagement member <NUM> is engaged between each two adjacent pumps to linearly connect the respective pumps. <FIG> shows a stringed driving mode. The respective pumps are coaxially or nearly coaxially serially connected.

Please further refer to <FIG>, which show a second embodiment of the present invention. The second embodiment also mainly includes a fixed wall member <NUM>, a movable wall member <NUM> and a movable vane chamber sleeve <NUM> defining a vane chamber <NUM> having variable capacity with multiple eccentric vane chamber sections <NUM>. A vane rotor <NUM> with multiple vanes <NUM> is arranged in the vane chamber <NUM>. The number and configuration of the vanes <NUM> correspond to the number and configuration of the eccentric vane chamber sections <NUM>. 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 <NUM> should be less than or equal to the number of the eccentric vane chamber sections <NUM> so as to prevent the suction passage opening and the discharge passage opening with sucking effect and discharge effect between each two vanes <NUM> appear in the same eccentric vane chamber section <NUM> at the same time to lead to communication between the suction passage opening and the discharge passage opening and deteriorate the driving performance of the pump.

The second embodiment is obviously different from the first embodiment in that : (<NUM>) The second embodiment is composed of five eccentric vane chamber sections <NUM> and four vanes <NUM> and a <NUM>-degree phase interval exists between each two of the four vanes <NUM>. Due to the design of the track of the inner wall of the five eccentric vane chamber sections <NUM>, when the vane rotor <NUM> rotates to any angle, the vane faces of at least three vanes <NUM> extend out of the impeller <NUM> to be passive by the fluid. Therefore, the second embodiment is free from the problem of the first embodiment that when the single vane <NUM> is retracted into the vane rotor <NUM>, there is no vane <NUM> to be passive by the fluid. (<NUM>) In the second embodiment, the four vanes <NUM> are arranged at <NUM>-degree phase intervals. This is equivalent to that there are two sets of vanes <NUM> and each set has two vanes <NUM>. The two vanes <NUM> of each set have <NUM>-degree phase difference and are complementary to each other. In cooperation with the design of the track of the inner wall of the five eccentric vane chamber sections <NUM>, the sum of the areas of the movable wall faces <NUM> on the discharge sides of the vanes <NUM> in the eccentric vane chamber sections <NUM> is equal to the sum of the areas of the movable wall faces <NUM> on the suction sides of the vanes <NUM> in the eccentric vane chamber sections <NUM>. Accordingly, the vane rotor <NUM> can operate in a balanced state without the condition of undulated rotation. (<NUM>) In the second embodiment, the movable vane chamber sleeve <NUM> can only axially displace relative to the vane rotor <NUM>, while failing to rotate with the vane rotor <NUM> as in the first embodiment. (<NUM>) <FIG> shows an active pump <NUM> with variable suction/discharge amount with four vanes <NUM> and five eccentric vane chamber sections <NUM> and a passive pump <NUM> with variable suction/discharge amount with four vanes <NUM> and five eccentric vane chamber sections <NUM>. The assembly of the active pump <NUM> and the passive pump <NUM> 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 <FIG>. 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.

Claim 1:
A pump with variable suction/discharge amount, which includes a vane chamber body (<NUM>) and a vane rotor (<NUM>), the vane chamber body (<NUM>) having a vane chamber (<NUM>), characterized in that the vane chamber (<NUM>) is defined between a fixed wall member (<NUM>), a movable wall member (<NUM>) and a movable vane chamber sleeve (<NUM>) in the vane chamber body (<NUM>) and having a capacity space, the vane chamber (<NUM>) being partitioned by an impeller (<NUM>) of the vane rotor (<NUM>) in the vane chamber (<NUM>) to form at least one eccentric vane chamber sections (<NUM>,<NUM>), at least one vane (<NUM>) being disposed on the impeller (<NUM>), the number of the eccentric vane chamber sections (<NUM>, <NUM>) being more than or equal to the number of the vanes (<NUM>), one side of the vanes (<NUM>) in the eccentric vane chamber sections (<NUM>, <NUM>) being a suction side, while one side of the vanes (<NUM>) in the eccentric vane chamber sections (<NUM>, <NUM>) being a discharge side, the suction side and the discharge side respectively having suction/discharge passages in communication with outer side of the pump, the fixed wall member (<NUM>) being positioned in a fixed position in the vane chamber body (<NUM>), the movable wall member (<NUM>) and the movable vane chamber sleeve (<NUM>) being displaceable in an axial direction of the vane rotor (<NUM>) relative to the fixed wall member (<NUM>) to increase/decrease and change the capacity space of the vane chamber (<NUM>), so as to form a pump with variable suction/discharge amount.