TWI831952B - Variable suction displacement pump, driving device composed of the pump and driving method thereof - Google Patents

Abstract

The present invention relates to a variable suction displacement pump, a variable speed drive device composed of the pump and a driving method thereof. It is mainly located inside an impeller pump, with a fixed wall piece, a movable wall piece and a movable wall piece. The movable impeller chamber sleeve is assembled into a chamber body with at least one impeller chamber, and then cooperates with the blade rotor installed in the impeller chamber body to form a variable suction and displacement pump in which the impeller chamber can expand and contract along the axial direction of the blade rotor; and utilize At least two of the variable suction and displacement pumps are connected and combined to form a closed circuit in which the active pump drives the passive pump. During operation, when the driving force of the active pump and the load resistance of the passive pump differ, the main , the size of the passive pump's impeller chamber will automatically expand and contract until the above-mentioned driving force and load resistance reach a balance, and under the operating conditions where the fluid suction and displacement of the active and passive pumps are nearly equal at any same instant, the active and passive pumps will The impeller chamber capacity and speed between the pumps are automatically balanced in an inversely proportional relationship, and this automatic balance adjustment can achieve the purpose of smooth variable speed driving.

Description

Variable suction displacement pump, driving device composed of the pump and driving method thereof

The present invention relates to a variable suction displacement pump and a driving device composed of the pump and a method thereof. In particular, it refers to an impeller pump composed of a fixed wall piece, a movable wall piece, a movable impeller chamber sleeve and a The impeller pump is composed of a vane rotor. The impeller pump has a vane chamber. The vane chamber can be expanded and contracted along the axial direction of the vane rotor to change the capacity of the vane chamber. The expansion and contraction of the vane chamber can change the capacity space, forming a movable impeller chamber. Variable suction and displacement pumps, and at least two of these variable suction and discharge pumps can be connected and combined to form an active and passive drive device, and then use the principle that the driving force and load resistance need to achieve a balance of forces to form a structure that can be automatically adjusted during operation Variable speed drive device for the speed ratio between the active and passive pumps.

General pumps (pumps) can be divided into two types: fixed suction and displacement pumps and variable suction and displacement pumps. Among them, variable suction and displacement pumps have been widely used in related industries due to their wide applicability; if based on the structure Type classification can be divided into two types: piston type variable suction and discharge pumps and impeller type variable suction and discharge pumps. Among them, piston type variable suction and discharge pumps usually use a variable-angle rotating swash plate during rotation. It is formed by sequentially pushing a plurality of piston-type oil pump cylinders arranged roughly in parallel; the impeller-type variable suction and discharge pump is as shown in Figure 1, which mainly includes a blade rotor 10, which is arranged between an eccentric ring 11 inside the pump 1 , one side of the eccentric ring 11 uses an eccentricity adjusting element 12 to push its eccentricity relative to the blade rotor 10 , and the adjustability of the eccentricity creates a fluid containing space between the blade rotor 10 and the eccentric ring 11 Being adjustable, the suction and displacement of the pump can be adjusted.

However, because the above-mentioned eccentric ring 11 is installed inside the pump 1, the adjustable displacement is limited to a fixed space in the pump casing. The size of the internal space directly affects and limits the pump body and The radial dimensions of all assembled components, therefore, when the application requires the manufacture of products with different maximum suction and discharge capacities, because the component commonality between pumps with different suction and discharge capacities is quite low, resulting in each new maximum suction and discharge Measuring pumps will relatively increase their manufacturing costs because most components need to be redesigned and molded. In addition, during operation, if the distance between the suction side and the discharge side of the pump is long, resulting in a too large pressure difference between them, it may cause damage. The back-and-forth radial expansion and contraction displacement of each blade during operation is too large, causing vibration or collision noise.

Based on the above-mentioned shortcomings of traditional variable suction and displacement pumps, the main purpose of the present invention is to provide a brand new impeller-type variable suction and displacement pump. In particular, the impeller chamber of the pump is configured to be telescopic along the axial direction of the blade rotor. The function of adjusting its capacity space allows the unit circulation suction and discharge volume of the fluid inside the pump to increase or decrease due to the axial change of the impeller chamber space. Therefore, when it is necessary to manufacture pumps with different suction and discharge volumes, the components must be Since the radial specifications tend to be consistent, the commonality between them is improved, which can significantly reduce the material preparation cost of manufacturing pumps with different suction and displacement. Moreover, when the demand for the maximum suction and displacement of the pump increases, only the axial direction of the pump and related components need to be changed. size can be achieved.

In addition, based on the design of the variable suction and displacement pump of the present invention, if two corresponding fluid suction inlets and discharge outlets are connected and combined between at least two correspondingly configured variable suction and displacement pumps, A closed active and passive driving circuit is formed; during the driving operation of the circuit, when a difference occurs between the driving force of the active pump and the load resistance of the passive pump, the retractable impeller chamber of the impeller body is subject to the difference force The pushing and pulling effect can cause the size of the impeller chambers of the active and passive pumps to automatically expand and contract. Until the driving force of the fluid in the active pump and the load resistance driven by the fluid in the passive pump reach a balance. At the same time, under the operating conditions where the fluid suction and displacement of the active and passive pumps are nearly equal at any same instant, the active and passive pumps will The automatic balance adjustment between the impeller chamber capacity and the rotation speed of the passive pump is in an inverse proportion, and this automatic balance adjustment can achieve the purpose of smooth variable speed drive.

In order to achieve the above purpose, the present invention provides a variable suction and displacement pump, which has a blade chamber body and a blade rotor arranged in the blade chamber body. The blade chamber body at least has a fixed wall member, a movable wall member and a movable wall member. The blade chamber is surrounded by a blade chamber sleeve. The blade chamber has at least one offset blade chamber area. The blade rotor has an impeller arranged in the blade chamber. The impeller is provided with at least one blade. One side of the blade is The suction side, the other side is the discharge side; the movable wall piece and the movable impeller chamber sleeve can be relatively displaced with the fixed wall piece along the axial direction of the blade rotor, so that the capacity of the impeller chamber can be adjusted along the blade The rotor expands and contracts in the axial direction.

According to the above variable suction and displacement pump, the fixed wall member is provided with a fixed wall end surface, the fixed wall end surface is provided at one end of the fixed wall member, and the fixed wall member is mounted on a base of the frame , the end face of the fixed wall can be closely attached to an axial vertical end face on the impeller of the blade rotor; the movable impeller chamber sleeve can be mounted on the fixed wall member and framed around the periphery of the blade rotor; The movable wall member is provided with the same number of blade receiving slots as the blades, and is provided with a set of holes in the center. The movable wall member is mounted on the impeller of the blade rotor through the set of holes, and the blades on the impeller can be mounted on the impeller. The movable wall piece slides in the vane-containing groove; the movable wall piece is in close contact with the movable vane chamber sleeve and can move synchronously along the axial direction of the vane rotor to change the capacity of the vane chamber; A rotor shaft end passes through the fixed wall piece, and at least one of the rotor shaft ends is pivoted on the frame, and at least one of the rotor shaft ends outputs power or receives power.

According to the above variable suction and displacement pump, the impeller of the vane rotor is provided with at least two entrances and exits of the suction and discharge channels. At least one of the entrances and exits of the suction and discharge channels is connected to the suction side of the blade, and at least one is connected to the discharge side of the blade. The sides are connected, and the entrance and exit of the suction and discharge channel are connected with the outside of the leaf chamber.

According to the above-mentioned variable suction displacement pump, a sealing block is provided at the location where the blade, the movable wall member and the movable chamber sleeve intersect at the same time to prevent gaps and leakage at the location where the three intersect at the same time. Fluid inside the leaf chamber.

According to the above variable suction and displacement pump, at least one of the variable suction and displacement pumps is connected and combined to form a variable suction and displacement driving device. The suction side of all the blades of the variable suction and displacement driving device is at each offset blade. The total area of the movable walls included in the chamber area is equal to the total area of the movable walls included on the discharge side of all blades in each offset blade chamber area.

According to the above variable suction and displacement pump, at least one of the variable suction and displacement pumps is connected and combined to form a variable suction and displacement driving device, and each of the variable suction and displacement driving devices has four times the number of blades and The number of offset blade chamber areas is greater than or equal to the number of blades; each blade in the variable suction and displacement driving device has another blade with a complementary relationship of 180 degrees with the angle phase of the blade.

According to the above variable suction and displacement pump, at least one of the variable suction and displacement pumps is connected to form an active pump, and at least one of the variable suction and displacement pumps is connected to form a passive pump, and then the active pump and The passive pumps are connected to form a variable speed drive device with primary and passive closed circuits.

According to the above variable speed drive device, in the active pump and the passive pump, the sum of the area of the movable walls contained in the suction side of all blades in each offset blade chamber area is equal to the sum of the area of the movable walls included in the discharge side of all blades in each offset position. The total area of the movable walls contained in the leaf chamber area is equal.

According to the above variable speed driving device, at least one of the movable wall member and the movable impeller chamber sleeve of the active pump is at least one of the movable wall member and the movable impeller chamber sleeve of the passive pump. The inter-connection has one of a synchronous displacement connecting piece and a synchronous displacement connecting piece.

According to the above variable speed driving device, at least one of the impeller chamber increasing direction of the active pump and the impeller chamber reducing direction of the passive pump is provided with a displacement damping element.

According to the above variable speed drive device, the active pump is composed of a plurality of variable suction and displacement pumps, and all variable suction and displacement pumps are synchronously driven by a common associated member; the passive pump is composed of a plurality of variable suction and displacement pumps. It is composed of a pump, and also drives all variable suction and displacement pumps synchronously with a common associated component.

The driving method of applying the above variable suction and displacement driving device is to form a driving device with at least one of the variable suction and displacement pumps in a closed circuit, and the fluid is input into the impeller chamber of the driving device. The fluid pushes one side of the blades in the blade chamber and drives the blade rotor to rotate. At the same time, the blades push the fluid on the other side of the blades in the blade chamber out of the blade chamber to form a driving circuit; the movable wall part of the driving device and the movable When the moving impeller chamber sleeve is synchronously displaced relative to the fixed wall member along the axial direction of the blade rotor, thereby changing the impeller chamber capacity of the driving device, the fluid squeezed out and sucked in every time the blade rotor in the impeller chamber rotates The quantity changes accordingly, and under the requirement of quantitative fluid flow per unit time, when the capacity of the blade chamber becomes larger, the rotation speed of the blade rotor becomes slower, and when the capacity of the blade chamber becomes smaller, the rotation speed of the blade rotor becomes faster, that is, the blade The rotation speed of the rotor is inversely proportional to the changed chamber capacity.

According to the driving method of the above-mentioned variable suction and displacement driving device, an external force is used to forcefully push at least one of the movable wall member and the movable impeller chamber sleeve of the driving device, so that the movable wall member and the movable impeller chamber cover are forced to move. The moving blade chamber sleeve is synchronously displaced along the axial direction of the blade rotor.

According to the driving method of the above-mentioned variable speed drive device, one of the pumps is set as an active pump and the other pump is set as a passive pump. The active pump and the passive pump are combined into a closed drive circuit; the change in the impeller chamber capacity of the active pump increases. is large, and the amount of fluid in the closed circuit is fixed, so that the chamber capacity of the passive pump becomes relatively small. When a fixed amount of fluid flows at the same time, the vane rotor of the active pump will be damaged. As the rotation speed slows down, the rotation speed of the vane rotor of the passive pump becomes faster, and the rotation speeds of the vane rotors of the active and passive pumps are inversely proportional to each other; conversely, when the impeller chamber capacity of the active pump becomes smaller, the impeller chamber capacity of the passive pump becomes smaller. The relative strain increases, and when a fixed amount of fluid flows at the same time, the rotation speed of the vane rotor of the active pump becomes faster, and the rotation speed of the vane rotor of the passive pump becomes slower, and the rotation speeds of the vane rotors of the active and passive pumps are also inversely proportional.

According to the driving method of the above-mentioned variable speed drive device, an external force is used to forcefully push at least one of the movable wall member and the movable impeller chamber sleeve of the active and passive pumps at the same time, so that the active and passive pumps can move The movable wall member and the movable impeller chamber sleeve are synchronously displaced along the axial direction of the blade rotor, and the synchronous displacement distances of the movable wall member and the movable impeller chamber sleeve of the active and passive pumps are equal.

According to the above-mentioned driving method of the variable speed drive device, the amount of fluid in the closed circuit is fixed, so that the changes in the chamber capacity of the active and passive pumps are synchronously changed and in a complementary relationship; that is, when The movable wall member and the movable impeller chamber sleeve of the active pump move relatively close to the fixed wall member along the axial direction of the blade rotor, and when the impeller chamber capacity is reduced, the movable wall member and the movable impeller chamber sleeve of the passive pump The movable impeller chamber sleeve also synchronously moves away from the fixed wall member along the axial direction of the blade rotor, thereby increasing the impeller chamber capacity, and the movable wall members and movable impeller chamber sleeves of the active and passive pumps The displacement distance of The movable wall member and the movable impeller chamber sleeve of the passive pump also move relative to the fixed wall member along the axial direction of the blade rotor simultaneously, thereby reducing the capacity of the impeller chamber, and the movable impeller chamber sleeve of the active and passive pumps The displacement distances of the movable wall piece and the movable chamber cover are the same.

According to the above driving method, the steps can be: (1) The variable speed driving device is operated, and a difference occurs between the driving force of the active pump and the load resistance of the passive pump; (2) Under the action of the difference between the driving force and the load resistance, the The movable wall parts and movable chamber sleeves of the active and passive pumps are pulled by the extrusion thrust and vacuum suction force generated inside the impeller chamber, causing the movable wall parts and movable blade chamber sleeves of the active and passive pumps to undergo synchronous displacement. , which jointly causes the capacity of the impeller chambers of the active and passive pumps to be pulled by the difference in force, and automatically produces regulatory changes; (3) In a closed circuit, the capacity of the impeller chambers of the active and passive pumps is affected by the force. Under the balancing effect, it is finally automatically adjusted to make the driving force of the active pump equal to the load resistance of the passive pump. At this time, the chamber capacity and speed between the active and passive pumps are also automatically adjusted to achieve an inverse relationship. operation.

The detailed structure of the present invention is described below with reference to the drawings of possible embodiments of the present invention.

1:Pump

10:Blade rotor

101:Active pump

102: Passive pump

11: Eccentric ring

12: Eccentricity adjustment component

2:Chamber body

204: Fixed wall

21: Fixed wall parts

211: Fixed wall seat cover

212: Fixed wall end face

213: Fixed wall hole

22: Movable wall pieces

221: Movable wall

222:Treat hole

2221:leaf trough

23: Removable leaf chamber cover

230:Ye Shi

2301, 2303: Offset leaf chamber area

2302: Leaf chamber sleeve end face

3: Blade rotor

30: Impeller

301: Axial vertical end face

31: blade

311:Blade top edge

33:Rotor shaft end

34:Rotor shaft end

341: First suction and discharge port

342: Second suction and discharge port

343, 344: Suction and discharge channel

345:Shaft center

346: Non-axis center

35: Fluid suction and discharge port parts

351: First suction and discharge port

352: Second suction and discharge port

36: Transmission components

37:Sealing block

4. 40: Frame

41:Pedestal

410, 4100: Suction and discharge port

411: Fixed wall end column

4110: Column end face

412:Rotor shaft hole

5: Fixtures

6, 60, 61, 62: Commonly related parts

8: External force forcing component

80: Co-directional displacement coupling

800: Synchronous displacement coupling

9. 90: Displacement damping element

Figure 1 is a schematic structural diagram of a traditional variable suction displacement pump.

Figure 2 is an exploded perspective view of the structure of the first possible embodiment of the present invention.

Figure 3 is a partially assembled perspective view of the structure of the embodiment shown in Figure 2 .

Figure 4 is a cross-sectional view of the combined structure of the embodiment shown in Figure 2, where the space in the leaf chamber is relatively smaller than that shown in Figure 4-l.

Figure 4-1 is a cross-sectional view of the combined structure of the embodiment shown in Figure 2, where the space in the leaf chamber is relatively larger than that shown in Figure 4.

Figure 5 is a schematic diagram of the combined structure of the embodiment shown in Figure 2, using a forcing mechanism to actuate the movable wall member.

Figure 6 is a schematic diagram of the combined structure of the embodiment shown in Figure 2, in which the suction and discharge channels are connected outward from the two axial ends of the blade rotor.

Figure 7 is a schematic diagram of the active and passive connection relationship between an active pump and a passive pump using the combined structure of the embodiment shown in Figure 2; the movable wall parts and movable impeller chamber sleeves of the active and passive pumps are At least one of the two is connected with a same-direction displacement connecting piece.

Figure 7-1 is a schematic diagram of the active and passive connection relationship between two active pumps and two passive pumps using the combined structure of the embodiment shown in Figure 2; the movable wall parts of the active and passive pumps and the movable At least one of the two movable leaf chamber sleeves is connected with a same-direction displacement connecting piece.

Figure 7-2 is a schematic diagram of the active and passive connection relationship between four active pumps and four passive pumps using the combined structure of the embodiment shown in Figure 2; the movable wall parts of the active and passive pumps and the movable At least one of the two movable leaf chamber sleeves is connected with a synchronous displacement connecting piece.

Figure 7-3 is a schematic view of the combined structure of the embodiment shown in Figure 7, especially a displacement damping element in the expansion direction of the impeller chamber of the active pump; the movable wall parts of the main and passive pumps A same-direction displacement connecting piece is connected to at least one of the movable leaf chamber sleeves.

Figure 7-4 is a schematic view of the combined structure of the embodiment shown in Figure 7, especially a displacement damping element in the direction of shrinkage of the passive pump's impeller chamber; the main part is the movable wall member of the passive pump. A same-direction displacement connecting piece is connected to at least one of the movable leaf chamber sleeves.

Figure 8 is a schematic diagram of the relationship between two pumps combined into an active pump end using the combined structure of the embodiment shown in Figure 2 and driven synchronously by a common associated component.

Figure 8-1 is a schematic diagram of the relationship between four pumps assembled into an array-type active pump end using the combined structure of the embodiment shown in Figure 2, and driven synchronously by a common associated component in the center.

Figure 8-2 is a schematic diagram of the relationship in which four pumps are combined into an array-type active pump end using the combined structure of the embodiment shown in Figure 2, and are driven synchronously by a common associated component at the periphery.

Figure 8-3 is a schematic diagram of the relationship between four pumps combined into a linearly arranged active pump end using the combination structure of the embodiment shown in Figure 2.

Figure 8-4 is a schematic diagram of the relationship between four pumps assembled into an active pump end arranged in series by using the combined structure of the first embodiment of the present invention, changing the shape of one shaft end and the fluid suction and discharge port components.

Figure 9 is an exploded perspective view of the structure of the second possible embodiment of the present invention.

Figure 10 is a partially assembled perspective view of the structure of the embodiment shown in Figure 9 .

Figure 11 is a schematic axial cross-sectional view of the assembled structure of the embodiment shown in Figure 9 in its assembled state.

Figure 12 is a schematic radial cross-sectional view of the combined structure of the embodiment shown in Figure 11, taken along A-A.

Figure 13 is a schematic diagram of the active-passive connection relationship using an active pump combined with a passive pump based on the combined structure of the embodiment shown in Figure 10.

As shown in Figures 2 to 4, the present invention is mainly composed of a blade chamber body 2, a blade rotor 3 and a frame body 4, 40. The blade chamber body 2 is at least composed of a fixed wall member 21 and a movable wall. It is formed by a member 22 and a movable leaf chamber cover 23. The movable leaf chamber cover 23 is provided with a leaf chamber 230 inside, and is composed of the fixed wall member 21, the movable wall member 22 and the movable leaf chamber cover 23. The capacity space of the blade chamber 230, and the movable wall member 22 and the movable blade chamber sleeve 23 can simultaneously move relative to the fixed wall member 21 along the axial direction of the blade rotor 3 to change the group enclosed by the blade chamber 230. The size of the capacity space.

Based on the above principles, the fixed wall member 21 of the first embodiment of the present invention (Figures 2 to 5) is provided with a fixed wall seat cover 211 and a fixed wall end surface 212. The fixed wall end surface 212 is provided on the fixed wall. seat One end of the sleeve 211, and a fixed wall hole 213 is provided in the center of the fixed wall end surface 212; the frame 4 is provided with a base 41, and a fixed wall end column 411 is provided on the base 41. On the fixed wall end column One end of 411 is provided with a column end face 4110, and a rotor shaft hole 412 is provided on the column end face 4110; the fixed wall member 21 can be mounted on the fixed wall end column 411 of the base 41 by using the fixed wall hole 213. The fixed wall end column 411 is tightly packed into the fixed wall hole 213 , so that the column end surface 4110 and the fixed wall end surface 212 together form a fixed wall surface 204 .

The blade rotor 3 has at least one impeller 30, and the impeller 30 can be combined with at least one radially telescopic blade 31, so that an axial vertical end surface 301 of the impeller 30 can be closely attached to the above-mentioned blade. The fixed wall 204, at the same time, one of the rotor shaft ends 33 of the blade rotor 3 can pass through the fixed wall 204 and be pivoted in the rotor shaft hole 412 of the base 41, and pass through the frame 4 to connect the transmission elements outward. 36 to receive power or bear load; the other rotor shaft end 34 of the blade rotor 3 can be provided with a first suction and discharge port 341 and a second suction and discharge port 342 at the same time, and the first and second suction and discharge ports 341 and 342 are respectively connected. The suction and discharge channels 343 and 344 inside the blade rotor 3 are respectively extended to connect to the suction and discharge sides of both sides of the blade 31, forming the entrance and exit of the suction and discharge channels connected to the blade chamber 230; In addition to the rotor shaft end 34 being directly pivoted on the other end frame 40, as shown in Figures 2 to 5, a fluid suction and discharge opening component 35 can be fitted to the rotor shaft end 34 in advance, and then The fluid suction and discharge port component 35 is mounted on the frame 40; the fluid suction and discharge port component 35 allows the rotor shaft end 34 to pivot relative to its interior, thereby allowing the first end of the rotor shaft end 34 to rotate relative to the rotor shaft end 34. The two suction and discharge ports 341 and 342 are connected from their original axial rotation state through the intermediary of the fluid suction and discharge port component 35, and are connected correspondingly to the first suction and discharge port passage 351 and the second suction and discharge port passage 352 of the fluid suction and discharge port component 35, The rotating internal fluid passage is transformed into a static and non-rotating fluid connection interface (please refer to Figures 4 to 5); however, the implementation of these suction and discharge channels 343, 344 in the blade rotor 3 In addition to the above-mentioned type, there are countless feasible For example, as shown in Figure 6, the suction and discharge passages 343 and 344 are connected to the outside through the two rotor shaft ends 33 and 34 of the blade rotor 3 respectively; it can also be used as in the second embodiment of the present invention. In the embodiment shown in the figure, the suction and discharge passages 343 and 344 are respectively connected to the shaft center 345 and the non-shaft center 346 of the same rotor shaft end 34, and then directly through the base 41 and/or the frame 4. The external suction and discharge passages 410 and 4100 are connected outward.

An end surface of the movable wall member 22 is provided with a movable wall surface 221, and a sleeve hole 222 penetrating the movable wall member 22 is provided at the center of the movable wall member 22; the leaf chamber 230 is located between the movable leaf chamber sleeve 23. Inside, and on one end surface of the movable leaf chamber cover 23, there is a leaf chamber cover end face 2302, the leaf chamber 230 of the movable leaf chamber cover 23 can be fitted on the fixed wall seat cover 211 of the fixed wall member 21 , so that the movable impeller chamber cover 23 can slide on the fixed wall seat cover 211 and on the periphery of the impeller 30 of the blade rotor 3; 30, and a blade receiving groove 2221 is provided on the peripheral side of the sleeve hole 222. The blade receiving groove 2221 corresponds to the position of the assembled blade 31 on the impeller 30, allowing the blade 31 to extend into the blade receiving groove 2221 for operation. Sliding; the movable wall piece 22 can be on the impeller 30, with the movable wall surface 221 closely abutting the end surface 2302 of the movable blade chamber sleeve 23, so that the movable wall piece 22 and the movable blade chamber sleeve can The movable blade chamber sleeve 23 can move synchronously along the axial direction of the blade rotor 3 to change the capacity space of the blade chamber 230. When the movable wall member 22 is relatively axially close to the fixed wall member 21, the blades can be moved More parts of 31 can be slidably accommodated in the leaf slot 2221, and the capacity space of the leaf chamber 230 becomes smaller; conversely, when the movable wall member 22 is relatively axially away from the fixed wall member 21, the movable wall member 22 can be allowed to A smaller part of the blade 31 is slidably accommodated in the blade groove 2221, and the capacity space of the blade chamber 230 becomes larger; the interior of the blade chamber 230 is surrounded by the fixed wall end surface 212, the movable blade chamber cover 23, and the movable blade chamber cover 23. Between the moving wall 221 and the blade rotor 3, and deducting the remaining space of the blade chamber 230 occupied by the impeller 30, at least one offset blade chamber area 2301 that is offset from the axis of the blade rotor 3 can be formed; the above-mentioned blades 31 are far away from each other. The top edge 311 of one of the blades of the blade rotor 3 is closely attached to the blade chamber. 230, and can slide relative to the inner wall of the leaf chamber 230 in the axial and/or circumferential directions; and the above-mentioned contact parts of the blade 31 and the inner wall of the leaf chamber 230, as well as the fixed wall member 21 and the movable wall Parts 22, movable impeller chamber sleeve 23, blade rotor 3 and other parts that are in close contact or relatively displaced can be equipped with appropriate sealing and leak-proof components to prevent the fluid inside the impeller chamber 230 from leaking at the above-mentioned parts during operation. Phenomenon; especially at the point where the blade top edge 311 of the blade 31 intersects with the movable wall member 22 and the movable chamber cover 23, due to the curve of the surface of the blade top edge 311, it penetrates the blade top edge 311 The cross-sectional curves of the blade groove 2221 of the movable wall member 22 and the inner wall curve of the blade chamber 230 of the movable blade chamber sleeve 23 that is in contact with the blade top edge 311 are different, resulting in the intersection of the three parts. There will be a tiny gap, so that the blade chamber 230 cannot be completely closed during operation; for this reason, the present invention provides a seal on the blade top edge 311 that can slide synchronously with the blade top edge 311 and the blade 31 Block 37, the sealing block 37 is further limited in the intersection path of the vane groove 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 cover 23, so that it can be operated during operation. , is blocked at any time at the intersection of the above-mentioned blade top edge 311, the blade receiving groove 2221, and the outer edge of the inner wall of the blade chamber 230, which can produce a good sealing and anti-leakage effect on the above-mentioned gap. The movable wall member 22 and the movable chamber cover 23 can be combined by using a fixing member 5 (the structure of the fixing member 5 can have many feasible types, which will not be described in detail here) to maintain the two. The above-mentioned axial sliding can be performed synchronously in a close combination relationship.

According to the above combined structure, when the blade rotor 3 drives the blade 31 to sweep in the offset blade chamber area 2301 during operation, the fluid located on the forward side of the sweeping direction of the blade 31 is extruded and discharged to form the discharge side, and The vacuum suction force generated by sweeping on the other side of the blade 31 sucks the fluid into the suction side; the movable wall member 22 is fitted on the impeller 30 of the blade rotor 3 and is fitted on the fixed wall seat cover The movable chamber sleeve 23 on the blade 211 can synchronously displace along the axial direction of the blade rotor 3. When the movable wall 221 gradually approaches the fixed wall 204 axially, the suction and discharge capacity of the offset chamber area 2301 That is phase On the other hand, if the movable wall 221 gradually axially moves away from the fixed wall 204, the suction and discharge capacity of the offset chamber area 2301 will gradually increase, thereby forming an axially telescopic suction and discharge capacity of the leaf chamber 230. Variable suction displacement pump.

Therefore, using the variable suction displacement pump described above, if the pump is combined in a fluid closed circuit and forced by an external force (such as the external force forcing element 8 in Figure 5), the inside of the impeller chamber 230 The pressure changes, and the push acts on at least one of the movable wall member 22 and the movable leaf chamber cover 23, causing the movable wall member 22 and the movable leaf chamber cover 23 to generate pressure relative to the fixed wall member 21. The displacement of approaching or moving away changes the size of the capacity space of the impeller chamber 230, so that within a unit time, the output and input amounts of the fluid pushed through the impeller chamber 230 by the rotation of the blade rotor 3 can be adjusted according to the Changes in the capacity of the impeller chamber 230 produce differences, so that the blade rotor 3 can generate power transmission at different speeds according to changes in the capacity of the impeller chamber 230, forming a variable suction and displacement driving device.

What is shown in Figure 7 is that the variable suction and displacement pump formed above is arranged and connected in two corresponding ways, and the first suction and discharge outlet passages 351 and the second suction and discharge outlet passages of the two correspondingly arranged pumps are The suction inlet and discharge outlet set in 352 are interconnected with each other; therefore, if the left pump of the two correspondingly configured pumps is set as the active pump 101 and the other right pump is set as the passive pump 102 and connect the discharge port of the active pump 101 to the suction port of the passive pump 102, so that the fluid on the discharge side of the blade 31 of the active pump 101 is discharged from the discharge port and enters the suction port of the passive pump 102 and the suction side of the blade 31; on the contrary, the discharge port of the passive pump 102 is connected to the suction port of the active pump 101, so that the fluid on the discharge side of the blade 31 of the passive pump 102 is discharged from its discharge port and then flows to the active pump 101. The suction inlet of the pump 101 and the suction side of the blade 31 make the chambers and the overall suction and discharge passages of the active and passive pumps 101 and 102 form a closed circuit in which the active pump 101 drives the passive pump 102, and in the active and passive pumps Between at least one of the movable wall members 22 and the movable chamber sleeve 23 of 101 and 102, the connection between the movable wall member 22 and the movable chamber cover 23 can be made by moving the displacement connecting member 80 together. are connected so that the movable wall members 22 of the active and passive pumps 101 and 102 and the movable chamber sleeve 23 can move together in the same axial direction; when the closed loop of the active and passive pumps is in operation, if the fluid used is a liquid fluid, then the liquid fluid on the discharge side of the offset chamber area 2301 of the active pump 101 will be pushed to the suction side of the passive pump 102 by its blades 31 as the blade rotor 3 rotates; on the contrary, the The liquid fluid on the discharge side in the offset chamber area 2301 of the passive pump 102 is also pushed to the suction side of the active pump 101 by its blades 31 as the blade rotor 3 rotates, forming a complete active and passive pump liquid fluid. drive circuit.

When the above-mentioned driving circuit is running, the driving force of the active pump 101 rotates the blade rotor 3 and drives the blades 31. The fixed wall end surface 212, The movable impeller chamber cover 23 and the movable wall surface 221, as well as the offset impeller chamber area 2301 of the passive pump 102, the blade surface of the blade 31 and the fixed wall end surface 212 on the suction side of the blade 31, the movable impeller chamber cover 23 and the movable impeller chamber cover 230. The moving wall 221 exerts pushing pressure; at the same time, because the blade 31 of the active pump 101 pushes and sweeps through the offset blade chamber area 2301, a vacuum suction force is generated. The offset blade chamber area 2301 of the active pump 101 is located on the suction side of the blade 31. The fixed wall end surface 212, the movable impeller chamber sleeve 23 and the movable wall surface 221, as well as the offset impeller chamber area 2301 of the passive pump 102, the blade surface of the blade 31 located on the discharge side of the blade 31 and the fixed wall end surface 212, movable The leaf chamber sleeve 23 and the movable wall 221 form a traction suction force; because the pushing pressure or vacuum suction direction of the movable leaf chamber sleeve 23 is exactly perpendicular to the axial movement direction of the movable leaf chamber sleeve 23, so the drive The pushing pressure or vacuum suction force cannot directly cause the displacement of the movable chamber sleeve 23, and the fixed wall end surface 212 is fixed and immovable, so only the movable wall surface 221 will bear the traction of the pushing pressure or vacuum suction force during the driving process, so that The movable wall member 22 moves axially, which also causes the movable chamber sleeve 23 to move axially toward or away from the fixed wall end face 212 in synchronization with the movable wall member 22; at this moment, the inside of the passive pump 102 The suction side of the blade 31 is pushed by the pushing pressure, and the discharge side on the other side is sucked by the vacuum. Due to the traction of force, the blade 31 is driven by double forces in the same direction and drives the blade rotor 3 to rotate, thereby outputting power to the load end of the passive pump 102.

When the above-mentioned driving circuit is initially driven, the passive pump 102 is still in a stationary state, and the vane rotor 3 of the active pump 101 begins to be rotated by the driving force, so that the liquid fluid on the discharge side of the vane 31 begins to be pushed. If At this time, the area of the movable wall 221 in the offset chamber area 2301 of the active pump 101 on the discharge side of the blade 31 is larger than the movable wall surface of the offset chamber area 2301 of the passive pump 102 on the suction side of the blade 31 221 area, the larger the force-bearing area, the greater the pressure it is pushed. At this time, the blade 31 of the passive pump 102 is supported by the load resistance, so that the pressure can be transferred to the active pump 101 with a larger force-bearing area. The movable wall 221 pushes, causing the movable wall 22 of the active pump 101 together with the movable chamber sleeve 23 to gradually move along the axis of the blade rotor 3 in a direction away from the fixed wall end surface 212, thereby expanding the offset chamber area. The axial space of 2301 also creates a vacuum suction force on the suction side of the blade 31 of the passive pump 102, sucking the movable wall member 22 of the passive pump 102 together with the movable chamber sleeve 23 in a direction close to the fixed wall end surface 212 Displacement; on the other hand, the area of the movable wall 221 in the offset chamber area 2301 of the active pump 101 on the suction side of the blade 31 is smaller than the area of the movable wall 221 in the offset chamber area 2301 of the passive pump 102 on the discharge side of the blade 31 The area of the movable wall 221 of the passive pump 102 is such that the vacuum suction force generated on the suction side of the active pump 101 after the blade 31 is swept forms a greater suction force on the larger area of the movable wall 221 of the passive pump 102, resulting in The movable wall member 22 of the active pump 101 together with the movable impeller chamber sleeve 23 will be displaced away from the fixed wall end face 212, and the movable wall member 22 of the passive pump 102 together with the movable impeller chamber sleeve 23 will be moved closer to the fixed wall. The direction displacement of the wall end surface 212; similarly, when the active and passive pumps 101 and 102 are located in the offset chamber area 2301, the area size of the movable wall surface 221 located on the discharge side and the suction side of the blade 31 is opposite to the above. , then the movable wall member 22 and the movable impeller chamber cover 23 of the active and passive pumps 101 and 102 will be displaced in the opposite direction as mentioned above; during the operation of the closed circuit, the movable wall member 22 together with the movable impeller chamber cover 23 will hold The above-mentioned reciprocating displacement along the axial direction of the vane rotor 3 continues until the liquid fluid originally located in the suction side of the vane 31 of the active pump 101 and the discharge side of the vane 31 of the passive pump 102 is replaced by the drive cycle conversion. If the volume of liquid fluid in the passage between 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 is greater than that of the discharge side of the vane 31 of the active pump 101 and the vane 31 of the passive pump 102 after replacement, When the maximum total volume modulated by the axial movement of the suction side is reached, due to the traction of the coupling member 80 that moves in the same direction between the active and passive pumps 101 and 102 and the incompressible characteristics of the liquid, as the active pump 101 moves When the blade 31 is driven, all the driving force of the liquid fluid will be borne by the suction side blade surface of the blade 31 in the passive pump 102, thereby gradually pushing the passive pump 102 and its load end, so that the closed circuits of the active and passive pumps gradually operate. .

Therefore, the fluid closed circuit composed of the above combination is used, and the external force forcing element 8 is used to forcefully push at least one of the movable wall members 22 and the movable impeller chamber sleeve 23, or the active and passive pumps 101, 102 The pushing pressure and vacuum suction force generated inside the respective leaf chambers 230 cause the movable wall member 22 and the movable leaf chamber sleeve 23 to move toward or away from the fixed wall member 21 , and then change the size of the impeller chambers 230, so that the active and passive pumps 101 and 102 can respectively change according to the capacities of their impeller chambers 230, so that the respective impeller chamber capacities of the active and passive pumps 101 and 102 can be changed. The rotation speed of the vane rotor 3 changes in inverse proportion, and the changes in the impeller chamber capacity between the active and passive pumps 101 and 102 are complementary to each other, so that the rotation speed of the vane rotor 3 between the active and passive pumps 101 and 102 is complementary. The speed is inversely proportional.

During the operation of the above-mentioned active and passive pump circuits, the movable wall member 22 and the movable impeller chamber sleeve 23 of the active and passive pumps 101 and 102 will continue to undergo reciprocating displacement along the axial direction of the blade rotor 3, resulting in this The rotation of the passive pump 102 occurs suddenly and slowly; and in the above embodiment, the active and passive pumps 101 and 102 both have a single offset impeller chamber area 2301 and a single blade 31. If the passive pump 102 initially When it is first started, the blades 31 are all inserted into the blade rotor 3. At this time, the active pump 101 will always be idle because there are no blades 31 in the passive pump 102 to bear the driving force. The passive pump 102 cannot apply driving force, causing the entire circuit to become inactive. In order to avoid the above-mentioned fast and slow or ineffective operation of the circuit, the two variable suction and discharge can be combined as shown in Figure 7-1. The active pump 101 formed by a displacement pump (or the active pump 101 with twice the number of offset impeller chamber areas 2301) is coupled with the passive pump 102 formed by two variable suction and displacement pumps (or the active pump 101 with twice the number of offset impeller chambers 2301). The combination type of the passive pump 102 in the area 2301), and Figure 7-2 shows the active pump 101 formed by four variable suction and displacement pumps (or the active pump 101 with four times the offset impeller area 2301 ) is a combined form of a passive pump 102 formed by connecting four variable suction and displacement pumps (or a passive pump 102 with four times the number of offset impeller chamber areas 2301), which is composed of multiple variable suction and displacement pumps. The active pump 101, or the passive pump 102 composed of multiple variable suction and displacement pumps, allows the total area of the movable wall 221 on the suction side of all offset impeller chamber areas in the active pump 101 and the passive pump 102 to be The sum of the areas of the movable walls 221 on the discharge side is very close to or equal to that of the active and passive pumps 101 and 102 at any time during operation. The sum of the volumes of the suction side is very close to or equal to the discharge This can effectively improve the above-mentioned situation of sudden speed and slowness; at the same time, the blades 31 in each variable suction and displacement pump have another symmetrical blade 31 that is 180 degrees apart to complement it and maintain During operation, at least one blade 31 must extend out of the blade rotor 3, so that the combined variable speed drive device with active and passive pumps 101, 102 can continue to have the blade surface of the blade 31 bear power during operation, and will not occur. The phenomenon of ineffective idling of the circuit is eliminated to achieve a smoother and more stable driving effect.

The main and passive pumps 101 and 102 composed of the above-mentioned multiple pump combinations, and the main and passive pump drive circuits composed of them, especially the active pump 101 formed by four pumps in Figure 7-2 is connected to the four pumps. The formed passive pump 102 is combined into a circuit type with an active pump 101 and a passive pump 102. In terms of implementation settings, the sum of the areas of the movable walls 221 corresponding to the suction sides of all offset impeller chamber areas 2301 is equal to The sum of the areas of the movable walls 221 corresponding to the discharge sides of all offset impeller chamber areas 2301 is almost equal. This is also equivalent to the combination of the active pump 101 with four pumps and the passive pump 102 with four pumps. The liquid in it is The fluid discharge volume is nearly equal to the suction volume, which allows the overall circuit to continue to operate stably. If the driving force of the active pump 101 remains unchanged, but the load of the passive pump 102 increases, the sweeping speed of each blade 31 of the passive pump 102 decreases. , forming the suction side of each blade 31 of the passive pump 102 to generate an amplified thrust on the movable wall 221 due to the accumulation of liquid fluid, and the backflow from the discharge side of each blade 31 of the passive pump 102 to the suction of each blade 31 of the active pump 101 The liquid fluid on the side of the active pump 101 decreases, forming a vacuum suction force on each movable wall surface 221 of the active pump 101. Since the sum of the areas of the movable wall surfaces 221 on the discharge side and the suction side in the offset impeller chamber area 2301 is almost equal, it is equivalent to the active and passive pumps. The sum of the forces on the movable walls 221 of 101 and 102 is almost equal. Under the action of the capacity expansion thrust of the passive pump 102 and the vacuum suction of the active pump 101, each movable wall member 22 of the active pump 101 together with the movable chamber sleeve 23 is displaced in the direction closer to the fixed wall end face 212, reducing the total pump capacity of the active pump 101; at the same time, each movable wall member 22 of the passive pump 102 together with the movable chamber sleeve 23 is displaced in a direction away from the fixed wall end face 212, increasing the The total pump capacity of the passive pump 102 requires multiple power cycle inputs from the active pump 101 to drive the passive pump 102 to output one power cycle, producing an effect similar to a power transmission downshift drive; conversely, if the driving force of the active pump 101 remains unchanged, However, when the load of the passive pump 102 is reduced, all the above operation conditions are completely opposite, causing the active pump 101 to input power once, which can drive the passive pump 102 to output multiple power cycles, producing an effect similar to the power transmission upshift drive; from the above It can be seen that in the closed driving circuit operation of the active and passive pumps 101 and 102 combination, when the driving force and load resistance change, the respective total capacities of the active and passive pumps 101 and 102 can be automatically adjusted to make the driving force and load The resistance automatically reaches a balanced state and becomes a variable speed drive device that can automatically adjust the speed.

Figures 7 to 7-4 show that under the condition that the suction and displacement per unit time of the above-mentioned active and passive pumps 101 and 102 are almost the same, the displacement coupling 80 or the synchronous displacement coupling is used together. 800 is linked between the movable wall member 22 or the movable chamber sleeve 23 of the active and passive pumps 101 and 102, and by pushing the same direction displacement connecting member 80 or the synchronous displacement connecting member 800 through external force, the main and passive pumps 101 and 102 can be forced to move. The movable wall members 22 or the movable chamber sleeves 23 of the passive pumps 101 and 102 perform mutually opposite displacements away from or close to their corresponding fixed wall end faces 212 in the same direction or synchronously, thereby ensuring that the active The increase or decrease value of the impeller chamber capacity of the pump 101 is almost equal to or the same as the decrease or increase value of the impeller chamber capacity of the passive pump 102; in addition, the increase direction of the impeller chamber capacity of the active pump 101 in Figure 7-3, and Figure 7 - In the direction of the reduction of the chamber capacity of the passive pump 102 in Figure 4, a displacement damping element 9, 90 (such as a spring) can be added to make the main body of the present invention and the passive pump 101, 102 automatically adjust. The function of the rotational speed ratio can produce a pre-loaded internal load resistance due to the installation of the displacement damping elements 9 and 90, thereby producing a preset balance condition in which the actual input driving force needs to be slightly larger than the actual external load resistance, so as to Creates a forced downshift effect similar to that of a transmission mechanism.

What is shown in Figure 8 is a schematic diagram of the integrated structure of the active device with two adjacent pumps as a combined unit. The two pumps are synchronously driven by a common associated member 6; what is shown in Figure 8-1 is A schematic diagram of the integrated structure of the active device with four pumps as a combined unit. The position of the blades 31 of each pump in the figure is a simple representation of the above-mentioned phase difference, and then a common correlation member 60 between the four pumps is used to drive it synchronously. , it can be found that the suction and discharge states between the pumps can complement each other to increase and decrease the suction and discharge volumes, so that the suction volume and the discharge volume at each time point are equal, so that the operation tends to be stable, and the operation is avoided due to the fluid suction volume and the displacement volume. There is a difference in displacement, which causes instability in the driving process. The one shown in Figure 8-2 is an active device based on the four pumps shown in Figure 8-1 or an array combination unit. , only its driving system is driven by another common associated member 61 connected at the periphery of each pump to achieve a similar synchronous driving effect; in addition, what is shown in Figure 8-3 is a linear arrangement driving mode, two phases. There is an adjacent common correlation member 62 between adjacent pumps. Each pump is connected linearly; the one shown in Figure 8-4 is a series type, and the pumps are connected in series with a coaxial or nearly coaxial relationship.

Please refer to Figures 9 to 12 again, which are the second possible embodiment of the present invention. They are mainly composed of a fixed wall member 21, a movable wall member 22 and a movable chamber cover 23. A variable-capacity blade chamber 230 with a plurality of offset blade chamber areas 2303, and according to the number and form of the offset blade chamber areas 2303, a multi-blade blade rotor 3 with a plurality of blades 31 is disposed in the blade chamber 230 , thereby forming a variable suction and displacement pump that can complete multiple suction and discharge actions in a single operating cycle. In principle, the number of blades 31 should be less than or equal to the number of offset blade chamber areas 2303 to avoid The entrances and exits of the suction and discharge passages between each two blades 31 appear in the same offset chamber area 2303 at the same time, causing the suction and discharge interconnection phenomenon and reducing the pump driving efficiency.

The second possible embodiment has the following significant differences from the first embodiment: (1) The second embodiment has five offset blade chamber areas 2303 and four blades 31, Moreover, the four blades 31 are each 90 degrees apart. Due to the design of the inner wall trajectory of the five offset blade chamber areas 2303, at any angle when the blade rotor 3 rotates, the blade surfaces of at least three blades 31 will protrude. In addition to the impeller 30, it can withstand fluid drive. There is no problem in the first embodiment because the single blade 31 is retracted in the blade rotor 3, causing no blade 31 to bear the fluid drive; (2) Because of the second embodiment The four blades 31 are 90 degrees apart from each other, which is equivalent to two groups of two blades 31 in each group, and the two blades in each group are 180 degrees complementary in phase, and are matched with the inner walls of the five offset chamber areas 2303. The trajectory is designed so that the total area of the movable wall 221 located on the discharge side of the blade 31 in each offset chamber area 2303 is equal to the total area of the movable wall 221 located on the suction side of the blade 31, so that the blade rotor 3 can operate smoothly without any The situation of sudden fast and slow rotation; (3) The movable blade chamber cover 23 of the second embodiment can only perform axial displacement relative to the blade rotor 3, but cannot move like the movable blade chamber cover 23 of the first embodiment. It will rotate following the blade rotor 3; (4) As shown in Figure 13 As shown in Figure 7-2, the main and passive pumps 101 and 102 are composed of variable suction and displacement pumps with four blades 31 and five offset blade chamber areas 2303. The driving force generated by them is as shown in Figure 7-2. It combines multiple sets of main and passive pumps with single blades combined in a single blade chamber area to form a stable driving effect, which obviously has extremely high industrial utilization value.

According to the above-mentioned design of the variable suction and displacement pump of the present invention, it is indeed possible to effectively achieve the adjustable function of suction and displacement without increasing the original radial size. It can not only effectively improve the aforementioned traditional variable suction and displacement pump. In addition, the combination of the pumps of the present invention can be used to form a driving device that can automatically adjust the rotation speed ratio, which is indeed a design with profound practical value.

2:Chamber body

204: Fixed wall

21: Fixed wall parts

211: Fixed wall seat cover

212: Fixed wall end face

22: Movable wall pieces

221: Movable wall

23: Removable leaf chamber cover

230:Ye Shi

2301: Offset lobe area

2302: Leaf chamber sleeve end face

3: Blade rotor

30: Impeller

301: Axial vertical end face

31: blade

311:Blade top edge

33:Rotor shaft end

34:Rotor shaft end

341: First suction and discharge port

342: Second suction and discharge port

343, 344: Suction and discharge channel

35: Fluid suction and discharge port parts

351: First suction and discharge port

352: Second suction and discharge port

36: Transmission components

37:Sealing block

4. 40: Frame

41:Pedestal

411: Fixed wall end column

4110: Column end face

412:Rotor shaft hole

5: Fixtures

Claims (14)

A variable suction displacement pump has a blade chamber body and a blade rotor. The blade chamber body has a blade chamber, and the blade chamber is composed of fixed wall parts, movable wall parts and movable blade chamber sleeves in the blade chamber body. The volume space surrounding the impeller chamber constitutes the impeller chamber. The impeller chamber and the blade rotor located in the impeller chamber are divided into at least one offset impeller chamber area. The impeller is provided with at least one blade, and the number of the offset impeller chamber areas is Greater than or equal to the number of blades; one side of the blade in each offset chamber area is the suction side, and the other side is the discharge side. Both the suction side and the discharge side have connected suction and discharge channels that are connected to the outside of the pump. Pass; the position of the fixed wall part in the blade chamber body is fixed, and the movable wall part and the movable blade chamber sleeve can be relatively displaced with the fixed wall part along the axial direction of the blade rotor, so that the blade chamber The capacity space of the pump increases or decreases, forming a pump with a variable suction and displacement space. According to the variable suction and displacement pump described in item 1 of the patent application, the fixed wall member is provided with a fixed wall end surface, the fixed wall end surface is provided at one end of the fixed wall member, and the fixed wall member is mounted on a On a base of the frame body, a rotor shaft end of the blade rotor passes through the fixed wall piece, and at least one of the rotor shaft ends is pivoted on the frame body, and at least one of the other rotor shaft ends is output outward. power or receive power; the end surface of the fixed wall can be closely attached to one end surface of the impeller of the blade rotor; the movable impeller chamber sleeve can be mounted on the fixed wall member and framed around the periphery of the blade rotor; The movable wall member is provided with the same number of blade receiving slots as the blades, and is provided with a set of holes in the center. The movable wall member is mounted on the impeller of the blade rotor through the set of holes, and the blades on the impeller can be mounted on the impeller. The movable wall piece slides in the blade receiving groove; the movable wall piece keeps close contact with the movable blade chamber sleeve, and can move synchronously along the axial direction of the blade rotor to change the capacity of the blade chamber. According to the variable suction and displacement pump described in item 1 of the patent application, the impeller of the vane rotor is provided with at least two entrances and exits of the suction and discharge channels. One of the entrances and exits of the suction and discharge channels is connected to the suction side, and the other is connected to the suction side. The discharge side is connected, and the entrance and exit of the suction and discharge channel are connected with the outside of the leaf chamber. According to the variable suction displacement pump described in item 1 of the patent application, a sealing block is provided at the position where the blade, the movable wall member and the movable blade chamber sleeve intersect at the same time. A variable suction and displacement driving device composed of the variable suction and displacement pump described in item 1 of the patent application, which is combined with at least one variable suction and displacement pump to form a variable suction and displacement driving device , at any time during the operation of the variable suction and displacement driving device, the sum of the suction side volumes in all offset impeller chamber areas is equal to the sum of the discharge side volumes in all offset impeller chamber areas. A variable suction and displacement driving device composed of the variable suction and displacement pump described in item 1 of the patent application, which is combined with at least one variable suction and displacement pump to form a variable suction and displacement driving device. , and each of the variable suction and displacement driving devices has four times the number of blades; each blade in the variable suction and displacement driving device has another blade that is 180 degrees symmetrical to the blade, and is symmetrical during operation At any time during the process, when the blades extend out of the impeller of the blade rotor, another 180-degree symmetrical blade retracts into the impeller of the blade rotor. When the blade retracts into the impeller of the blade rotor, the other blade retracts into the impeller of the blade rotor. The 180-degree symmetrical blades extend out of the impeller of the blade rotor, forming a complementary relationship. A variable speed drive device composed of the variable suction and displacement pump described in item 1 of the patent application, which is connected and combined with at least one of the variable suction and displacement pumps to form an active pump, and at least one of the variable suction and displacement pumps is The displacement pump is connected to form a passive pump, and then the active pump and the passive pump are connected to form a variable speed drive device with a main and passive closed circuit. A variable speed drive device composed of the variable suction and displacement pump described in item 2 of the patent application, which is connected and combined with at least one of the variable suction and displacement pumps to form an active pump, and to At least one of the variable suction and displacement pumps is connected to form a passive pump, and then the active pump and the passive pump are connected to form a variable speed drive device of a primary and passive closed circuit. According to the variable speed drive device described in item 7 of the patent application, at least one of the direction in which the impeller space of the active pump increases and the direction of the passive pump in which the impeller space decreases is provided with a displacement damping element. A driving method for a variable suction and displacement driving device composed of a variable suction and displacement pump as described in Item 5 or 6 of the patent application, in which at least one of the variable suction and displacement pumps is connected in a closed circuit. A variable suction and displacement drive device is formed, and fluid is input into the blade chamber of the variable suction and displacement drive device. The input fluid pushes one side of the blades in the blade chamber and drives the blade rotor to rotate. At the same time, the blades move the blades into the blade chamber. The fluid on the other side of the blade pushes out of the blade chamber to form a drive circuit; the movable wall member and the movable blade chamber sleeve in the variable suction and displacement drive device are synchronized with the fixed wall along the axial direction of the blade rotor. When the parts are relatively displaced to change the capacity space of the impeller chamber of the variable suction and displacement drive device, the amount of fluid squeezed out and sucked in by the blade rotor in the impeller chamber changes with each rotation, and in unit time When the same fluid volume is input and output to the variable suction and discharge drive device, the blade chamber capacity of the variable suction and discharge drive device becomes larger, the rotation speed of the blade rotor becomes slower, and the blade chamber capacity becomes smaller. The rotation speed of the blade rotor becomes faster when the variable suction displacement drive device is used, that is, the rotation speed of the blade rotor of the variable suction displacement drive device is inversely proportional to the changed blade chamber capacity. A driving method using the variable speed drive device described in Item 7 or 8 of the patent application, in which one of the variable suction and displacement pumps is set as an active pump, and the other variable suction and displacement pump is set as a passive pump. The active pump The pump and the passive pump are combined into a closed drive circuit; the change in the impeller chamber capacity of the active pump increases, and the amount of fluid in the closed circuit is fixed, so that the impeller chamber capacity of the passive pump becomes smaller accordingly. At the same time, When a fixed amount of fluid flows, the rotation speed of the vane rotor of the active pump becomes slower, and the rotation speed of the vane rotor of the passive pump becomes faster, and the rotation speed of the vane rotors between the active and passive pumps is inversely proportional; conversely, when the active pump The impeller chamber capacity of the passive pump becomes smaller, and the impeller chamber capacity of the passive pump becomes larger accordingly. At the same When a fixed amount of fluid flows over time, the rotational speed of the vane rotor of the active pump becomes faster, and the rotational speed of the vane rotor of the passive pump becomes slower, and the rotational speeds of the vane rotors between the active and passive pumps are also inversely proportional. According to the driving method described in item 11 of the patent application, an external force is used to forcefully push at least one of the movable wall member and the movable impeller chamber of the active and passive pumps at the same time, so that the active and passive pumps The movable wall parts and the movable impeller chamber sleeves are synchronously displaced along the axial direction of the blade rotor, and the synchronous displacement distances of the movable wall parts and the movable impeller chamber sleeves of the active and passive pumps are equal. According to the driving method described in item 11 of the patent application, the amount of fluid in the closed circuit is fixed, so that the chamber capacities of the active and passive pumps change synchronously and the increase or decrease in capacity is in a complementary relationship; that is, Because, when the movable wall member and the movable impeller chamber sleeve of the active pump move relative to the fixed wall member synchronously along the axial direction of the blade rotor, causing the impeller chamber capacity to become smaller, the movable wall member of the passive pump The components and the movable impeller chamber sleeve also synchronously move away from the fixed wall component along the axial direction of the blade rotor, causing the impeller chamber capacity to increase, and the movable wall components and movable impeller chambers of the active and passive pumps The displacement distance of the sleeves is the same; on the contrary, when the movable wall member and the movable impeller chamber sleeve of the active pump synchronously move away from the fixed wall member along the axial direction of the blade rotor, causing the impeller chamber capacity to increase, the The movable wall part and the movable impeller chamber sleeve of the passive pump also move relative to the fixed wall part along the axial direction of the blade rotor simultaneously, causing the impeller chamber capacity to become smaller, and the movable walls of the active and passive pumps The displacement distances of the wall parts and the movable chamber sleeve are the same. A driving method for the variable speed drive device described in Item 7 or 8 of the special application patent application, the steps of which are: (1) operating the variable speed drive device, and allowing the driving force of the active pump to match the driving force of the passive pump There is a difference in the load resistance; (2) Under the effect of the difference between the driving force and the load resistance, the movable wall parts and the movable impeller chamber sleeve of the active and passive pumps are subject to the extrusion thrust generated inside the impeller chamber. and the traction of vacuum suction, causing the movable wall parts and movable impeller chamber sleeves of the active and passive pumps to synchronously shift, and together with this, the active and passive pumps The capacity of the impeller chamber is driven by the difference in force, and automatically produces regulatory changes; (3) In a closed circuit, the capacity of the impeller chamber of the active and passive pumps is finally automatically adjusted to The driving force of the active pump is equal to the load resistance of the passive pump. At this time, the chamber capacity and rotation speed between the active and passive pumps are also automatically adjusted to achieve an inverse relationship.