JP2000170683A - Peripheral pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To continuously lower both discharge pressure and discharge capacity of a pump down to zero when revolving speed of a driving shaft is excessive and obtain both discharge pressure and discharge capacity as nearly high as those of a fixed discharge capacity type pump for high discharge capacity operation. SOLUTION: In housings 2, 3, a large number of semicircular grooves 12a, 12b are formed in the radial direction on the side surface of a disc-like impeller 11 installed in a driving shaft 6, while working chambers 18, 19 as nearly an annular groove having a semicircular sectional form and facing the grooves 12, 13 are formed on the inner wall surface of the housings 2, 3. A discontinuous part of the working chambers 18, 19 remains in between a neighboring intake port 16 and a discharge port, and both ends of it are connected to the intake port and discharge port, respectively. The discontinuous part of the working chambers 18, 19 comprises piston-like movable partitioning parts 22, 23 for controlling the quantity of liquid leaking from the discharge port side into the intake port 16 side by opening/closing a gap between the side surface of the impeller 11 and the inner wall surface of the housings 2, 3.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pump (including a compressor) of the type called a vortex pump (or a regenerative pump) for pressurizing a liquid or gaseous fluid. The present invention relates to a vortex pump having a variable discharge capacity (discharge capacity) characteristic.

[0002]

2. Description of the Related Art As described in Japanese Patent Application Laid-Open No. 8-177777, a large number of blades are formed on a peripheral surface (side surface) of a disk-shaped impeller rotatably supported in a housing. At the same time, on the wall surface of the housing close to the surface of the impeller, a groove-shaped side flow path is formed in an annular shape having a discontinuous portion over a range of about 220 ° along the periphery where the blades on the surface of the impeller are formed. The start end of the side flow path is connected to a fluid inlet formed in the housing, and the end is connected to the fluid outlet, respectively. The above-mentioned discontinuous portion of the side flow path between the discharge port and the outlet serves as a partition (stripper block),
In the vortex pump, which is configured to prevent the pressurized fluid from leaking from the discharge port side to the suction port side, the entire bottom surface of the side flow path can move in the axial direction of the drive shaft of the impeller. Is formed by movable side walls,
An eddy flow pump has been proposed in which the displacement is varied by moving the movable side wall in the axial direction to change the depth of the side flow path (first prior art).

Japanese Patent Application Laid-Open No. 54-57207 discloses an intake port which is relatively close to each other and faces the outer peripheral edge of a disk-shaped impeller having a large number of blades formed in the peripheral portion. And the discharge port are formed in the housing in the radial direction, and the partition partitioning between the suction port and the discharge port is movable, and the movable partition is moved forward and backward in the radial direction with respect to the outer peripheral surface of the impeller. When the movable partition is moved closer to the outer peripheral surface, a high discharge capacity is obtained, while when the movable partition is separated from the outer peripheral surface of the impeller, the pressurized fluid bypasses from the discharge port side to the suction port side. Describes a wesco pump in which the discharge capacity is made variable by reducing the discharge capacity (second example).
Prior art). In this Wesco pump, a common water passage is formed from both the suction port to the discharge port along the both sides of the periphery of the impeller and a part along the outer peripheral surface, and both sides are formed by rotation of the impeller. It is considered that the water discharged from the blades generates two symmetrical vortices back-to-back in the common water passage and flows from the suction port to the discharge port, so this Wesco pump also belongs to the vortex pump. Can be.

[0004]

In the first prior art, the movable side wall forming the bottom surface of the side passage is moved in the axial direction of the drive shaft of the impeller to thereby reduce the cross-sectional area and volume of the side passage. It is considered that the discharge capacity can be changed by changing the flow rate of the vortex flowing spirally in the side flow path, but the discharge capacity can be changed in the first prior art vortex flow pump. The scope is limited,
No matter how the movable side wall moves forward or backward, the discharge capacity cannot be made zero.

In general, the discharge amount (flow rate) of a vortex pump is proportional to the number of revolutions, and the discharge pressure is proportional to the square of the number of revolutions. Therefore, the amount of power consumed to drive the vortex pump is a drive shaft. Is proportional to the cube of the number of revolutions of the vortex pump, as is commonly used as a power source for rotating the impeller when the vortex pump is used, for example, as a fuel pump or a boost pump of an internal combustion engine or a gas turbine engine. When the internal combustion engine or the gas turbine engine itself is used, a high-speed operation state in which the number of revolutions of the power source exceeds the number of revolutions necessary for driving the vortex pump is often caused. As described above, there is a possibility that a vortex pump having a limited discharge capacity variable range cannot always cope with the problem. Therefore, it becomes necessary to use drive control means such as an electromagnetic clutch for intermittently connecting the drive shaft, which results in an increase in size and cost of the pump system.

In a second conventional Wesco pump, a water passage formed in the housing along the periphery of the impeller includes a portion along both side surfaces of the impeller and a portion along the outer peripheral surface. Since both sides are a common passage communicating with each other, water discharged radially by centrifugal force from blades formed on the periphery of both sides of the impeller is symmetrically back-to-back in the common water passage Two
It is considered that two swirls are generated and flow from the inlet to the outlet. However, it is difficult to imagine that two spiral vortices are formed symmetrically and orderly in the common water channel, and due to mutual interference and mixing of these two vortices,
As a result of these two spiral vortices being disturbed and not flowing smoothly, pump loss may increase.

Further, while the water passage has portions along both side surfaces of the impeller, the movable partition wall which advances and retreats radially with respect to the outer peripheral surface of the impeller has a simple plate-like shape. Even in a high discharge capacity state in which the movable partition takes the radial position closest to the outer peripheral surface of the impeller, the discharge port and the suction port communicate with each other by part of the water passages on both side surfaces of the impeller. However, it is impossible to prevent the pressurized water from flowing from the discharge port side to the suction port side along the water passage. Therefore, depending on the Wesco pump of the second prior art, even if the discharge capacity can be made zero, it is equivalent to a fixed high discharge capacity type vortex pump in a state of high discharge capacity operation. High discharge pressure, discharge capacity, and pump efficiency cannot be obtained.

The present invention addresses the above-mentioned problems in the prior art, and in an operation state in which the rotation speed of the drive shaft increases more than necessary, the discharge capacity, that is, the discharge capacity is steplessly reduced to zero. In the state of high discharge capacity operation, it is possible to substantially completely prevent the pressurized fluid from leaking from the discharge port side to the suction port side, and to fix the fixed high discharge capacity type. High discharge pressure, discharge capacity close to
It is an object of the present invention to provide an improved variable displacement type vortex pump in which the pump efficiency is improved.

[0009]

According to the present invention, there is provided a vortex pump according to the present invention as a means for solving the above-mentioned problems.

In the vortex pump according to the first aspect, unlike the conventional vortex pump, a gap formed between the side surface of the impeller and the inner wall surface of the housing at a discontinuous portion of the working chamber is opened and closed. For this purpose, there is provided a movable partition that can control communication and blocking between the fluid suction port and the fluid discharge port. Therefore, since the movable partition can substantially completely close the gap formed on the side surface of the impeller, in the state of high discharge capacity operation, high discharge pressure and discharge equivalent to those of the fixed discharge capacity type vortex pump are achieved. While the capacity and pump efficiency can be obtained, in the state of low discharge capacity operation, the movable partition can greatly open the gap formed on the side surface of the impeller, so that the discharge pressure and the discharge capacity can be substantially reduced. It is possible to freely control over a wide range up to zero.

In the vortex pump according to the second aspect, the gap formed along the side surface of the impeller can be opened and closed by moving the movable partition in the axial direction of the rotary drive shaft. Be composed. Further, in the vortex flow pump according to the third aspect, the movable partition portion is configured to be able to open and close the gap by moving forward and backward in the radial direction of the impeller toward the outer peripheral surface of the impeller. In this case, in addition to the gap formed along the side surface of the impeller, the movable partition can be configured to be able to simultaneously open and close the gap formed on the outer peripheral surface of the impeller. Further, in the vortex flow pump according to claim 8, the movable partition portion has a plate shape,
The side surface of the impeller is attached to a pin shaft parallel to the side surface, and is configured to be able to open and close a gap formed along the side surface of the impeller by rotating around the pin axis. In this case, the pin shaft can be configured to be rotated by a motor via a gear mechanism.

In the vortex pump according to the fifth aspect, the control fluid pressure is supplied to a back pressure chamber formed to support the movable partition from behind, and the control fluid pressure is changed. The movable partition can be moved to any position. In the vortex pump according to the sixth aspect, since the back pressure chamber formed behind the movable partition portion is filled with a compressible fluid to form a closed space,
The back pressure chamber acts like an air spring to automatically adjust the size of the gap formed along the side of the impeller. Further, in the vortex pump according to the seventh aspect, the piston portion formed integrally with the movable partition is driven by the thermowax which expands or contracts according to the temperature of the housing. The thermowax expands or contracts due to a change in the temperature of the housing due to a change in the discharge pressure, whereby the opening and closing of the movable partition can be automatically controlled. In any case, the movable partition may be provided on both side surfaces of the impeller, or may be provided only on one side surface of the impeller.

The application of the vortex pump of the present invention is not particularly limited. However, in the case where the power source is rotationally driven by a power source whose rotation speed fluctuates drastically, its characteristics are exhibited. Engines or gas turbine engines, wherein the vortex pump of the present invention is a cooling water pump for those engines, a circulation pump for circulating the cooling water for heating a vehicle or the like equipped with those engines, It can be suitably used for a fuel supply pump or a boost pump for an engine of the present invention.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A vortex pump 100 according to a first embodiment of the present invention will be described in detail with reference to FIGS. The same applies to the modified example and the second embodiment and the following embodiments, but in the vortex pump 100, the front housing 1, the center housing 2, and the rear housing 3 are integrally fastened to each other by through bolts or the like. It is configured inside the housing. Inside the housing, a rotary drive shaft 6 is supported by a front bearing 4 attached to the front housing 1 and a rear bearing 5 attached to the rear housing 3, and the drive shaft 6 protruding from the front housing 1 is supported.
A pulley 7 is attached to one end of the motor, and is rotatably driven by a power source such as an internal combustion engine or a gas turbine engine via a belt (not shown). In addition, 8 is a shaft sealing device, 9
Indicates a lid member that closes the opening of the rear housing 3.

The right side surface of the center housing 2 is formed with a shallow cylindrical cylinder opening 10 centered on the axis of the drive shaft 6, and a disk-shaped impeller mounted on the drive shaft 6 is formed in the cylinder opening 10. 11 is rotatably inserted and supported with a slight gap left between the side surface and the outer peripheral surface.
In the peripheral portion on both sides (or one side only) of the impeller 11, a large number of semicircular grooves 12 in a substantially radial direction (see FIG. 3) which are seen as a space having a semicircular cross section in FIG. ing. 1 and the like, the semicircular groove 1
2 are semicircular grooves 12a and 12 on each side of the impeller 11.
b. Semicircular groove 1 on the side of impeller 11
2, the same number of substantially radial blades 13 as the semicircular grooves 12 are provided between the adjacent semicircular grooves 12.
Thus, the annular outer peripheral edge 14 and the disk side surface 15 near the center remain in a land shape.

As is apparent from FIG. 2, a fluid suction port 16 and a fluid discharge port 17 are formed relatively close to each other in the center housing 2, and a working chamber comprising a generally annular groove connected to both ends thereof. 18 and 19 are formed on the side surfaces of the center housing 2 and the rear housing 3. The working chambers 18 and 19 are arc-shaped around the axis of the drive shaft 6 so as to be seen as spaces having a semicircular cross section in FIG. 1 and to face the semicircular grooves 12a and 12b of the impeller 11 described above. And the semi-circular groove 12
The annular discontinuous portion is located between the fluid inlet 16 and the fluid outlet 17. The discontinuous portion includes semicircular grooves 12 a and 12 b of the impeller 11 when viewed from the axis of the drive shaft 6. At substantially the same radial position as above, substantially rectangular parallelepiped holes 20 and 21 that are long in the axial direction of the drive shaft 6 are formed on the mutually facing side surfaces of the center housing 2 and the rear housing 3. Movable partitions 22 and 23 each having a substantially rectangular parallelepiped shape are inserted into these holes 20 and 21 so as to be slidable in an oil-tight manner and axially like hydraulic pistons, respectively. Pressure chambers 24 and 25 are formed.

In order to move the movable partitions 22 and 23 in the axial direction, a hydraulic actuator 26 as shown in FIG. 1 is provided in the first embodiment and the like. The operating device 26 includes an oil tank 27, a hydraulic pump 28, a pressure regulating valve 29, and a solenoid valve 30 as a bypass valve that is automatically opened or closed by a control device (not shown) or manually by a driver. The control hydraulic pressure output line 31 communicates with the above-described back pressure chambers 24 and 25 via an oil passage 32 formed between the center housing 2 and the rear housing 3.

A fluid such as water or air pumped by the vortex pump 100 flows into the pump 100 from the suction port 16 and is pressurized by the impeller 11 rotating together with the drive shaft 6, and then is discharged from the discharge port 17 to the outside. Is discharged to Looking at the process in detail, the fluid flows from the inlet 16 to the semicircular groove 12
(12a and 12b), and is centrifugally applied by being forcedly rotated by the blade 13 to be discharged radially outward.
Has a semicircular cross-section as shown in FIG.
Into the working chamber 18 or 19. Since the working chambers 18 and 19 also have a semi-circular cross-section as shown in FIG. 1, the fluid will repeatedly swirl between the semi-circular groove 12 and the working chamber 18 or 19. Then, the swirling vortex flows in the working chambers 18 and 19 in the rotation direction of the impeller 11 with the rotation of the impeller 11, so that the fluid spirally swirls through the working chambers 18 and 19 through the impeller 1.
1 and is discharged from the discharge port 17 to the outside. As a result, the fluid flowing out of the discharge port 17 becomes the suction port 1
The pressure will be higher than when entering from 6.

When the vortex pump 100 is required to have the maximum discharge capacity at the current rotational speed, the solenoid valve 30 of the operating device 26 is controlled by a control device (not shown) or manual control.
Are closed as shown in FIG. As a result, the hydraulic oil pressurized from the hydraulic pump 28 is supplied to the back pressure chambers 24 and 25 via the output line 31 and the oil passage 32, and presses the movable partitions 22 and 23 toward the impeller 11. Accordingly, the movable partitions 22 and 23 slide inside the holes 20 and 21 in the axial direction of the drive shaft 6 to approach both side surfaces of the impeller 11, and the high-pressure fluid at the discharge port 17 is supplied to the low-pressure suction port 16.
Therefore, leakage of fluid from the discharge port 17 to the suction port 16 is almost completely shut off. As a result, as shown in FIG. 2, a state of the high discharge capacity operation in which substantially the entire amount of the fluid flowing from the suction port 16 is discharged from the discharge port 17 is achieved.

As described above, the discharge amount (flow rate) of the vortex pump is proportional to the rotation speed, and the discharge pressure is proportional to the square of the rotation speed. Since the power increases in proportion to the cube of the number of revolutions of the drive shaft 6, the number of revolutions of a power source such as an internal combustion engine or a gas turbine engine is necessary for generating the discharge capacity required for the vortex pump 100. When the rotation speed is increased beyond a certain number of revolutions, the vortex pump 100 becomes a mere brake that wastes power. Also, the vortex pump 100 is forced to perform unnecessary high-load operation, so that the wear and the like of the sliding parts increase and the service life is shortened. Therefore, after the necessary discharge pressure or discharge capacity is obtained, the vortex pump 100 is set to a partial operation state, that is, a low discharge capacity operation state, and the power consumed by the pump 100 is reduced to the minimum necessary. It is desirable. In some cases, it may be better to set the discharge capacity to zero.

For that purpose, the vortex pump 1 of the first embodiment is used.
In FIG. 4, the solenoid valve 30 is opened as shown in FIG.
In addition, the control oil pressure in the oil passage 32 is bypassed to the oil tank 27, and the oil pressure in the back pressure chambers 24 and 25 is reduced. As a result, the movable partitions 22 and 23 retreat in the axial direction in the holes 20 and 21 to a position where the pressure of the fluid pressurized in the semicircular groove 12 and the control oil pressure of the back pressure chambers 24 and 25 are balanced. Large gaps 33 and 34 are formed between the two side surfaces of the movable member 11 and the movable partitions 22 and 23, and the pressurized fluid at the discharge port 17 side passes through the gaps 33 and 34 as shown in FIG. To prevent the fluid pressure (discharge pressure) of the discharge port 17 from further increasing,
An increase in power for rotationally driving the drive shaft 6 is suppressed.

The degree of suppression of the discharge pressure and the discharge capacity or power consumption is determined according to the level of the control oil pressure of the output line 31 which is determined by the degree of opening of the solenoid valve 30 of the operating device 26. By performing so-called duty control for controlling the opening and closing of the solenoid valve 30 in a finely repeated manner, the output line 3 is controlled.
The control oil pressure is changed to an arbitrary height and the gaps 33 and 3 are changed.
4 can be arbitrarily changed, so that the discharge pressure and the discharge capacity of the vortex pump 100 can be changed steplessly. Then, by holding the solenoid valve 30 in the fully open state, the control oil pressure of the back pressure chambers 24 and 25 is made substantially zero, and the movable partition parts 22 and 23 are retracted to the maximum as shown in FIG. it can. Thereby, the gaps 33 and 34 between the movable partitions 22 and 23 and both side surfaces of the impeller 11 are maximized, and the discharge ports 1
If the entire amount of the pressurized fluid on the side 7 is returned to the suction port 16 side as shown in FIG. 5, the discharge pressure and the discharge capacity become substantially zero.

Therefore, according to the vortex pump 100 as the first embodiment, the discharge pressure and the discharge capacity can be reduced from substantially zero to the fixed discharge capacity type even if the rotary drive shaft 6 is not interrupted by the electromagnetic clutch. Since the same maximum discharge pressure and discharge capacity as those of the vortex pump can be steplessly changed, power is not wasted when the power source rotates at high speed, and the durability of the vortex pump 100 is improved.

As described above, the vortex pump 100 according to the first embodiment can control the discharge pressure and the discharge capacity in a wide range from the maximum value according to the current drive speed to the minimum value substantially equal to zero. However, depending on the application, it may be sufficient to suppress the discharge pressure or the discharge capacity to a certain extent. In such a case, as a deformation of the vortex pump 100, for example, the movable range of the movable partitions 22 and 23 is narrowed, and even if the movable partitions 22 and 23 are retracted to the maximum extent, the gaps 33 and 34 are too small. If it is set so as not to increase, the variable range of the discharge pressure and the discharge capacity can be narrowed to the necessary minimum limit.

FIG. 6 shows a vortex pump 100 ′ which is a modification of the first embodiment for the same purpose. As apparent from comparison with FIG. 1, the vortex pump 100 ′ is shown.
, The hole 20 on the left side of the impeller 11 and the movable partition 2
2, only the back pressure chamber 25 formed by the hole 21 on the right side and the movable partition 23 is provided. Accordingly, the control for changing the discharge pressure and the discharge capacity is performed only on one side of the impeller 11, so that the control until the discharge pressure and the discharge capacity become zero is not performed, and the variable range is provided on both side surfaces of the impeller 11. It becomes narrower than the one provided with a movable partition.

Next, a vortex pump 200 according to a second embodiment of the present invention will be described with reference to FIGS. Components that are substantially the same as the components in the above-described embodiment are given the same reference numerals, and a detailed description thereof will be omitted. In the first embodiment, a pair of movable partitioning portions 22 and 23 correspond to both side surfaces of the impeller 11.
Are provided so as to be independently slidable in the axial direction of the drive shaft 6 in the holes 20 and 21, whereas the feature of the second embodiment is that the movable partitioning portions 35 and 36 are integrated to form a movable partition block 37, and the movable partition block 37 selectively communicates and shuts off between the discharge port 17 and the suction port 16 in a discontinuous portion of the annular working chambers 18 and 19. So that
The point is that the movable partition block 37 is provided so as to be able to advance and retreat in the radial direction with respect to the impeller 11. The movable partition block 37 has a substantially U-shape as a whole, straddles a part of the impeller 11 like a saddle, and the plate-shaped movable partition portions 35 and 36, each of which is a part thereof, The impeller 11 is supported so as to face each part of the peripheral portion on both side surfaces with a small gap.

The movable partition block 37 is moved to the working chambers 18 and 1
The center housing 2 and the rear housing 3 are provided with substantially rectangular parallelepiped holes 40 and 41 in order to move the impeller 11 in the radial direction at the discontinuous portion 9 so that they can move together. Partition block 37
To form a movable space for The remaining space radially outward of the movable partition block 37 inserted into the movable space is a back pressure chamber 42, which is always connected to the control oil pressure output line 31 of the operating device 26 by the oil passage 32. I have.
The movable partition block 37 includes return springs 38 and 3
9 urged radially outward. For this purpose, return springs 38 and 3 are mounted on movable partitioning portions 35 and 36, center housing 2 and rear housing 3.
A recess for accommodating 9 is formed. Other configurations are the same as those of the first embodiment.

Since the vortex pump 200 of the second embodiment is configured as described above, when it is required to have the maximum discharge pressure or discharge capacity with respect to the current rotation speed of the drive shaft 6, the first embodiment will be described. As in the case of the embodiment, the solenoid valve 30 of the actuator 26 is closed as shown in FIG. The hydraulic oil pressurized by the hydraulic pump 28 is thereby output from the output line 31.
Through the oil passage 32 and into the back pressure chamber 42, and the hydraulic pressure pushes the movable partition block 37 inward in the radial direction against the return springs 38 and 39. A movable partition block 37 covers both side surfaces and the outer peripheral surface of the impeller 11 at discontinuous portions of the working chambers 18 and 19, and closes a gap through which fluid can pass on both side surfaces or the outer peripheral surface. As a result, as shown in FIG.
The entire amount of the fluid that flows into the inside and is pressurized by the rotation of the impeller 11 is discharged from the fluid discharge port 17 to obtain a high discharge pressure and a high discharge capacity.

On the other hand, in an operation state in which the rotation speed of the power source connected to the drive shaft 6 is higher than the rotation speed required for driving the vortex pump 200 at that time,
In order to save power and protect the swirl pump 200, the solenoid valve 30 is opened to the required size as in the first embodiment. As a result, the control oil pressure of the output line 31 and the back pressure chamber 42 decreases, so that the movable partition block 37 is biased by the return springs 38 and 39 and pressurized near the discharge port 17 as shown in FIG. It moves (retreats) radially outward due to the pressure of the fluid. Along with this, gaps 43 and 44 are formed on both side surfaces of the impeller 11 in the above-mentioned discontinuous portion, and a gap 45 is also formed on the outer peripheral surface of the impeller 11 depending on the design.
The pressurized fluid near the discharge port 17 passes through the gaps 43 and 44 between the discharge port 17 and the suction port 16, and in some cases also passes through the gap 45, and is sucked from the discharge port 17 as shown in FIG. The vortex pump 200 is bypassed to the port 16.
The discharge pressure and the discharge capacity can be reduced to a required level substantially to zero.

In the vortex pump 200 according to the second embodiment, the provision of the single movable partition block 37 not only simplifies the structure, but also in the state of high discharge capacity operation, the movable partition block 37 The movable partitioning portions 35 and 36 close the gaps 43 and 44 on both side surfaces of the impeller 11 at the same time as the gap 45 on the outer peripheral surface of the impeller 11 is closed. It is possible to obtain a high discharge pressure, a discharge capacity and a pump efficiency equivalent to those of a fixed discharge capacity type vortex pump having no partition. In particular, since the return springs 38 and 39 are provided in the vortex pump 200 of the second embodiment, the movable partition block 37 can be reliably moved. In addition, the vortex pump 100 of the first embodiment
The same effect can be obtained.

Next, a vortex pump 300 according to a third embodiment of the present invention will be described with reference to FIGS. In the above-described first embodiment shown in FIG. 1 and the like,
Movable partitions 22 and 23 such as pistons are inserted into holes 20 and 21 formed in the center housing 2 and the rear housing 3, and are moved in the axial direction of the drive shaft 6 by a control oil pressure supplied from an actuator 26. In the third embodiment, the movable partitions 46 and 47 inserted into the holes 20 and 21 are provided with small pistons 48 and 49 integrally therewith, respectively. 49 is hermetically inserted into small cylinders 50 and 51 provided in the center housing 2 and the rear housing 3. A wax chamber 52 is formed in a part of the cylinder 50 or 51 between the pistons 48 and 49, and the wax chamber 52 is filled with a thermo wax 53.

The movable partition 46 in the holes 20 and 21
And 47 are closed back pressure chambers 54 and 55.
The back pressure chambers 54 and 55 are filled with a compressible fluid such as air to act as an air spring.
Return springs (not shown) may be loaded into the back pressure chambers 54 and 55, respectively, to ensure the operation. Needless to say, the vortex pump 300 of the third embodiment does not include any external control means such as the actuator 26 in each of the above-described embodiments.

When the vortex pump 300 of the third embodiment is operated, the temperature of the pressurized fluid discharged to the discharge port 17 is low because the discharge pressure is low when the drive shaft 6 rotates at a low speed. Since the temperature of the thermo wax 53 in the wax chamber 52 formed in a part of the center housing 2 is low and in a contracted state, the pistons 48 and 49 are not pressed. Therefore, the movable partitions 46 and 47 are pressed toward the impeller 11 by the pressure of the air in the back pressure chambers 54 and 55, and a minimum gap is formed between the movable partitions 46 and 47, as shown in FIG. The pressurized fluid does not leak from the discharge port 17 to the suction port 16 through the gap, and the entire amount of the pressurized fluid is discharged to the discharge port 17 as shown in FIG. The state of the high discharge capacity operation in which the maximum discharge pressure and the discharge capacity are obtained according to the rotation speed of the drive shaft 6 is obtained.

On the other hand, when the driving speed of the drive shaft 6 is increased and the discharge pressure and the discharge capacity of the swirl type pump 300 of the third embodiment become excessive, the discharge pressure is increased. As a result, the temperature of the fluid to be discharged also increases, and the temperature of the housing such as the center housing 2 increases. Accordingly, the thermo wax 53 in the wax chamber 52 is heated and expands, and presses the pistons 48 and 49 in the axial direction of the drive shaft 6 as shown in FIG. As a result, the movable partition 4
6 and 47 are retracted to the left and right in the axial direction and separated from the impeller 11, so that gaps 33 and 34 are formed in the same manner as in the low discharge capacity operation state in the first embodiment, and as shown in FIG. Since the pressurized fluid flows out of the suction port 16 into the suction port 16, the discharge pressure and the discharge capacity of the vortex pump 300 decrease, and depending on the size of the gaps 33 and 34, they become substantially zero.

In the vortex pump 300 according to the third embodiment, the discharge displacement control operates completely automatically without performing external control. Further, since there is no need to provide external control means such as the actuator 26 in each of the above-described embodiments, the number of parts is reduced as a whole, and the size and weight are reduced as compared with the vortex pump 100 or the like of the first embodiment. It becomes possible. In addition, costs are reduced as a result. Other effects are almost the same as those of the first embodiment. Needless to say, the movable partition 46 or 47 may be provided only on one side of the impeller 11.

Next, a vortex pump 400 according to a fourth embodiment of the present invention will be described with reference to FIGS. As shown in FIG. 16, in the vortex pump 400, unlike the vortex pump of each of the above-described embodiments,
Movable partitions 56, 5 provided on both sides of impeller 11
7 and 58, 59 are all plate-shaped and supported by pin shafts 60, 61 and 62, 63, respectively, and by rotating about each pin shaft,
At the above-mentioned discontinuous portion, the gaps 64 and 65 formed between the side surfaces 66 and 67 of the impeller 11 and the wall surfaces 68 and 69 of the center housing 2 and the rear housing 3 opposed thereto are opened and closed, respectively. There is a feature in the configuration.

In order to rotate the pin shafts 60, 61 and 62, 63, each of the pin shafts has a pinion 7
0, 71 and 72, 73 are mounted, the pinions of which mesh with a single main gear 74 at the same time. The main gear 74 is rotatably driven by a motor 75, and the motor 75 can be energized by an electronic control device (not shown) or manual means. In the drawing, reference numeral 76 denotes a semi-circular groove in which fluid is formed in the impeller 11 near the pin shafts 60, 61 and 62, 63 when the movable partitions 56, 57 and 58, 59 close the gaps 64 and 65. In order to prevent leakage from the discharge side to the suction side via 12a and 12b, the semi-circular grooves 12 at the discontinuous portions of the working chambers 18 and 19 are mounted on the center housing 2 and the rear housing 3 so as to close them. Fixed partition plates, 77, 78
, 79, and 80 are movable partitions 56, 57, and 5, respectively.
8 and 9 show stoppers for preventing the rotation of 8, 59 beyond the fully closed positions of the gaps 64 and 65.

Since the vortex pump 400 according to the fourth embodiment is configured as described above, in the state of the high displacement operation shown in FIG. 15, the main gear 74 is clocked by the motor 75 as shown in FIG. Rotated in the direction of rotation, and the pinions 70, 71 and 72, 7 associated therewith
1 through the movable partitions 56, 57 and 58, 59 in FIG.
When the movable partitioning portions 56, 57, 58, and 59 are rotated to the positions where they abut against the stoppers 77, 78, 79, and 80 as shown in FIG. From leaking into the suction side
The vortex pump 400 is in a state of high discharge capacity operation, and as shown in FIG.
The entire amount of fluid flowing into the discharge port 17 is discharged to the discharge port 17.

On the other hand, in the low discharge capacity operation state shown in FIG. 18, the main gear 74 is rotated in the counterclockwise direction by the motor 75 as shown in FIG. Rotate 58, 59 to the open position. Thereby, the discharge side and the suction side communicate with each other, and the pressurized fluid flows from the discharge side to the gap 64 as shown in FIG.
And 65, and returns to the suction side, so that the power for rotating the drive shaft 6 is reduced. In this case, the movable partitions 56, 57 and 58, 59 can be opened at any position, so that the discharge pressure and the discharge capacity at the discharge port 17 change depending on the degree of opening. In addition, the movable partitions 56 and 57
It is also possible to set the discharge pressure and the discharge capacity to be substantially zero when the rotary shaft 58 and the rotary shaft 58 and 59 are rotated until they come into contact with the partition plate 76 to take the maximum opening degree.

The motor 75 is rotated forward or backward to rotate the movable partitions 56, 57 and 58, 59.
Are the stoppers 77, 78 and 79, 80 or the partition plate 76
The fully closed or fully opened state stopped by contact with
When a constant voltage is applied to the motor 5, it can be easily determined by detecting a change (rapid increase) in the current flowing through the motor 75. Therefore, the movable partitions 56, 5
The power supply to the motor 75 may be stopped when the fully closed state or the fully opened state of the switches 7, 58, 59 is detected. In the fully closed state or the intermediate opening degree, the movable partitions 56 and 5
7 and the differential pressure between the discharge side and the suction side acting on the movable partitions 58 and 59, respectively, are pinions 70, 71 and 7
Since torques in opposite directions tend to rotate the main gear 74 and the motor 75 in mutually opposite directions via the gears 2 and 73, the movable partitions 56, 57 and 58, 59 are rotated by canceling them. Therefore, it is not necessary to provide any special means for holding the rotating position of the movable partition. Needless to say, when the movable partitions 56, 57 and 58, 59 are fully opened as shown in FIG. 19, there is no differential pressure before and after the movable partitions 56, 57 and 58, 59, so that no torque is generated to rotate them.

Also in the fourth embodiment, the first embodiment shown in FIG.
Since it is not necessary to provide the actuator 26 provided in the embodiment and the like, the overall configuration of the vortex pump 400 can be simplified, and the size can be further reduced. Other effects are almost the same as those of the first embodiment. In the illustrated vortex pump 400, stoppers 77 and 78 for forcibly stopping the movable partitions 56, 57 and 58, 59 at the fully closed position.
And 79 and 80 are provided. If the rotation angle of the motor 75 is detected by using, for example, a rotary encoder, it is not necessary to provide a stopper, and the position of the intermediate opening can be easily and accurately detected. can do.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a configuration of a first embodiment and a state of a high discharge capacity operation.

FIG. 2 is a cross-sectional view showing the configuration of the first embodiment and a state of a high displacement operation.

FIG. 3 is a front view illustrating the shape of the impeller;

FIG. 4 is a longitudinal sectional view showing a state of a low displacement operation according to the first embodiment.

FIG. 5 is a cross-sectional view showing a state of a low displacement operation according to the first embodiment.

FIG. 6 is a longitudinal sectional view showing a configuration of a modification of the first embodiment.

FIG. 7 is a longitudinal sectional view showing a configuration of a second embodiment and a state of a high discharge capacity operation.

FIG. 8 is a cross-sectional view illustrating a configuration of a second embodiment and a state of a high displacement operation.

FIG. 9 is a longitudinal sectional view showing a state of a low displacement operation according to a second embodiment.

FIG. 10 is a cross-sectional view showing a state of a low displacement operation according to the second embodiment.

FIG. 11 is a longitudinal sectional view illustrating a configuration of a third embodiment and a state of a high displacement operation.

FIG. 12 is a cross-sectional view illustrating a configuration of a third embodiment and a state of a high displacement operation.

FIG. 13 is a longitudinal sectional view showing a state of a low displacement operation according to a third embodiment.

FIG. 14 is a transverse sectional view showing a state of a low displacement operation according to a third embodiment.

FIG. 15 is a vertical sectional front view showing a configuration of a fourth embodiment and a state of a high displacement operation.

FIG. 16 is a plan view showing a partial configuration of a fourth embodiment and a state of a high displacement operation.

FIG. 17 is a cross-sectional side view showing the configuration of the fourth embodiment and a state of a high displacement operation.

FIG. 18 is a longitudinal sectional front view showing a configuration of a fourth embodiment and a state of a low displacement operation.

FIG. 19 is a plan view showing a partial configuration of a fourth embodiment and a state of a low displacement operation.

FIG. 20 is a cross-sectional side view showing the configuration of the fourth embodiment and a state of a low displacement operation.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Front housing 2 ... Center housing 3 ... Rear housing 6 ... Rotation drive shaft 11 ... Impeller 12, 12a, 12b ... Semicircular groove 16 ... Fluid suction port 17 ... Fluid discharge port 18, 19 ... Working chamber 22, 23 ... Movable Partitions 24, 25 ... Back pressure chamber 26 ... Hydraulic actuator 31 ... Control oil pressure output line 33, 34 ... Gap 35, 36 ... Movable partition 37 ... Movable partition block 42 ... Back pressure chamber 43, 44, 45 ... Gap 46, 47 movable partition 48, 49 piston 50, 51 cylinder 53 thermo wax 54, 55 back pressure chamber 56, 57, 58, 59 movable partition 60, 61, 62, 63 pin shaft 64 65, gap 66, 67 side surface of impeller 68, 69 wall surface of housing 70, 71, 72, 73 pinion 74 main gear 75 motor 76 ... Partition plates 77,78,79,80 ... Stopper 100 ... Swirl pump of the first embodiment 200 ... Swirl pump of the second embodiment 300 ... Swirl pump of the third embodiment 400 ... Swirl of the fourth embodiment Type pump

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Sadahisa Onimaru 14 Iwatani, Shimowakaku-cho, Nishio-shi, Aichi Prefecture Inside the Japan Automobile Parts Research Institute Co., Ltd. Inside the Japan Auto Parts Research Institute (72) Inventor Mitsuo Inagaki 14 Iwatani, Shimowakaku-cho, Nishio City, Aichi Prefecture Inside the Japan Auto Parts Research Institute (72) Inventor Toshio Morikawa 1-1-1, Showa-cho, Kariya City, Aichi Prefecture Shares F term in DENSO (reference) 3H020 AA01 BA06 BA13 CA06 CA08 CA10 DA17 EA07 EA12 EA14

Claims (11)

[Claims] 1. A housing, a fluid inlet port and a fluid outlet port provided adjacent to each other on the housing, a rotary drive shaft supported by the housing, and mounted to the rotary drive shaft in the housing. And a rotating disk-shaped impeller, and the impeller is formed with a large number of generally radial grooves on at least one side surface so as to be arranged on the same circumference, and the housing is provided with the impeller. A working chamber as a substantially annular groove is formed at a radial position corresponding to a radial groove of the impeller on an inner wall surface facing the side surface, and the working chamber is provided between the fluid suction port and the fluid discharge port. An unfinished discontinuous portion is left as a ring, and both ends of the working chamber forming the discontinuous portion are connected to the fluid suction port and the fluid discharge port, respectively. A movable part that can open and close a gap formed between a side surface of the impeller and an inner wall surface of the housing in a discontinuous portion of the chamber to control communication and cutoff between the fluid suction port and the fluid discharge port. A vortex type pump characterized by having a partition portion. 2. The gap according to claim 1, wherein the movable partition portion moves back and forth in the axial direction of the rotary drive shaft toward the side surface of the impeller, thereby opening and closing the gap formed along the side surface of the impeller. A vortex pump, wherein the vortex pump is configured so as to be able to do so. 3. The gap according to claim 1, wherein the movable partition portion moves back and forth in a radial direction of the impeller toward an outer peripheral surface of the impeller to open and close the gap formed along a side surface of the impeller. A vortex pump, characterized in that it is configured to be able to perform. 4. The apparatus according to claim 3, wherein the movable partition can simultaneously open and close a gap formed on an outer peripheral surface of the impeller in addition to the gap formed along a side surface of the impeller. A vortex pump. 5. The method according to claim 1, wherein
A vortex pump, wherein a control fluid pressure is supplied to a back pressure chamber formed to support the movable partition. 6. The method according to claim 1, wherein
A back pressure chamber formed to support the movable partition,
A vortex pump wherein a compressible fluid is sealed and configured as a closed space. 7. The method according to claim 1, wherein
The movable partition unit integrally includes a piston portion,
The piston is driven by a thermo wax that expands or contracts according to the temperature of the housing, thereby opening and closing the gap formed along the side surface of the impeller. Swirling pump. 8. The impeller according to claim 1, wherein the movable partition is plate-shaped, and is attached to a pin shaft parallel to the side surface of the impeller, and is rotated around the pin axis. A swirl type pump configured to be able to open and close the gap formed along the side surface of the pump. 9. The vortex pump according to claim 8, wherein the pin shaft is rotated by a motor via a gear mechanism. 10. The vortex pump according to claim 1, wherein the movable partition is provided on both side surfaces of the impeller. 11. The vortex pump according to claim 1, wherein the movable partition is provided only on one side of the impeller.