Patent Application
20080159884
The present invention relates to a motor-mounted internal gear pump and electronic equipment.
Internal gear pumps have long been known as pumps which discharge sucked liquid against pressure, and particularly have been popular as hydraulic source pumps or oil feed pumps.
An internal gear pump includes, as main active components, a spur gear type inner rotor with teeth on its outer surface, and an annular outer rotor with teeth on its inner surface which has almost the same width as the inner rotor. A pump casing, which has flat inner surfaces facing both side faces of these rotors with a small gap, is provided to house the rotors. The number of teeth of the inner rotor is usually one smaller than that of the outer rotor, and the rotors rotate with their teeth meshed with each other, like power transmission gears. As the groove area changes with this rotation, the liquid trapped in the grooves is sucked or discharged so that the function as a pump is performed. When one of the inner and outer rotors is driven, the other rotor, meshed with it, rotates as well. Since the center of rotation is different between the rotors, each rotor must be pivotally supported in a rotatable manner individually. The pump casing has openings to flow channels communicated with the outside, called a suction port and a discharge port. The suction port is designed to communicate with a groove whose volume increases and the discharge port is designed to communicate with a groove whose volume decreases. As for rotor profiles, typically, the outer rotor profile includes an arc and the inner rotor teeth are trochoidal teeth.
Since the internal gear pump rotates with its inner rotor and outer rotor meshed, when one rotor is driven, the other rotor rotates as well. When a motor part is integral with the outer surface of a pump part and the rotator of the motor part is integral with the outer rotor and the motor part drives the outer rotor, this structure can be shorter than a structure in which the pump part and the motor part are arranged in series along the axial direction and is thus suitable for a compact pump.
One example of this type of internal gear pump is the internal gear pump as disclosed in Japanese Patent Application Laid-Open Publication No. H2-277983 (Patent Document 1). According to Patent Document 1, the internal gear pump includes an internal gear which combines an outer gear (outer rotor) having a rotor on its outer surface to face and contact a stator fitted in a motor casing, with a given gap inside the stator in the radial direction, and an inner gear (equivalent to an inner rotor) to mesh with this outer gear, wherein both end faces of the internal gear are liquid-tightly closed by end plates and one of the end plates has a suction port and a discharge port which communicate with the internal gear. The end plates (pump casings) include a front casing and a rear casing; disc thrust bearings are disposed between the casings and both sides of the internal gear pump; and both sides of the outer gear are supported by the thrust bearings; both ends of a support shaft are fixed to the casings and the inner gear is rotatably supported by the support shaft through a radial bearing; and also a liquid feed channel is provided to allow some of the pressurized liquid on the discharge side to flow between the rotor and stator and lubricate the bearings and flow back to the suction side.
Patent Publication 1: Japanese Patent Application Laid-Open Publication No. H2-277983
However, the internal gear pump described in Patent Document 1 has a problem that since the outer gear and rotor are separate members, inevitably the size is considerable and the cost is high.
Furthermore, Patent Document 1 neither discloses the materials of the rotor, outer gear, inner gear and end plates which constitute the internal gear pump nor discloses that it is used in electronic equipment. If this internal gear pump is used in electronic equipment, such as a personal computer or server, it should meet the following requirements: mass productivity, long service life, the ability to maintain high accuracy, less friction in sliding parts, low cost and lightness. Also, it has been found that since in consideration of the storage temperature of the electronic equipment, an antifreeze liquid such as ethylene glycol is used as hydraulic fluid which flows in the pump for use in electronic equipment, compatibility between the internal gear and the antifreeze liquid must be taken into account.
An object of the present invention is to provide a motor-mounted internal gear pump and electronic equipment which assure compactness, inexpensiveness and high reliability taking advantage of the functionality as an internal gear pump suitable for high lift application.
In order to achieve the above object, in a first mode of the invention, a motor-mounted internal gear pump includes a pump part which sucks and discharges hydraulic fluid, and a motor part which drives the pump part; the pump part includes an inner rotor with teeth on its outer surface, an outer rotor with teeth on its inner surface to mesh with the teeth of the inner rotor, and a pump casing which houses the inner rotor and the outer rotor, and the motor part includes a rotator, and a stator which rotates the rotator, wherein a common member of permanent magnet material as resin containing magnetic powder serves as the rotator and the outer rotor.
Preferred concrete examples in the first mode of the present invention are as follows.
(1) Water or a liquid containing water as an ingredient is used as hydraulic fluid which is sucked and discharged by the pump part and the common member for the rotator and the outer rotor is made of ferrite bond magnet containing ferrite magnetic powder.
(2) The common member for the rotator and the outer rotor is formed as a member whose magnetic force is strong on its outer surface side and weak on its inner surface side, and the stator is located around and outside the common member.
(3) In the example mentioned above in (1), an antifreeze liquid containing water and an organic substance is used as the hydraulic fluid.
(4) In the example mentioned above in (1), the common member is made of PPS/ferrite bond magnet as PPS resin containing ferrite magnetic powder.
(5) In the example mentioned above in (1), the pump casing consists of two casings, a first casing and a second casing, which are connected; shoulder sections protruding inward are formed on the first casing and the second casing respectively in a way to face each other; and annular bracket sections axially extending from the inner teeth are formed at both sides of the outer peripheral part of the common member; the annular bracket sections are fitted to the outer surfaces of the respective shoulder sections of the first casing and the second casing; and the stator is located around and outside the common member.
(6) In the example mentioned above in (1), the pump casing is made of PPS carbon fiber resin as PPS resin containing carbon fiber or PPS glass fiber resin as PPS resin containing glass fiber.
(7) In the example mentioned above in (1), the inner rotor is made of PPS carbon fiber resin as PPS resin containing carbon fiber, or POM resin.
(8) In the example mentioned above in (5), the first casing and the second casing are made of PPS carbon fiber resin as PPS resin containing carbon fiber.
(9) In the example mentioned above in (8), an outer peripheral part of either of the first casing and the second casing is extended axially to form a can for sealing between the rotator and the stator, and the stator is fitted outside the can.
In a second mode of the present invention, a motor-mounted internal gear pump includes: a pump part which sucks and discharges hydraulic fluid, and a motor part which drives the pump part; the pump part includes an inner rotor with teeth on its outer surface, an outer rotor with teeth on its inner surface to mesh with the teeth of the inner rotor, and a pump casing which houses the inner rotor and the outer rotor, and the motor part includes a rotator, and a stator which rotates the rotator, wherein the rotator is made of PPS resin/ferrite bond magnet as PPS resin containing ferrite magnetic powder.
A preferred concrete example in the second mode of the present invention is as follows.
(1) The pump casing is made of PPS carbon fiber resin as PPS resin containing carbon fiber and the inner rotor is made of PPS carbon fiber resin as PPS resin containing carbon fiber.
A third mode of the present invention is electronic equipment in which one of the above motor-mounted internal gear pumps is mounted as a liquid circulation source and an antifreeze liquid composed of water and an organic substance is used as hydraulic fluid.
According to the present invention, it is possible to provide a motor-mounted internal gear pump and electronic equipment which assure compactness, inexpensiveness and high reliability taking advantage of the functionality as an internal gear pump suitable for high lift application.
Next, a motor-mounted internal gear pump, a manufacturing method thereof and electronic equipment according to an embodiment of the present invention will be described referring to
First, the general structure of a motor-mounted internal gear pump according to this embodiment will be described referring to
The pump 80 is a motor-mounted internal gear pump which includes a pump part 81 which sucks hydraulic fluid and discharges it, a motor part 82 which drives the pump part 81, and a control part 83 which controls the motor part 82.
The pump part 81 includes an inner rotor 1 made of resin, an outer rotor 2 made of resin, a front casing (first casing) 3 made of resin, a rear casing (second casing) 4 made of resin and an internal shaft 5 made of metal. The front casing 3 and rear casing 4 are members which constitute a pump casing: in other words, the pump casing member consists of two separate pump casing members. The rear casing 4 includes a can 6, a flange 18 and a cover 13. The internal shaft 5, which constitutes a shaft for supporting the inner rotor, is a member separate from the front casing 3 or the rear casing 4 in this embodiment.
The motor part 82 includes a rotator 11 as a permanent magnet, a stator 12, and a can 6. The can 6 is shared by the pump part 81 and the motor part 82.
The inner rotor 1 of the pump part 81 is similar in shape to a spur gear and has trochoidal teeth 1a on its outer surface. Strictly speaking the tooth surface is slightly angled in the axial direction, making an angle called a “draft angle” which facilitates drafting in injection molding. Also, the inner rotor 1 has, in its center, an axial hole 1b with a smooth inner surface which penetrates it axially. Both end faces 1c of the inner rotor 1 are flat and smooth and constitute sliding surfaces between the flat inner faces 25, 26 as the end faces of shoulder sections 22 protruding inward from the front casing 3 and rear casing 4.
The inner rotor 1 is made of a self-lubricating synthetic resin in which swelling or corrosion caused by water or an aqueous solution is negligible. Concretely, it is made of PPS carbon fiber resin as PPS (polyphenylene sulfide) resin containing carbide fiber. Because of this, the inner rotor 1 has sufficient strength and wear resistance and can be an inexpensive inner rotor 1. Instead of PPS carbon fiber resin, POM (polyacetal) resin may be used. Since POM is low in friction resistance and low in sliding resistance, it improves the pump efficiency. Also since it is a soft material, it can alleviate impact load, thereby suppressing vibration noise caused by rotor motion. Although these materials have a water-absorbing property and transmit water, there is no problem since they are used for the inner rotor 1. When it absorbs hot water, it may deform; however, if it is profiled to compensate for such deformation, deformation is mitigated. At low temperatures, the gap between both rotors 1, 2 increases but if an antifreeze liquid composed of water and an organic substance is used for the hydraulic fluid, the viscosity of the antifreeze liquid increases and the pump efficiency improves, thereby preventing performance deterioration.
The outer rotor 2 takes the form of an annular internal gear having almost the same tooth width as the inner rotor 1 and has arched teeth where the number of teeth is one larger than the number of teeth of the inner rotor 1. The teeth 2a of the outer rotor 2 as a spur gear have a sectional profile which is almost constant in the axial direction; however, they may be slightly angled in the axial direction, or have an angle called a “draft angle” to facilitate drafting in injection molding. In this case, the inner rotor 1 should have a similar draft angle and the inner rotor 1 and the outer rotor 2 are angled in opposite directions and the rotors 1, 2 are meshed so that the inner teeth diameter of the outer rotor 2 increases in the direction in which the outer teeth diameter of the inner rotor 1 increases. This can prevent the meshing surfaces of the rotors 1, 2 from contacting each other unevenly in the axial direction. Both end faces 2b of the teeth of the outer rotor 2 are flat and smooth and constitute sliding surfaces between the flat inner faces 25, 26 of the front casing 3 and rear casing 4 and function as thrust bearings.
The outer rotor 2 has almost the same width as the inner rotor 1 except its outer periphery, and the outer rotor 2 is disposed outside the inner rotor 1 in a way that both end faces of the inner rotor 1 almost coincide with those of the outer rotor 2. Annular bracket sections 21, which protrude axially from the teeth portion (which has almost the same tooth width as the inner rotor 1 located inside), are formed on the outer periphery of the outer rotor 2. The inner surfaces of the bracket sections 21 are smooth and constitute sliding surfaces between the outer surfaces 27, 28 of the shoulder sections 22.
The outer rotor 2 and inner rotor 1 are designed to rotate between the front casing 3 and rear casing 4 while meshed with each other. A bearing of the internal shaft 5 with a smooth outer surface is fitted into the central axial hole of the inner rotor 1 with a small gap, and thus the inner rotor 1 is pivotally supported by the internal shaft 5 in a rotatable manner. The internal shaft 5 does not rotate because it is tightly fitted into the front casing 3 and rear casing 4.
A permanent magnet as the rotator 11 of the motor part 82 is integrated with the outside of the outer rotor 2. In this embodiment, resin mixed with magnetic powder is used to form the rotator 11 integral with the outer rotor 2. In other words, the rotator 11 of the motor part 82 and the outer rotor 2 of the pump part 81 constitute a common member 112 made of permanent magnet containing magnetic powder. This means that the rotator 11 and the outer rotor 2 can be compact and manufactured at low cost. The rotator 11 provides alternate polarities in the radial direction and when viewed from outside, it has N and S poles arranged alternately along its circumference.
In this embodiment, the common member 112 is made of ferrite bond magnet containing ferrite magnet powder. Therefore, even if water or a liquid containing water as an ingredient is used as hydraulic fluid, the magnet neither corrodes nor rusts and can be manufactured at low cost. This common member 112 is also made of PPS/ferrite bond magnet as PPS resin containing ferrite magnetic powder. Therefore, the magnetic property as the rotator 11 of the motor part 82 is improved, high precision teeth for the pump part 81 can be formed, and a low-friction, low-wear sliding property is achieved in the portion which functions as a bearing, and also formability is high and stability against corrosion in water is high.
In this embodiment, the common member 112 is formed cylindrically so that the magnetic force of its outer surface is strong and that of its inner surface is weak, and since the stator 12 is located outside the outer surface of the common member 112, magnetization from the outer surface is easy and even if ferrite bond magnet, usually inexpensive and weaker in magnetic force than neodymium magnet, is used, the function as the rotator 11 can be well performed.
Furthermore, in this embodiment, shoulder sections 22, protruding inward, are respectively formed on the front casing 3 and rear casing 4 in a way to face each other; and annular bracket sections 21, protruding axially from the teeth portion of the inner surface, are formed at both sides of the outer periphery of the common member 112 and the annular bracket sections 21 are fitted to the outer surfaces 27, 28 of the respective shoulder sections 22 of the front casing 3 and rear casing 4, so that the portion which functions as the rotator 11 can be increased in size axially, which helps the use of ferrite bond magnet which is inexpensive and weak in magnetic force.
It is possible that a composite structure serves as both the outer rotor 2 and the rotator 11 where the outer surface including the outer rotor 2's bracket sections is of PPS/ferrite bond magnet and the teeth portion is of PPS carbon fiber. In that case, if PPS/ferrite bond magnet, from which it is difficult to make a complicated shape, is used to make a simple cylindrical shape and PPS resin is used to make the teeth portion which requires accuracy, teeth with low loss and low wear are formed without hard ferrite powder in the surface of meshing with the inner rotor 1.
The internal shaft 5 includes: a cylindrical bearing 51 which has an outside diameter slightly smaller than the inside diameter of the axial hole 1b of the inner rotor 1 and is slightly longer than the tooth width of the inner rotor 1 in the axial direction; and a fitting part 53 which extends from both end faces of the bearing 51 in both axial directions and has an outside diameter smaller than the outside diameter of the bearing 51. Concretely, the axial length of the bearing 51, located in the center of the internal shaft 5, is slightly (for example, 0.05-0.1 mm) longer than the tooth width of both rotors. The cylindrical fitting part 53, located at each end of the bearing 51, is concentric with the bearing 51. The bearing 51 and the fitting part 53 are parts of the internal shaft 5 which are all made of the same metal material, and integral with each other. The internal shaft 5, made of a metal material, is superior in strength and dimensional accuracy to the inner rotor 1, outer rotor 2, front casing 3 and rear casing 4 which are made of synthetic resin.
The internal shaft 5 also has the function as a structural member which connects the front casing 3 and the rear casing 4. Its fitting part 53 is inserted and fixed into fitting holes 27a, 28a made in the flat inner surfaces 25, 26 of both casings 3, 4. In this condition, the step faces (both end faces of the bearing 51) 51a as boundaries between the bearing 51 and the fitting part 53 are in close contact with the flat inner surfaces 25, 26 of the casings. This means that the length of the bearing 51 is equal to the distance (interval) between both flat inner surfaces 25, 26, and both rotors 1, 2 are inside the flat inner surfaces 25, 26 as the axial end faces of the front casing 3 and rear casing 4, with a small gap. The fitting holes of the front casing 3 and rear casing 4 are eccentric with respect to the outer surfaces 27, 28 of the shoulder sections 22 in a way to accommodate both rotors 1, 2 which are meshed.
The shoulder sections 22 of the front casing 3 and rear casing 4 protrude inward in a way to face each other. The outer surfaces 27, 28 of the shoulder sections 22 are fitted to the inner surfaces of the bracket sections 21 of the outer rotor 2 with a small gap; and the shoulder sections 22 of the front casing 3 and rear casing 4 pivotally support both sides of the outer rotor 2 in a rotatable manner, functioning as radial bearings. The shoulder sections 22 of the front casing 3 and rear casing 4 are in a positional relation as if they originated from a single cylinder.
The front casing 3, one of the two pump casing members, has a hole called a suction port 8 and a hole called a discharge port 10 in its flat inner surface 25. The suction port 8 and the discharge port 10 are holes whose profile extends inside the tooth-base circle of the inner rotor 1 and outside the tooth-base circle of the outer rotor 2 (since the outer rotor 2 is an internal gear, its tooth-base circle diameter is larger than its tooth-tip circle diameter). The suction port 8 faces a working chamber 23 whose volume increases and the discharge port 10 faces a working chamber 23 whose volume decreases. When the volume of a working chamber 23 is maximized, either port 8, 9 does not face the working chamber 23 or is communicated with it only through a small sectional area.
The suction port 8 and discharge port 10 are respectively communicated from the innermost port grooves through an L-shaped flow channel with a suction hole 7 and a discharge hole 9 which are open to the outside. Midway in the flow channel from the discharge port 10 to the discharge hole 9, there is a branched communication path 9a which communicates with an internal space 24 facing the outer surface of the outer rotor 2. The internal space 24 is a space surrounded by the front casing 3 and the rear casing 4 including the can 6.
The can 6, a thin-walled cylinder, is located with a small gap from the outer surface of the rotator 11 (for example, gap of 1 mm or less), so that the rotator 11 can rotate together with the outer rotor 2.
The rear casing 4, one of the two casing members, has a cylindrical can 6 covering the outside of the outer rotor 2 and axially extending outward from the portion constituting its flat inner surface 26, where the can 6 side is softer than the flat inner surface 26 side in terms of axial rigidity; and at the tip side of the can 6, it is connected with the front casing 3, one of the two casing members. In other words, the can 6 is part of the rear casing 4 and refers to a cylindrical thin portion extending frontward and outward from the portions constituting the flat inner surface and shoulder section.
The front casing 3 and rear casing 4 contact each other on a cylindrical surface called a fitting surface 16, engaging with each other with freedom in axial movement while binding each other in the radial direction. The fitting surface 16 consists of a fitting surface between the inner surface of the tip of the can 6 and the outer surface of the outer annular part 29 formed inside the front casing 3. A dent is formed in the inner surface of the tip of the can 6 adjacent to the fitting surface 16 and an O ring 14 inserted into this dent keeps confidentiality between the front casing 3 and rear casing 4. Such structure allows the front casing 3 and rear casing 4 to be combined in a confidentiality manner while assuring freedom in the axial direction.
The front casing 3 and rear casing 4 are made of PPS carbon fiber resin, PPS resin containing carbon fiber. The front casing 3 and rear casing 4 of PPS carbon fiber resin are less water-absorbent and less deform due to water absorption and less deform thermally and are corrosion-resistant against an antifreeze liquid and heat-resistant. Since PPS carbon fiber resin is an insulating material, it is effective in prevention of ground leakage and also it transmits less water and well slides on bearings so that wear rarely occurs and long life and high reliability are expected and forming can be done with high precision.
Plural welding projections 41 which are annular and oriented rearward are formed near the outer surface of the front casing 3 and annular welding grooves 42 into which the welding projections 41 are inserted are formed in the flange 18 of the rear casing 4. In this embodiment, as shown in
The groove on the rear casing 4 into which the welding tool 44 is inserted is an annular groove into which the stator 12 is inserted after welding and can be smaller and simpler in shape than a groove dedicated to welding.
Any contact that limits axial movement, except two points of contact, contact between the welding projection 41 and the welding groove 42 and contact between the internal shaft 5 step and the flat inner surface 25, 26, should be eliminated before completion of welding. The can 6 is thin-walled and the can and its vicinity are softer than the flat inner surfaces, the shoulder sections and the areas around welding points. This establishes a positional relationship among members in the following order.
First, the fitting part 53 of the internal shaft 5 is inserted in the rear casing 4; the inner rotor 1 and outer rotor 2 are fitted into the internal shaft 5; and the front casing 3 with the O ring 14 fitted thereon is fitted to the rear casing 4. In this condition, the welding tools 43, 44 are applied to both casings 4, 5 from both sides and ultrasonic vibrations are given to them while they are pushed with a prescribed force. Consequently the point of contact between the welding projection 41 and welding groove 42 melts and the front casing 3 and rear casing 4 come closer to each other. In this process, the step faces 51a of the internal shaft 5 come into tight contact with the flat inner surfaces 25, 26. As welding goes on, the can 6 of the rear casing 4 and its vicinity are elastically deformed and welding goes deeper. Vibrations are stopped with a force on the welding tools 43, 44 and the molten welded parts cool down and solidify, settling into shape. Even after the welding tools are removed, the step faces 51a of the internal shaft 5 remain in contact with the flat inner surfaces 25, 26 and that contact force remains a reactive force against elastic deformation of the can 6 and its vicinity.
The internal shaft 5 is made of metal and easier to manufacture with required dimensional accuracy in the axial direction than the resin casing members 3, 4. It is also advantageous in that dimensional accuracy in the tooth width direction is assured in its central part adjacent to the teeth of the rotors 1, 2. It is far easier to maintain accuracy than in the method in which accuracy in the distance between both flat inner surfaces 25, 26 is assured only by dimensional accuracy of the casings 3, 4 through the outer periphery of the can 6, etc. without relying on accuracy of the internal shaft 5. Hence the structure in this embodiment is effective in keeping the gap at tooth end faces, which has a large influence on pump performance and reliability, adequate
The welding projection 41 is annular but not a continuous circle and there are missing parts in the circumference as shown in
Thanks to the function of the fitting surface 16, the two casings are combined with high positioning accuracy in the radial direction, and their axial positional accuracy is maintained by contact between the internal shaft 5 and the flat inner surfaces 25, 26. The internal space 24 is hermetically sealed by the O ring 14 and there are no holes or fitting surfaces communicated with the outside except the suction hole 8 and discharge hole 10 and this simple structure is highly liquid-tight. Hence, it prevents liquid leakage with reliability.
The cover 13 is integrally molded as a backwardly folded extension from the flange 18 on the front side of the can 6 which is continuous with the rear casing 4. The cover 13, which covers the outer surface of the stator 12 of the motor part 82, is useful in preventing electric shock, keeping a good appearance and shutting off the noise.
The stator 12 is press-fitted into the outer surface of the can 6 outside the can 6 and opposite to the rotator 11 where the stator 12 consists of a winding around a comb-shaped iron core. The stator 12 is fitted into a circular groove formed between the can 6 and the cover 13. Since the motor part 82, composed of the rotator 11 and the stator 12, is located around the pump part 81, composed of the inner rotor 1 and the outer rotor 2, namely the motor part 82 and the pump part 81 are not arranged in series along the axial direction, the pump 80 is thin and compact.
The control part 83, which is intended to control the motor part 82, is equipped with an inverter electronic circuit for driving a brushless DC motor. Since the motor part 82 is located around the pump part 81 as mentioned above, the control part 83 can be located on the rear side where the suction hole 7 and the discharge hole 9 of the pump part 81 are not located.
A power device 32 as a main electronic component is mounted on a circuit board 31, constituting an inverter circuit for driving a brushless DC motor. The circuit board 31 is fixed to the rear casing 4 by caulking, or passing a projection 45 on the back of the rear casing 3 through a hole in its center. The power device 32 contacts the rear casing 4 through the circuit board 31. Consequently, heat generated in the inverter circuit can be passed through the rear casing 4 into the hydraulic fluid in the pump part 81. The circuit board 31 is connected with one end of the winding of the stator 12 and also with a power line 33 for external power supply, a rotation output line 34 for transmitting rotation speed information by pulses and a common grounding line for them.
The brushless DC motor includes: the motor part 82 having the rotator 11 as permanent magnet, and the stator 12; and the control part 83 having the inverter electronic circuit. The structure that the rotator 11 is inside the thin-walled can 6 and the stator 12 is outside the can 6 is called a “canned motor”. Since the canned motor does not require a shaft seal, etc. and transmits the turning force to the inside of the so-called can 6 by the use of a magnetic force, it is suitable for the structure of a positive displacement pump which pumps out the hydraulic fluid through change in the volume of the working chambers 23 while isolating the fluid from the outside.
When the pump 80 has dimensional relations as shown in
If the outside diameter of the inner rotor 1 is above this range, the rate of internal leakage (back flow from the higher pressure discharge port communicating side to the suction port communicating side, which deteriorates pump performance) would increase, deteriorating pump performance. If it is below the range, the velocity of flow would increase at opening areas where the working chambers communicate with the suction or discharge port, leading to increased pressure loss and deterioration in pump performance.
The inside diameter of the bracket section 21 of the outer rotor 2 must be geometrically larger than the outside diameter of the inner rotor 1. At the same time, if it is above this range, frictional force and internal leakage from bearing surfaces would increase, leading to deterioration in pump performance.
If the axial length of the outer rotor bracket section 21 is below this range, the bearing surface pressure might increase and thus frictional wear might increase, leading to shorter pump life and lower reliability. If it is above this range, it is disadvantageous because unevenness in contact easily occurs due to errors in bearing surface cylindricality and concentricity, etc.
It is recommended that the inner rotor rotation speed be within the range of 2500-5000 rpm. If the rotation speed is slower than this, the ratio of internal leakage to transportation flow rate would increase, leading to deterioration in pump efficiency. If it is faster than this, vibration noise generated by the pump would increase.
Next, how the pump 80 works will be explained referring to
By giving 12 V DC power to the power line 33 to supply electric current to the motor drive circuit of the control part 83, electric current is fed through the power device 32 to the winding of the stator 12. This starts the motor part 82 and controls it to rotate it at a preset rotation speed. Since the power device 32 outputs rotation information on the rotator 11 as a pulse signal through the rotation output line 34, a higher-level control apparatus which receives the signal can confirm the operating condition of the pump 80.
As the rotator 11 of the motor part 82 rotates, the outer rotor 2, united with it also rotates; as the rotation is transmitted like an ordinary internal gear, the inner rotor 1, meshed with it, also rotates. The volume of working chambers 23 formed in the grooves of the two rotors 1, 2 increases or decreases as both rotors 1, 2 rotate. As shown in
The hydraulic fluid passes through the suction hole 7 and then the suction port 8 and is sucked into the working chambers 23 whose volume is increasing. As the rotors rotate, the working chamber 23 whose volume is maximized leaves the profile of the suction port 8 and finishes its suction process, then communicates with the discharge port 10. Then, the volume of the working chamber 23 begins to decrease and the hydraulic fluid in the working chamber 23 is discharged through the discharge port 10. The discharged hydraulic fluid is sent out through the discharge hole 9. Since the branched communication path 9a lies midway in the discharge flow channel, the inner pressure of the internal space 24 is maintained at a discharge pressure level.
In this embodiment, since the suction flow channel is short, the negative pressure for suction is small, which prevents cavitation. In addition, a relatively high discharge pressure is applied to the inner surface of the can 6 to push and expand it outward and therefore even though the can 6 is thin-walled, it cannot be so deformed inward as to touch the rotator 11. At the same time, leakage from the gap as a radial bearing formed on the bracket section 21 of the outer rotor 2 can be reduced. The reason is that although the outward force of leakage from this gap is increased by a centrifugal force, if the inner pressure of the internal space 24 around it is high, there is an action which pushes it back.
In the power device 32, which must be cooled because it generates heat during operation, the heat passes through the wall of the rear casing 4 which the device contacts through the circuit board 31, and moves to the hydraulic fluid flowing in the internal space 24 before being released outside. Since the hydraulic fluid in the internal space 24 is always stirred and successively replaced due to minor leaks from the radial bearing surface, it carries away the heat efficiently. Since the inside of the pump 80 is cooled efficiently as described above, a heat sink or cooling fan for cooling the power device 32 is not needed. Similarly, the heat generated by motor loss in the rotator 11 or the stator 12 is carried away efficiently, which prevents an abnormal temperature rise.
Next, electronic equipment which has the above pump 80 will be described referring to
The personal computer system 60 includes a personal computer 61A, a display unit 61B, and a keyboard 61C. A liquid-cooling system 69 is housed in the personal computer 61A together with a CPU (central processing unit) 62 and consists of a closed loop system in which a liquid reservoir 63, a pump 80, a heat exchanger 65, a heat radiating plate A66 and a heat radiating plate B67 are connected in the order of mention by tubing. This liquid-cooling system 69 is primarily intended to convey out the heat generated by the CPU 62 housed in the personal computer 61A and keep the temperature rise of the CPU 62 below a prescribed level. The liquid-cooling system 69, which uses, as a heat transfer medium, water or an aqueous liquid such as an antifreeze liquid composed of water and an organic substance (ethylene glycol, etc), features a higher heat transfer capability and lower noise than an air-cooling system, so it is suitable for cooling the CPU 62 which generates much heat.
The liquid being conveyed (hydraulic fluid) and air are filled in the liquid reservoir 63. The liquid reservoir 63 and the pump 80 are placed side by side where the outlet of the liquid reservoir 63 and the suction hole of the pump 80 are connected by tubing. The heat exchanger 65 is bonded to the heat radiating surface of the CPU 62 through thermally conductive grease. The discharge hole of the pump 80 and the inlet of the heat exchanger 65 are communicated by tubing. The heat exchanger 65 is communicated with the heat radiating plate A66 by tubing; and the heat radiating plate A66 is communicated with the heat radiating plate B67 by tubing; and the heat radiating plate B67 is communicated with the liquid reservoir 63 by tubing. The heat radiating plate A66 and the heat radiating plate B67 are so located as to allow heat radiation from different surfaces of the personal computer 61A.
The pump 80 is connected with the power line 33 from a 12 V DC power supply usually provided in the personal computer system 60 and the rotation output line 34 is connected with the electronic circuit of the personal computer system 60 as a higher-level control apparatus.
Next, how this liquid-cooling system 69 works will be explained. As the personal computer system 60 is started, power is supplied, the pump 80 begins running and the liquid being conveyed begins circulating. The liquid is sucked from the liquid reservoir 63 into the pump 80 and pressurized by the pump 80 and sent to the heat exchanger 65. The liquid sent from the pump 80 to the heat exchanger 65 absorbs the heat emitted from the CPU 62 and the liquid temperature rises. Then, the heat of the liquid is exchanged for outside air through the heat radiating plate A66 and the heat radiating plate B67 (heat is released to the outside) and consequently the liquid temperature falls, then the liquid returns to the liquid reservoir 63. This process is repeated so that the CPU 62 is continuously cooled.
Since the pump 80 is an internal gear pump as a kind of positive displacement pump, even if it is started in a dry (no liquid) condition, it has the ability to make the suction hole have a negative pressure. Therefore, even when the liquid comes through a tube above the liquid level inside the liquid reservoir 63 or when the pump 80 is located at a higher position than the liquid level, the pump 80 has a self-priming ability to suck liquid without priming water. The internal gear pump 80 has a higher pressurizing ability than a centrifugal pump, etc, so it can also be used in such a condition that the liquid passes through the heat exchanger 65 and the heat radiating plates 66, 67 and thus liquid pressure loss increases. Particularly when the heat density of the CPU 62 is high, in order to increase the heat exchange area, the flow channel inside the heat exchanger 65 must be elongated by folding it; thus a liquid cooling system which uses a centrifugal pump, etc. would be difficult to use because of increased pressure loss in the liquid passing through the channel, while the liquid cooling system 69 according to this embodiment can cope with such a situation.
In the liquid cooling system 69 according to this embodiment, the liquid being conveyed passes through the heat radiating plates 66, 67 just after the outlet of the heat exchanger 65 where the liquid temperature is highest, and the liquid temperature falls, so the temperature of the liquid reservoir 63 and pump 80 is maintained at a relatively low level. For this reason, the internal parts in the pump 80 provide higher reliability than in a high temperature environment.
As a result of operation of the liquid cooling system 69, the temperature of each of the components through which the liquid circulates is determined and the temperature is monitored by a thermo sensor (not shown). If insufficiency of the cooling performance is confirmed by detection of a temperature above a prescribed level, a command is given to increase the rotation speed of the pump 80 to prevent an excessive temperature rise. Contrarily, if the cooling performance is too high, the rotation speed is decreased. The rotation output signal from the pump 80 is always monitored; if no rotation signal is sent and there is an abnormal change in the liquid temperature, the pump 80 is considered to be out of order and the personal computer system 60 enters an emergency mode. In the emergency mode, a fatal hardware damage is prevented by taking minimum necessary steps such as decreasing the CPU speed and saving current program data.
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| Number | Date | Country | Kind |
|---|---|---|---|
| 2005-190933 | Jun 2005 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2006/312975 | 6/29/2006 | WO | 00 | 8/2/2007 |
