CN102135103B - Refrigerated medium pump unit - Google Patents
Refrigerated medium pump unit Download PDFInfo
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- CN102135103B CN102135103B CN201110031160.9A CN201110031160A CN102135103B CN 102135103 B CN102135103 B CN 102135103B CN 201110031160 A CN201110031160 A CN 201110031160A CN 102135103 B CN102135103 B CN 102135103B
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- Prior art keywords
- bearing
- centrifugal pump
- tubular container
- contact
- interface
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D1/06—Multi-stage pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D13/0606—Canned motor pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
- F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/086—Sealings especially adapted for liquid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention relates to the refrigerated medium pump unit that one has drive motor (2) and centrifugal pump (4), this centrifugal pump (4) by tubular container (18) around, this tubular container (18) is tightly connected with the electric machine casing of the first axial end portion and described drive motor (2), and the opposite axial end portion (20) of this tubular container (18) is configured to close.
Description
Technical field
The present invention relates to a kind of refrigerated medium pump unit.
Background technique
Refrigerated medium pump unit is used in chiller plant or air-conditioning, carry freezing mixture or refrigeration agent to circulate to make it.Centrifugal pump can be used for this reason.
Refrigeration agent is under higher pressure in such devices usually, thus higher to the seal request of separate part and link position.In addition, refrigeration agent is very expensive, poisonous and/or be harmful to surrounding medium often, therefore should definitely avoid leaking.
Summary of the invention
Consider these problems, the object of the invention is to propose a kind of refrigerated medium pump unit, it can prevent from revealing effectively.
Refrigerated medium pump unit according to the present invention has drive motor, particularly electric drive motor and the centrifugal pump that driven by this drive motor.Single-stage or multistage is configured at this this centrifugal pump.Drive motor and centrifugal pump are connected to each other to a pump assembly
According to the present invention, centrifugal pump by tubular container institute around.This tubular container, is preferably radially spaced with first shell body wall of each pump stage (Pumpenstufen) of centrifugal pump around centrifugal pump as additional wall.Tubular container is connected with the housing seal of drive motor by the first open axial end portion.Tubular container is configured to close at its relative axial end portion, thus makes it have the shape of can-like generally.Whole system to outer closure, and is born the power produced by the system pressure of fluid therein by tubular container.In order to seal, only needing a Sealing to the interface area of electric machine casing.Thus, by reducing the risk needing the interface of sealing to reduce leakage.In addition, the housing parts of each pump stage of centrifugal pump need not be configured to measuring body, and bearing system pressure, these housing parts need only withstand the pressure difference produced by the can-like pump stage of centrifugal pump or centrifugal pump.Therefore, can abandon in this region using expensive foundry goods.Due to the preferred refrigeration agent to be conveyed to the whole vessel filling around centrifugal pump, therefore, therefore, system pressure be the inside of the pump stage housing of centrifugal pump group or outside all dominant.In addition, the Sealing for centrifugal pump inside also need not propose higher requirement, because the seal will outwards not seal for surrounding environment by centrifugal pump hermetically.This function by around container bear.
Preferred tubular container has inhalation interface and pressure interface.Except that be connected with electric machine casing, open axial forward end portion, these two openings are preferably independent opening other in container, thus make container externally only relatively easily need seal three interfaces in this case.But it is also conceivable to, according to the equipment installing this container wherein, also can more than one inhalation interface and/or pressure interface be set on container.At internal tank, inhalation interface connects the suction side of centrifugal pump, and pressure interface connects the compression-side of centrifugal pump.
Preferred inhalation interface and/or pressure interface radially stretch out from container, and therefore they constitute the connecting head (Anschlussstutzen) for being connected with the pipeline be connected.
In addition, container preferably has closed wall.This wall be preferably one piece or one form, sometimes also formed by multiple components welding.Therefore, except the forward end of the opening for connecting motor and inhalation interface and pressure interface, the closed container so formed preferably no longer has other opening or needs the interface of sealing, can drop to minimum by the danger of leakage thus.
Inhalation interface and/or pressure interface can be equipped with the adpting flange for being connected with connected pipeline.Inhalation interface and/or pressure interface and connecting pipeline (Anschlussleitungen) directly can also be welded together in addition.If by connected pipeline directly and inhalation interface and/or pressure interface weld together, then its advantage is, need not arrange other Sealing at these jointings, thereby further reduces the danger of leakage.Therefore, when this connecting pipeline is welded direct to inhalation interface and pressure interface, on container, only have an opening needing sealing in the ideal case, namely to the interface of drive motor.Inhalation interface and pressure interface can be configured to connecting head.Alternatively connecting pipeline can also be welded direct on the perisporium of container.
Further preferably, container has annular and separation wall therein, and the suction side of centrifugal pump and compression-side are separated from each other by this partition wall.This annular and separation wall preferably extends radially inwardly from inwall as annular protrusion.At this, the axis along container is seen, the direction namely along the spin axis of centrifugal pump is seen, annular and separation wall is preferably arranged between inhalation interface and pressure interface in a reservoir.In the inner circumferential of annular and separation wall, also preferred annular and separation wall to be configured to, to make it closely stick together with the periphery of housing parts of the centrifugal pump being arranged on internal tank.Here if desired can setting example as the Sealing for O shape ring.At this, partition wall is preferably placed vertically, centrifugal pump is joined in the inner circumferential of divider walls wall with the axial end portion of its suction side, and closely abuts on partition wall with the axial end portion of suction side.On the partition wall side sucking wall side dorsad, preferably with the fluid flowed out from centrifugal pump fill centrifugal pump and around this centrifugal pump container between free space.Then, preferably this space is connected with pressure interface.Therefore, preferably retain the free space between centrifugal pump and the inner circumferential of container, namely the internal diameter of container is greater than the external diameter of centrifugal pump.
Preferred centrifugal pump extends with one heart relative to container, and vertically, namely inserts container along the longitudinal axis of centrifugal pump or the direction of spin axis from open forward end.At this, container is preferably removably connected with the electric machine casing of drive motor, such as, Flange joint by tightening.This makes container and electric machine casing can be separated from one another, like this, just drive motor and centrifugal pump group can be removed from container or therefrom extracts out, such as to safeguard centrifugal pump or drive motor or to change.The repairing of very simple maintenance and necessity can be carried out thus, because the connecting pipeline of all connection centrifugal pump groups all need not unclamp with the remaining part of refrigeration system, but can keep being connected with container securely.
Further preferably, drive motor is configured to seam tubular motor (Spaltrohrmotor).This means that drive motor is the wet motor run.At this, preferably slit-tube (Spaltrohr) is set to, directly utilizes the axial end portion of the opening of container to be sealed, or utilization makes it be connected with seal of vessel for the flange connecting drive motor.Such as, by such flange, slit-tube can be welded on drive motor or electric machine casing.The advantage done like this is, also no longer needs other Sealing to seal the inner space with refrigerant charge and under being in system pressure in drive motor.Therefore, in the ideal case, only between electric machine casing or the drive motor in side and the container at opposite side, a Sealing is needed.Particularly no longer needing to carry out shaft sealing in the mode of execution using seam tubular motor, especially easily there is the danger of leaking in this shaft sealing.
As mentioned above, for the system pressure of refrigeration agent to be conveyed, be preferably measuring body by container structure.Therefore, by container structure be particularly preferably, the system pressure of > 25bar can be withstood, further preferred > 30bar, the particularly preferably internal pressure of > 50 or 60bar.
Pump assembly has at least one impeller and a thrust-bearing in known manner, and thrust-bearing absorbs impeller and to be in operation produced axial reaction force.This thrust-bearing such as can be arranged on the axle of drives impeller.Thrust-bearing is made up of the bearing part rotated and fixing bearing part, and wherein, the axial force that is in operation is delivered to fixing bearing part from the bearing part rotated, and is such as bearing in by fixing bearing part on the housing of pump or drive motor.
According to a kind of preferred implementation of the present invention, be that the bearing part that rotates or fixing bearing part be all configured to can be self-aligning.That is, fixing bearing part and the bearing part of rotation are all configured to, and their bearing surface can be aligned with each other, thus enable them stretch in parallel with each other, and can such as directly against each other together, mutually to slide with the form of sliding bearing.Thus, no matter be the bearing part or fixing bearing part that rotate, not only be configured to can be self-aligning for one of bearing part, and still can reliably support when positional fault or skew appear in axle, because the bearing surface of these two bearing part can be in Angle Position (Winkellage) parallel to each other all the time, on this Angle Position, they reliably slide over each other.Therefore can prevent one of these bearing part from trembleing (Taumeln).
Such thrust-bearing is very suitable for the centre being arranged on axle.So, preferably the axial end portion of thrust-bearing and transmission shaft is arranged on transmission shaft at interval, particularly makes the axial centre of thrust-bearing distance transmission shaft nearer than distance axial end portion.That is, in this embodiment, compared with the axial end portion of usual radial support axle, thrust-bearing is arranged in the region that the skew of slight radial axle and axle position mistake may occur of transmission shaft more.Be arranged on by thrust-bearing in the region that radial axle skew and axle position mistake may occur and usually can bring following problem, namely bearing part starts vibration, and this will cause higher friction and higher wearing and tearing.By making two self-aligning embodiments of bearing part will avoid this problem according to of the present invention, even and if low friction also can be guaranteed when thrust-bearing being arranged on the central region of axle, lowly abrasively to run.
Preferably be arranged on transmission shaft by the rotor of electric drive motor and at least one impeller, at this, thrust-bearing is presented axially between rotor and at least one impeller.At this, transmission shaft can be configured to the transmission shaft of continuous print, one, but also can be such as configured to by transmission shaft manifold with the form of motor shaft and pump shaft, these parts be torsionally connected to each other.Therefore, preferably thrust-bearing is arranged on centrifugal pump towards on the axial end portion of drive motor.
On the compression-side of also preferred (when multistage centrifugal pump) when thrust-bearing being arranged at least one impeller or being provided with multiple impeller.Compression-side is the side that the medium to be conveyed of impeller has higher pressure thereon.This means, what preferably thrust-bearing is arranged on pump has in the region of most high fluid pressure.The advantage done like this is, can guarantee that thrust-bearing has enough lubrications in this region by fluid.This is specially adapted to the situation being tending towards under heating and/or less pressure when carrying fluid or liquid volatilizing.Can guarantee that fluid to be conveyed in this region exists with flow morphology by the region that thrust-bearing is arranged on maximum pressure, and therefore can provide enough lubrications by axial thrust bearing.When fluid to be conveyed is such as the refrigeration agent that will volatilize at very low temperatures, this will have the meaning of particular importance.The highest region of the pressure of centrifugal pump is preferably made to be positioned at the axial end portion towards drive motor of centrifugal pump.That is, the suction side of pump is spaced apart with drive motor vertically.At this, thrust-bearing is preferably placed at before drive motor, thus makes fluid to be conveyed in this region substantially not yet by the waste heat of drive motor.Therefore in the ideal case, thrust-bearing is arranged in high pressure and the low-temperature region of fluid to be conveyed, thus can guarantee the non-volatile and lubricating bearings in liquid form of fluid in this region.
As mentioned above, be preferably sliding bearing by thrust bearing structure, and utilize fluid to be conveyed or liquid to be conveyed to lubricate it.
The bearing surface of at least one bearing part is also preferably made to be aim on the Angle Position of its spin axis relative to transmission shaft (Rotationsachse) and can freely swing at least one limited angular region.Thus ensure that auto-alignment, namely make bearing surface can at its Angle Position upper deflecting about spin axis, and to be registered to such angle: this bearing surface is entirely abutted on the bearing surface of another bearing part corresponding thereto.Can be in operation thus and prevent vibration.
For this reason, the bearing surface of at least one bearing part is also preferably made to be the axis oscillating adjusting its Angle Position and can extend each other in right angle and perpendicular to the spin axis of transmission shaft around two.That is, this main manifestations is the deflection on sphere (Kugelebene), and sphere centre point is positioned on spin axis.Therefore, bearing surface freely can be aimed at along any direction on its Angle Position.
Preferably installed by the bearing surface of at least one bearing part or support on the bearer, this supporting member has the ball type of contact surface of bearing surface dorsad, and this ball type of contact surface abuts in corresponding taper shape docking surface of contact slidably
on.At this, this ball type of contact surface preferably raises into arch, and conical docking surface of contact is then correspondingly configured to concavity.At this, docking surface of contact is preferably configured to concavity arch along its radius, is namely configured to spherical, thus these faces are reclined in face each other.Therefore, surface of contact and docking surface of contact form a part for spherical surface, and foregoing bearing surface can be deflected relative to spin axis on its Angle Position.Will not be configured to spherical forcibly by conical docking surface of contact, on the contrary, also the taper shape with straight cross-section line (geraderQuenchnittslinie) can be configured to, at this, diameter and the slope of cone are chosen as, and ball type of contact surface at least can be abutted on conical docking surface of contact linearly.Bearing surface can directly construct on the bearer, this means that supporting member itself can be made up of desired bearing material.Supporting member can also be set to independent parts in addition, the bearing element that at least one is made up of suitable bearing material is set on the supporting, and on this bearing element, form actual bearing surface.
In addition preferably, make at least one bearing part, be preferably the surface of contact of the bearing part rotated and dock surface of contact to keep reclining by elastic force.The advantage done like this is, even if when pump is in halted state, the Angle Position of the bearing surface that the deflection toward each other that also can be maintained by surface of contact and docking surface of contact occupies, because surface of contact and docking surface of contact utilize certain frictional connection to keep reclining.
In addition, surface of contact and docking surface of contact arrange engaged element (Eingriffselemente), worthily for transmitting torque mutual in engagement.Surface of contact and docking surface of contact should slide, mutually to change the Angle Position of bearing surface.As mentioned above, this mainly comprises the deflection around two orthogonal axiss of oscillation, wherein the jante et perpendiculaire of these axiss of oscillation and transmission shaft.But between surface of contact and docking surface of contact around the swing of spin axis or rotation be less desirable because it is the motion that will occur between the bearing surface of two bearing part in thrust-bearing.These bearing surfaces should slide each other rotatably.Thus, should prevent from rotating between surface of contact and docking surface of contact.Such as, engaged element can be configured to the shape of the mesh groove engaging bump and correspondence, at this, such as, will engage bump and arrange on the contact surface, and mesh groove is arranged in docking surface of contact.At this, engagement bump and mesh groove preferably radially extend, thus engagement bump can move relative to each other in mesh groove when surface of contact swings relative to docking surface of contact.But prevent moving relative to each other along the circumferential direction.Therefore, the torque between surface of contact and docking surface of contact can be guaranteed by the engagement of the form fit of engaged element.
Surface of contact and/or docking surface of contact are preferably made up of stupalith.These materials have enough intensity, particularly have enough wear resistancies.
One also in preferred bearing part has the bearing surface be made up of multiple independent bearing liner (Lagerschuhen), and another bearing part then has continuous print bearing surface, and bearing liner slides on this continuous print bearing surface.Therefore, such as fixing or static bearing part can have multiple independent bearing liner, and the bearing part rotated then has continuous, annular bearing surface, preferably this bearing surface is made single-piece part.But groove or recess can be set on the surface of continuous print bearing surface at this, with guarantee by transport pump, for the fluid supply of lubricating bearings.Independent bearing liner on another bearing part can have certain mobility, thus enables them be aimed at relative to opposite bearing surface equally by its surface, thus these bearing surfaces can be made to recline in face each other.Can retain free space or gap between each bearing liner, these free spaces or gap are used to equally as lubricating bearings provides fluid to be conveyed or liquid to be conveyed.Corresponding recess or groove can also be set in bearing surface on bearing liner, in order to provide lubrication.
As mentioned above, centrifugal pump group is designed for refrigerant conveying.Just be desirably on the pressure side going up of centrifugal pump in such centrifugal pump group, namely thrust-bearing is set in the axial central region of axle, at this, the quality of bearing structure is improved in foregoing mode by the mode of execution of thrust-bearing according to the present invention.
Accompanying drawing explanation
With reference to the accompanying drawings the present invention is done below and exemplarily illustrate.Wherein:
Fig. 1 shows the sectional view of the centrifugal pump group for refrigerant conveying according to the first mode of execution,
Fig. 2 shows the sectional view of the centrifugal pump group for refrigerant conveying according to the second mode of execution,
Fig. 3 shows the overall perspective of centrifugal pump group as shown in Figure 1,
Fig. 4 illustrate in perspective view centrifugal pump group as shown in Figure 3 in the on-state,
Fig. 5 shows the zoomed-in view of the embodiment of thrust-bearing in centrifugal pump as depicted in figs. 1 and 2,
Fig. 6 illustrates the first bearing part rotated of thrust-bearing as shown in Figure 5 with exploded perspective,
Fig. 7 shows the perspective exploded view of the fixing bearing part as shown in Figure 6 axially seen along another,
Fig. 8 shows the perspective exploded view of the fixing bearing part of thrust-bearing as shown in Figure 5,
Fig. 9 shows the perspective exploded view of the fixing bearing part as shown in Figure 8 axially seen along another.
Embodiment
Centrifugal pump group is as depicted in figs. 1 and 2 designed for refrigerant conveying especially, and on axial end portion, have drive motor 2, and in the axle side of drive motor 2, the direction namely along spin axis X is provided with centrifugal pump 4.Centrifugal pump 4 is designed to multistage, and namely it has multiple impeller 8 in succession arranged vertically on transmission shaft 6.As known at traditional centrifugal pump, impeller 8 by have housing parts 10 institute that is positioned at inner guider (Leitapparaten) 12 around.Guider 12 for guiding from an impeller 8 to the stream of next impeller, and makes the liquid stream flowed out from impeller 8 radial direction deflect vertically.
Housing parts 10 vertically X is laid adjacent to each other, thus makes them jointly form tubular shell.First axial end portion 13 of the formation suction side of centrifugal pump 4 arranges filter 14, and centrifugal pump 4 sucks refrigeration agent to be conveyed by filter 14 and makes it enter in centrifugal pump.On opposite axial end portion on the pressure side, be provided with in last housing parts 10 circumference outflow opening (
) 16, the refrigeration agent carried by centrifugal pump 4 is flowed out from centrifugal pump 4 by outflow opening 16 radial direction.
When refrigerant conveying, Problems existing is, usually needs refrigerant conveying under higher system pressure.The total system pressure of refrigeration system can more than 50bar, and the suction side of centrifugal pump 4 and on the pressure side between pressure difference possibly much smaller than this, such as may in the scope of 2.5bar to 6bar.But higher system pressure requirements centrifugal pump group has enough crushing resistances.At this, particularly definitely to avoid when refrigerant conveying leaking, because such refrigeration agent is often expensive and to bad environmental and/or poisonous, so definitely will avoid leaking in surrounding enviroment.
Construct to make centrifugal pump group to obtain enough sealing and resistance to compression, centrifugal pump 4 is arranged on around compression resistanted container 18 in.Container 18 is configured to tubulose, and closes in the end 20 of its drive motor 2 dorsad.Therefore, the container of can-like is obtained generally.This container only has three openings.They are: the opening 22 be made up of the end face of the axial end portion dorsad 20 of container 18, and suction port 24 and pressure port 26.In addition, container wall has been totally enclosed.Container 18 can weld especially in remaining region, with carrying out pressure-resistant seal.Draw refrigeration agent to be conveyed by suction port 24, then enter centrifugal pump 4 by filter 14.Then, the refrigeration agent carried by the pump stage of centrifugal pump is exported by outflow opening 16 at the opposite axial end portion of centrifugal pump 4.Next, flow of refrigerant arrives pressure port 26 through the space 28 between the outside of housing parts 10 and the inner circumferential of container 18, is then exported from centrifugal pump by pressure port 26.In order to form gap 28, the internal diameter of container 18 is greater than the external diameter of housing parts 10, and at this, container 18 preferably has the circular cross-section about spin axis X.
In inner circumferential, arrange ring 29 in the inside of container 18, it forms partition wall and will on the pressure side separate with suction side in space 28.Ring 29 abuts on the axial end portion 13 of the tubular shell be made up of housing parts 10 hermetically.Be provided with the O shape ring for sealing for this reason.Thus can anti-fluid from the opening on the pressure side flowing into suction side and the axial end portion 13 around centrifugal pump 4 space 28.Ring 29 firmly, is hermetically connected with container wall, particularly connects by being weldingly connected.
In the embodiment shown in fig. 1, suction port 24 and pressure port 26 by flange 30 institute around, centrifugal pump group can be connected on adjacent connecting pipeline by means of flange 30.At this, flange 30 and and its abutted flange (not shown) adjoined between insert a seal element for sealing respectively.In order to avoid carrying out such sealing, also can by container 18 directly together with the pipeline welding be connected.For this reason, in the embodiment illustrated in fig. 2, by means of only the tubular configured joint 32 extended radially outwardly from container 18 to form suction port 24 and pressure port 26, interface 32 directly can be welded together with the pipeline be connected.In addition, it is also conceivable to connected pipeline directly to weld on containers 18.The tie point that will seal that may form potential risk of leakage can be avoided in this way.
Around opening 20, be provided with flange 34 at the axial end portion of container 18, flange 34 is welded together with the wall of container 18 in the circumferential.Flange 34 is for connecting drive motor 2, and drive motor 2 has abutted flange 36 on its axial end portion towards centrifugal pump 4 for this reason, abutted flange 36 and flange 34 is tightened by bolt 38.O shape ring 40 for sealing is set between flange 34 and abutted flange 36.
Drive motor 2 is designed to stitch tubular motor, wherein, its slit-tube 42 is open at it, be connected with abutted flange 36 hermetically on the end of centrifugal pump 4, preferably weld with abutted flange 36.Can be realized by this mode of execution, whole centrifugal pump group only has an interface except suction port 24 and 26, inner space is to external sealed over that interface, namely between flange 34 and abutted flange 36, and the join domain between drive motor 2 and container 18.Therefore, when the suction port 24 of embodiment as shown in Figure 2 is also connected with the pipeline be connected by welding with 26, the Sealing that independent is only needed, with external sealing load space.Make the risk minimization of leakage thus.In addition, this can make maintenance become very easy, as shown in Figure 4, after unclamping bolt 38 whole centrifugal pump 4 vertically X shift out from container 18.Therefore, the whole centrifugal pump 4 comprising drive motor 2 can be changed easily.
Another feature according to the present invention of shown centrifugal pump group is the mode of execution of thrust-bearing 44, will be described in detail below in Fig. 5 to Fig. 9 to it.
From Fig. 1 and Fig. 2, thrust-bearing 44 is arranged on the central region of transmission shaft 6, and namely two axial end portions of it and transmission shaft 6 are spaced apart, and the center of distance transmission shaft 6 is nearer than distance axial end portion.Therefore, thrust-bearing 44 is between centrifugal pump 4 and the rotor 46 of drive motor 2, and rotor 46 is fixed on transmission shaft 6 equally.For this reason, be configured to two-part in this embodiment by transmission shaft 6, the part of axle in rotor 2 is separated with the part of transmission shaft 6 in centrifugal pump 4.These two parts torsionally interconnect.But it should be noted that, also can use the transmission shaft 6 of integration at this.
Thrust-bearing 44 has following advantage at centrifugal pump 4 towards the position on the end of drive motor 2: the thrust-bearing 44 passing through carried refrigeration agent lubrication is positioned at the region be under refrigeration agent maximum pressure of centrifugal pump.But thrust-bearing is still spaced apart with the rotor 46 of drive motor 2, thus makes carried refrigeration agent no longer be subject to the superheating of the used heat of drive motor 2 in this region simultaneously.This means that thrust-bearing 44 is be positioned at this region just: refrigeration agent is due to higher pressure and also not heated by drive motor and non-volatile in this region, thus here guarantees to make thrust-bearing 44 keep reliable liquid lubrication.
That the parts of thrust-bearing can be tending towards vibration due to the possible radial deflection of transmission shaft at the usual Problems existing in the central region of thrust-bearing 44 that is provided with of transmission shaft 6.According to the present invention, by by thrust bearing structure for self-aligningly this problem can be avoided.Thrust-bearing is made up of two bearing part 48 and 50, namely fixing bearing part 48 and the bearing part 50 rotated.The bearing part 50 rotated torsionally is connected with axle 6, and fixing bearing part 48 is torsionally arranged in the housing parts 52 together with being screwed in abutted flange 36.That fixing bearing part 48 or the bearing part 50 rotated all be configured to can auto-alignment (selbstausrichtend).
The bearing part 50 rotated has by suitable bearing material, the annular bearings element 54 that such as stupalith is made.On bearing element 54, the axial sides about spin axis X forms clutch shaft bearing face 56.Bearing element 54 remains on supporting member 58, wherein, makes bearing element 54 placed in the middle by O shape ring 60.At this, O shape ring 60 is arranged on the bump 62 of supporting member 58 circumferentially, bump 62 inserts in the inner circumferential of annular bearings element 54, thus O shape ring 60 is abutted in the inner circumferential of bearing element 54.Entirely abutted on supporting member 58 by the axial dorsal part bearing element 54 of bearing surface 56 dorsad.On the shoulder 65 that the radial direction that supporting member 58 is bearing in sleeve 66 by wavy spring pad 64 is given prominence to, be fixed on transmission shaft 6 at this sleeve 66.
The dorsal surface of the bearing element dorsad 54 of supporting member 58 is configured to ball type of contact surface 68.This means, surface of contact 68 has the shape of ring-type spherical section, and at this, the central point of this ball is positioned on spin axis X.Surface of contact 68 abut in conical, be configured on spherical docking surface of contact 70 accordingly in this case, docking surface of contact 70 be arranged in supporting mass 72.Therefore in this case, docking surface of contact 70 has the curvature identical with surface of contact 68, namely has identical radius.At this, surface of contact 68 is formed as convex, and docks surface of contact 70 and be formed as concavity.Supporting mass 72 is bearing in again on the ring projection 74 of transmission shaft 6.In embodiment shown in this, bump 74 is made up of the axial end portion of the joint of transmission shaft 6, and this axial end portion forms the rotor shaft of rotor 46.At this, the bump 74 opposite ground orientation of shoulder 65, thus make support 72 and supporting member 58 act on clamping between shoulder 65 and bump 74 by the elastic force of spring pad 64, surface of contact 68 and docking surface of contact 70 keep sticking together by this elastic force.
Due to surface of contact 68 and the spherical form docking surface of contact 70, supporting member 58 can around the spherical central point deflection of surface of contact face 68 and docking surface of contact 70, thus bearing surface 56 can and axis of perpendicular to spin axis X orthogonal around two about the Angle Position of spin axis X be changed.Bearing surface 56 can be made in this way automatically, freely to aim on its Angle Position about spin axis X, and at this, surface of contact 68 slides on docking surface of contact 70.Do to guarantee by the elastic force of spring pad 64, even if when pump is in halted state, when the axial force acted on when being in operation on thrust-bearing no longer exists, then surface of contact 68 and docking surface of contact 70 are fixed to one another, thus the Angle Position of self-adjusting bearing surface 56 in advance is also remained in the halted state of pump.
Fixing bearing part 48 is also configured to can be self-aligning.Fixing bearing part 48 has multiple bearing liner 76, and the axial surface of these bearing liners forms two bearing surfaces 78, and bearing surface 78 and clutch shaft bearing face 56 stick together slidably.Bearing liner 76 is fixed in stop ring 80, and stop ring 80 has the recess 82 corresponding with the external frame of bearing liner 76.Therefore, bearing liner 76 can be extended by recess 82, and is radially fixed in stop ring 80 with circumferencial direction.On the axle side of bearing surface 78 dorsad, bearing liner 76 is close to supporting member 84.Supporting member 84 has ball type of contact surface 86 on the axle side of its bearing liner 76 dorsad.This ball type of contact surface 86 forms circular segment or the annular cross section on ball surface, and at this, the central point of ball is positioned on spin axis X.Surface of contact 86 is attached on the docking surface of contact 88 that is configured in housing parts 52.Docking surface of contact 88 is configured to conical, is then configured to the spherical of correspondence in this case, that is, dock surface of contact 88 and have the curvature identical with surface of contact 86, and bend around identical central point.At this, surface of contact 86 is convex curvature, and docking surface of contact 88 is then convex curve.This embodiment allows supporting member 84 to deflect around the spherical central point of definition surface of contact 86 and docking surface of contact 88.Therefore bearing surface 78 on bearing liner 76 can be made in its Angle Position about spin axis X auto-alignment.This means that bearing surface 78 can around two orthogonal axiss of oscillation (perpendicular to longitudinal axis X) free deflection in the angular range of setting.In this way, bearing surface 78 can always entirely abut on the bearing surface 56 of swivel bearing parts, thus does not occur swingingly to remain sliding contact in situation at bearing surface.
As shown in Figure 9, be peripherally provided with three radial grooves 90 extended in bearing surface 86 evenly distributedly, it is for improving fluid circulation and the therefore lubrication improved in thrust-bearing.
In order to make supporting member 86 torsionally remain on housing parts 52, the periphery of surface of contact 86 is provided with three and is peripherally uniformly distributed and the engagement bump 92 extended vertically, it correspondingly inserts in the recess 94 of housing parts 52.At this, between engagement bump 92 and recess 94, be disposed radially the gap of the as much that can need needed for surface of contact 86 and the swing of docking between surface of contact 88 described by maintenance or alignment motion especially.
Correspondingly supporting member 58 is torsionally bearing on supporting mass 72, makes torque can be delivered to supporting member 58 from supporting mass 72.For this reason, the periphery of surface of contact 68 arranges the engagement bump 96 radially extended, and in the recess 98 making it correspondingly insert supporting mass 72.Here, especially radially engaging between bump 96 and enough spaces are also being set in recess 98, the swing of face 68 relative to docking surface of contact 70 can be kept in touch further.
Surface of contact 68,86 and docking surface of contact 70,88 are preferably made up of hard, wear-resisting material, particularly supporting member 58, housing parts 52 and supporting mass 72 may be also had can be made up of corresponding harder material, such as firmly metal or pottery.
Reference numerals list
2-drive motor
4-centrifugal pump
6-transmission shaft
8-impeller
10-housing parts
12-guider
13-axial end portion
14-filter
16-outflow opening
18-container
20-axial end portion
22-opening
24-suction port
26-pressure port
28-gap
29-ring
30-flange
32-joint
34-flange
36-abutted flange
38-bolt
40-O shape ring
42-slit-tube
44-thrust-bearing
46-rotor
The bearing part that 48-is fixing
The rotatable bearing part of 50-
52-housing parts
54-bearing element
56-bearing surface
58-supporting member
60-O shape ring
62-bump
64-spring pad
65-shoulder
66-sleeve
68-surface of contact
70-docks surface of contact
72-supporting mass
74-bump
76-bearing liner
78-bearing surface
80-stop ring
82-recess
84-supporting member
86-surface of contact
88-docks surface of contact
90-groove
92-engages bump
94-recess
96-engages bump
98-recess
X-spin axis
Claims (6)
1. one kind has and is configured to the seam drive motor (2) of tubular motor and the refrigerated medium pump unit of centrifugal pump (4), it is characterized in that, described centrifugal pump (4) by as additional wall tubular container (18) around, this tubular container (18) has inhalation interface (24) and pressure interface (26), and with the electric machine casing of the first axial end portion and described drive motor (2) removably and be connected hermetically, and be configured to close at the opposite axial end portion (20) of this tubular container (18), wherein, described inhalation interface (24) and described pressure interface (26) are configured to directly be welded on connecting pipeline, described tubular container (18) directly utilizes described slit-tube to seal or directly and be connected with the flange that described slit-tube welds, and wherein, described centrifugal pump (4) has the housing parts connecting into tubular shell in the axial direction, this tubular shell by the described tubular container as additional wall (18) institute around, described tubular container (18) is configured to single parts, and only there is described inhalation interface (24) and pressure interface (26) and the mouth for being connected with electric machine casing.
2. refrigerated medium pump unit as claimed in claim 1, it is characterized in that, described inhalation interface (24) and/or described pressure interface (26) radially stretch out from described tubular container (18).
3. refrigerated medium pump unit as claimed in claim 1, it is characterized in that, described tubular container (18) has closed wall.
4. refrigerated medium pump unit as claimed in claim 1, it is characterized in that, described inhalation interface (24) and/or described pressure interface (26) are equipped with adpting flange (30).
5. as the refrigerated medium pump unit above as described in any one claim, it is characterized in that, in described tubular container (18), be provided with ring-type partition wall, this ring-type partition wall by the suction side (24) of described centrifugal pump (4) and on the pressure side (26) be separated from each other.
6. refrigerated medium pump unit as claimed in claim 1, is characterized in that, for the system pressure of refrigeration agent to be conveyed, be configured to measuring body by described tubular container (18).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP10000704.6 | 2010-01-25 | ||
| EP10000704.6A EP2348219B1 (en) | 2010-01-25 | 2010-01-25 | Coolant pump system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102135103A CN102135103A (en) | 2011-07-27 |
| CN102135103B true CN102135103B (en) | 2015-08-19 |
Family
ID=42236332
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110031160.9A Active CN102135103B (en) | 2010-01-25 | 2011-01-25 | Refrigerated medium pump unit |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20110182725A1 (en) |
| EP (1) | EP2348219B1 (en) |
| CN (1) | CN102135103B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ES2682035T3 (en) | 2013-03-19 | 2018-09-18 | Flow Control Llc. | Low profile pump suitable for mounting in various configurations |
| DE102013005923A1 (en) * | 2013-04-04 | 2014-10-09 | Linde Aktiengesellschaft | Refrigerant compressor and method for compressing gas and method for producing liquid hydrogen |
| JP6111915B2 (en) * | 2013-07-18 | 2017-04-12 | ダイキン工業株式会社 | Turbo compressor and turbo refrigerator |
| CN111902634B (en) | 2018-02-05 | 2022-06-14 | 富兰克林电气有限公司 | Fault protection of pump-motor assembly |
| WO2019152951A1 (en) * | 2018-02-05 | 2019-08-08 | Franklin Electric Co., Inc. | Modular submersible motor and pump assembly |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2450137A (en) * | 1944-12-01 | 1948-09-28 | Smith Corp A O | Multistage centrifugal pump |
| GB701511A (en) * | 1949-11-01 | 1953-12-30 | Hayward Tyler & Co Ltd | Improvements in and relating to pump and motor combinations |
| FR1091514A (en) * | 1953-07-13 | 1955-04-13 | Vogel Pumpen | Device for absorbing axial forces in submersible motors |
| GB2242934A (en) * | 1990-04-09 | 1991-10-16 | Klein Schanzlin & Becker Ag | Pot casing pump |
| EP0657653A1 (en) * | 1993-12-08 | 1995-06-14 | Ebara Corporation | Canned motor pump |
| DE4415157A1 (en) * | 1994-05-02 | 1995-11-09 | Klein Schanzlin & Becker Ag | Self-priming multi-stage centrifugal pump |
Family Cites Families (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2343511A (en) * | 1941-06-13 | 1944-03-07 | Byron Jackson Co | Double casing pump |
| US2374122A (en) * | 1942-12-05 | 1945-04-17 | Arthur J Nelson | Double case pump |
| US2365310A (en) * | 1944-03-02 | 1944-12-19 | Worthington Pump & Mach Corp | Rotor unit |
| US2376528A (en) * | 1944-03-02 | 1945-05-22 | Worthington Pump & Mach Corp | Centrifugal pump |
| DE1528795A1 (en) * | 1965-07-02 | 1969-12-11 | Lederle Pumpen & Maschf | High pressure canned motor pump |
| DE3014103A1 (en) * | 1980-04-12 | 1981-10-15 | Hermetic-Pumpen Gmbh, 7803 Gundelfingen | Pump set with electromotor between two pumps - has fluid passing through motor from first to second pump |
| US5009578A (en) * | 1987-10-27 | 1991-04-23 | Crane Co. | Motor driven pumps |
| US5591016A (en) * | 1994-11-30 | 1997-01-07 | Nikkiso Co., Ltd. | Multistage canned motor pump having a thrust balancing disk |
| US5888053A (en) * | 1995-02-10 | 1999-03-30 | Ebara Corporation | Pump having first and second outer casing members |
| US5961301A (en) * | 1997-07-31 | 1999-10-05 | Ansimag Incorporated | Magnetic-drive assembly for a multistage centrifugal pump |
| DE29819363U1 (en) * | 1998-10-30 | 1999-02-18 | KSB AG, 67227 Frankenthal | Compensator |
| GB0117941D0 (en) * | 2001-07-24 | 2001-09-19 | Weir Pumps Ltd | Pump assembly |
| ES2586658T3 (en) * | 2003-03-10 | 2016-10-18 | Thermodyn | Centrifugal Compressor Group |
| US20050036895A1 (en) * | 2003-08-11 | 2005-02-17 | Mth Tool Company, Inc. | Canned motor and pump |
| JP4633396B2 (en) * | 2004-07-16 | 2011-02-16 | 株式会社荏原製作所 | Centrifugal pump |
| US7520720B2 (en) * | 2004-07-28 | 2009-04-21 | Sta-Rite Industries, Llc | Pump |
| JP4642788B2 (en) * | 2007-01-22 | 2011-03-02 | 株式会社荏原製作所 | Multistage high pressure pump |
-
2010
- 2010-01-25 EP EP10000704.6A patent/EP2348219B1/en active Active
-
2011
- 2011-01-24 US US13/012,287 patent/US20110182725A1/en not_active Abandoned
- 2011-01-25 CN CN201110031160.9A patent/CN102135103B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2450137A (en) * | 1944-12-01 | 1948-09-28 | Smith Corp A O | Multistage centrifugal pump |
| GB701511A (en) * | 1949-11-01 | 1953-12-30 | Hayward Tyler & Co Ltd | Improvements in and relating to pump and motor combinations |
| FR1091514A (en) * | 1953-07-13 | 1955-04-13 | Vogel Pumpen | Device for absorbing axial forces in submersible motors |
| GB2242934A (en) * | 1990-04-09 | 1991-10-16 | Klein Schanzlin & Becker Ag | Pot casing pump |
| EP0657653A1 (en) * | 1993-12-08 | 1995-06-14 | Ebara Corporation | Canned motor pump |
| DE4415157A1 (en) * | 1994-05-02 | 1995-11-09 | Klein Schanzlin & Becker Ag | Self-priming multi-stage centrifugal pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102135103A (en) | 2011-07-27 |
| EP2348219A1 (en) | 2011-07-27 |
| EP2348219B1 (en) | 2016-06-29 |
| US20110182725A1 (en) | 2011-07-28 |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |