CN103032338B - Refrigerant pump - Google Patents
Refrigerant pump Download PDFInfo
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- CN103032338B CN103032338B CN201210424548.XA CN201210424548A CN103032338B CN 103032338 B CN103032338 B CN 103032338B CN 201210424548 A CN201210424548 A CN 201210424548A CN 103032338 B CN103032338 B CN 103032338B
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- blade
- impeller
- blade part
- medium pump
- fluid
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- 239000003507 refrigerant Substances 0.000 title claims abstract description 66
- 239000012530 fluid Substances 0.000 claims abstract description 71
- 238000005057 refrigeration Methods 0.000 claims description 49
- 239000003795 chemical substances by application Substances 0.000 claims description 35
- 230000000694 effects Effects 0.000 claims description 7
- 230000033001 locomotion Effects 0.000 claims description 4
- 238000005452 bending Methods 0.000 claims description 3
- 239000006200 vaporizer Substances 0.000 claims description 3
- 238000000926 separation method Methods 0.000 description 9
- 238000004519 manufacturing process Methods 0.000 description 7
- 239000007788 liquid Substances 0.000 description 6
- 230000002093 peripheral effect Effects 0.000 description 5
- 230000000052 comparative effect Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000005242 forging Methods 0.000 description 2
- 238000001746 injection moulding Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 239000011347 resin Substances 0.000 description 2
- 229920005989 resin Polymers 0.000 description 2
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical class O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 1
- 208000016285 Movement disease Diseases 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 230000005514 two-phase flow Effects 0.000 description 1
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- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses a refrigerant pump, which comprises a shell, wherein the interior of the shell is partitioned into a rotor chamber and a motor chamber by a dividing plate, an impeller is arranged in the rotor chamber, and a refrigerant main runner is formed between the rotor chamber and the impeller; and the rotor chamber is also provided with a suction inlet and an exhaust outlet which cover the side part and the radial outer side of the impeller. The shape of the shell which is in contact with fluid is approximately identical with the eddy direction, so that the eddy loss is reduced; and in addition, the separating loss of the fluid flowing at an inlet of the impeller is reduced, and the flowing property of the fluid is improved. On the basis that the shapes of blades incline towards the rotating direction, the runner between the side surfaces of the blades and the shell component is semicircular, so that the impeller efficiency can be further improved, and the whole efficiency of the pump can be further improved.
Description
Technical field
The invention belongs to fluid machinery technical field, particularly a kind of refrigerated medium pump.
Background technique
In the refrigerant piping for refrigeration plant, aircondition, be provided with the fluid machinery and refrigerated medium pump that make refrigerant circulation.Refrigerated medium pump shown in patent documentation 1 (JP 2003-161284), having fluid intake and exhaust port and being formed in the shell of circular runner, is configured with the impeller being furnished with multiple blade in outer rim.Impeller rotates in shell high speed, thus refrigeration agent is roughly rotated a circle, and obtains the refrigeration agent of required lift.
But the shape of the blade of this refrigerated medium pump is planar, during vane rotary, fluid produces larger separation losses at impeller inlet place.And, in refrigerated medium pump represented by patent documentation 1, because the cross section of fluid channel shape between shell and impeller is orthogonal rectangle, in the operation process of refrigerated medium pump, when fluid in runner with eddy current shape rotary presser time, the angular region that is flowing in of fluid easily gets muddled, and can produce power lose, and causes the problems such as the efficiency of reduction pump.
In addition, refrigerated medium pump as shown in patent documentation 2 (JP 2003-193992) has following structure, multiple through hole (blade groove) is formed in the thickness of slab direction of discoideus impeller, when the impeller is rotated, flowing while rotating in through hole (blade groove) by making fluid, obtaining the fluid of regulation lift.
But, when discoideus impeller being formed with the structure of multiple through hole (blade groove), the radial outside of blade groove or through hole is covered by the periphery of impeller, at the radial outside of this blade groove or through hole, fluid in runner and the peripheral part of impeller clash, energy-producing consumption.And because through hole (blade groove) only opens to the side runner of impeller, the flow of fluid tails off.
Refrigerated medium pump of the prior art has the structure forming multiple through hole (blade groove) on discoideus impeller, and covered by the periphery of impeller due to the radially outer side portions of blade groove or through hole, fluid in runner and the peripheral part of impeller clash, energy-producing consumption.And only open to the side runner of impeller due to through hole (blade groove), the flow of fluid tails off.And because the runner between adjacent two blades opens to the sidepiece runner of impeller and radial outside runner in the present invention, flow fully can be guaranteed; And different from the runner being formed with blade groove or through hole, do not conflict between fluid and the peripheral part of impeller, the energy loss produced between fluid and the peripheral part of impeller can be reduced.
Refrigerated medium pump accommodates the drive units such as motor in shell, and the thickness of slab direction of discoideus impeller is inserted with running shaft, and impeller is connected with drive units such as motors by running shaft.Once the drive units such as motor rotate, impeller also can rotate, the flow passage while fluid spiral rotates between impeller and shell.Therefore, the flow channel shape between impeller and shell is one of principal element affecting the flow of fluid and the motion state of fluid.In prior art, when the cross section of fluid channel shape between the side and case member of blade is orthogonal rectangle, the angular region that is flowing in of fluid easily gets muddled, and produces flow losses, is the one of the main reasons reducing pump efficiency.
And the present invention is further, the flow channel shape between the side of blade and case member is improved to semi-circular shape, like this with the shape of the case member wall of fluid contact and the direction of eddy current roughly consistent, reduce eddy current loss.Its result, can improve the efficiency of impeller, and can improve the efficiency of pump entirety.In the shape of blade towards on the basis that sense of rotation tilts, the flow channel shape between the side of blade and case member is semi-circular shape, can improve the efficiency of impeller further, and can improve the efficiency of pump entirety further.
Further, form the first blade part of blade and the second blade part owing to having symmetrical shape, and relative to comprising the center line of outer circumferential face and the vertical surface dividing plectane equally tilts towards sense of rotation, therefore, the separation losses of fluid at impeller inlet place reduces, and can improve the mobile performance of fluid.
In the prior art, when the shape of blade is planar, fluid produces larger separation losses at impeller inlet place, the therefore efficiency step-down of pump.And the present invention is owing to forming the first blade part of blade and the second blade part has symmetric shape, relative to comprising the center line of outer circumferential face and the vertical surface dividing plectane equally tilts towards sense of rotation, the separation losses of fluid at impeller inlet place reduces, and can improve the mobile performance of fluid.Its result, can improve the efficiency of impeller, and can improve the efficiency of pump entirety.
Further again, due to the first outer surface and the second outer surface bending, and tilt towards sense of rotation, therefore, flowing not easily produces separation losses, can improve the mobile performance of fluid.
Carry out rotating when impeller and suck fluid from suction port, the fluid be inhaled into first with the outer surface on rear side of the sense of rotation being positioned at the first blade part and be positioned at the second blade part sense of rotation on rear side of outer surface contact.Here, due to two place's surface curvatures, and tilt towards sense of rotation, therefore, the separation losses of flowing reduces, and can improve the mobile performance of fluid.Its result, can improve the efficiency of impeller, and can improve the efficiency of pump entirety.
Refrigerated medium pump provided by the invention, the fluid be inhaled into, along the first blade part tilted towards sense of rotation and the flowing of the second blade part, during the blade part flowing that the fluid edge that viscosity is low tilts, not easily produces flow separation, the efficiency of impeller can be improved, and the efficiency of pump entirety can be improved.
Refrigerated medium pump provided by the invention, plectane portion and multiple blade integrally formed, and each side margin line of the first blade part and the second blade part is in line, can manufacture cost be reduced.Such as, then pass through forging when manufacturing impeller with metal, with then integrally formed by injection moulding during resin manufacture impeller, and each side margin line of the first blade part and the second blade part is in line, can manufacture cost be reduced.
Summary of the invention
The problem that the present invention solves is to provide a kind of refrigerated medium pump, by the shape optimization of the blade shape and runner that make refrigerated medium pump, reduces energy loss during vane rotary, provides efficient refrigerated medium pump.
The present invention is achieved through the following technical solutions:
A kind of refrigerated medium pump, comprise housing, in housing, divided plate is divided into rotor chamber and motor room, is provided with impeller in rotor chamber, is the sprue of refrigeration agent between rotor chamber and impeller; Rotor chamber also offers and covers the sidepiece of described impeller and the suction port of radial outside and exhaust port;
Be provided with motor in motor room, motor comprises stators and rotators, and the axis hole that the live axle be connected with rotor is arranged through fragmenting plate is connected with impeller;
Impeller comprises plectane portion and is arranged on multiple blades of its outer rim, and blade is uniform intervals arrangement in the sense of rotation of impeller; Runner between two adjacent blades opens to the sidepiece runner of impeller and radial outside runner;
When impeller is rotated via drive shaft by motor, divide the both sides to plectane portion from the refrigerant fluid of suction port suction, carry out spiral motion towards circumferential direction respectively, by pressurized during each blade, discharge from exhaust port.
Cross section of fluid channel shape between each side of described blade and housing is semi-circular shape.
First side of described blade, the cross section of fluid channel shape between the second side and housing are semi-circular shape.
Described blade comprises the first blade part and the second blade part, and the first blade part is symmetrical relative to the thickness of slab center line of the outer circumferential face in plectane portion with the second blade part;
First blade part, the second blade part tilt towards sense of rotation relative to vertical surface respectively, and described vertical surface comprises thickness of slab center line and divides plectane equally.Described first blade part becomes V-shaped with the second blade part.
The bottom of described blade is connected with plectane portion radial direction, the tip edge line of blade is the curve had on the ring surface of certain radius, the tip edge projection line of the internal surface of the first blade part and center line towards rotating square to angle be 60 °, the tip edge projection line of the internal surface of corresponding second blade part and center line towards rotating square to angle be 60 °; The tip edge projection line of the tip edge projection line of the outer surface of the first blade part and the outer surface of the second blade part is 120 ° along rotating reciprocal angle; Side margin line between the bottom of blade and top is straight line.
Described outer surface, the internal surface being positioned at the first blade part, the outer surface, the internal surface that are positioned at the second blade part are curved surface, and the degree of crook in the bending sideline of the annulus profile plan view of blade from bottom to top reduces gradually.Each side margin line of the first blade part and the second blade part is straight line.
Describedly work as vane rotary, after refrigerant fluid sucks from suction port, the refrigerant fluid be inhaled into contacts with the outer surface of the first blade part and the outer surface of the second blade part; The refrigerant fluid be inhaled into flows along the outer surface of the first blade part outer surface tilted towards sense of rotation and the second blade part side.
Described plectane portion and blade are one of the forming.
Based on the aircondition of described refrigerated medium pump, comprise heat source side refrigerant circuit and utilize side refrigerant circuit, the refrigeration agent in heat source side refrigerant circuit with utilize the refrigeration agent in the refrigerant circuit of side to carry out heat exchange in refrigeration agent-refrigerant heat exchanger;
The outdoor unit of heat source side refrigerant circuit is connected with compressor, four-way switching valve, thermal source heat exchanger and expansion mechanism in turn via heat source side refrigerant piping;
Utilize side refrigerant circuit by utilize side refrigerant piping to connect successively to utilize the reservoir vessel of side refrigeration agent, refrigerated medium pump and be located at indoor play effect as vaporizer utilize side heat exchanger, enable to utilize side refrigeration agent to circulate;
Refrigerated medium pump and refrigeration agent-refrigerant heat exchanger are configured in basement.
Compared with prior art, the present invention has following useful technique effect:
Refrigerated medium pump provided by the invention, wherein the runner of refrigerant fluid forms according to the shape of rotor chamber and the shape of multiple blade, different from the runner being formed with blade groove and through hole of the prior art, can not clash between fluid and the peripheral part of impeller.
Accompanying drawing explanation
Fig. 1 is the schematic diagram representing the aircondition refrigerant piping system using refrigeration pump;
Fig. 2 is the generalized section of refrigerated medium pump;
Fig. 3 is the rotor chamber sectional drawing of refrigerated medium pump;
Fig. 4 is the three-dimensional pattern figure of impeller;
Fig. 5 is the partial enlarged drawing in impeller blade portion;
Fig. 6-1 is the partial enlarged drawing of the Y-direction plan view of blade part;
Fig. 6-2 is the partial enlarged drawing of the X-direction side view of blade part;
Fig. 6-3 is the partial enlarged drawing of the Z-direction front view of blade part;
Fig. 7-1 is the plan view of the A-A part annulus profile of Fig. 6-2;
Fig. 7-2 is the plan view of the B-B part annulus profile of Fig. 6-2;
Fig. 7-3 is the plan view of the C-C part annulus profile of Fig. 6-2;
Fig. 8 is the schematic diagram representing the different section of blade Z-direction.
Fig. 9-1 is the sectional view representing half round runner;
Fig. 9-2 is the ideograph representing fluid flowing in half round runner;
Figure 10-1 is the sectional view representing orthogonal rectangle runner;
Figure 10-2 is the ideograph of fluid flowing in expression half orthogonal rectangle runner;
Figure 11 is the partial enlarged drawing of the Y-direction plan view of the different four kinds of blades in angle of inclination;
Figure 12 is the efficiency comparison result of each refrigerated medium pump of different blade shapes and runner combination;
Figure 13 is each refrigeration agent lift of pump comparative result of different blade shapes and runner combination.
Embodiment
Below in conjunction with specific embodiment, the present invention is described in further detail, and the explanation of the invention is not limited.
Refrigerated medium pump provided by the invention, by the improvement of the improvement of the blade to impeller and the flow channel shape between impeller and housing, reduces energy loss during vane rotary, improves the efficiency of refrigerated medium pump.This refrigerated medium pump can be used for the refrigerant circulation of refrigeration plant, aircondition.
Concrete is described for aircondition with refrigerated medium pump.The refrigerant piping system diagram of aircondition 300 shown in Figure 1.Aircondition 300 by heat source side refrigerant circuit I with utilize side refrigerant circuit II to form, the refrigeration agent I in heat source side refrigerant circuit I with utilize the refrigeration agent II in side refrigerant circuit II to carry out heat exchange in refrigeration agent-refrigerant heat exchanger 52.
The outdoor unit 50 of heat source side refrigerant circuit I is connected with compressor, four-way switching valve, thermal source heat exchanger, expansion mechanism (not shown) in turn via heat source side refrigerant piping 51.As heat source side refrigeration agent, spendable refrigeration agent is R134a, refrigeration agent R407C etc. such as.
The indoor that need carry out air conditioning play effect as vaporizer utilizes side heat exchanger 63,64,65 by utilizing side refrigerant piping 61 to connect successively to utilize the reservoir vessel 62 of side refrigeration agent, refrigerated medium pump 1 and being located to utilize side refrigerant circuit II, enable to utilize side refrigeration agent to circulate.
Side heat exchanger 63,64,65 is utilized to be the air heat exchangers with fan.As the refrigeration agent utilizing side refrigeration agent can use carbon dioxide series.And refrigerated medium pump 1 and refrigeration agent-refrigerant heat exchanger 52 are configured in basement.
The heat source side refrigeration agent that flows out of machine 50, is sent to refrigeration agent-refrigerant heat exchanger 52 via heat source side refrigerant piping 51, and from utilizing the side refrigeration agent that utilizes utilizing side refrigerant piping 61 to transport of side refrigerant circuit II to carry out heat exchange outdoor.And, being obtained and cold and hot utilizing side refrigeration agent, utilizing side heat exchanger 63,64,65 by utilizing the refrigerated medium pump 1 in side refrigerant circuit II to be sent to.
In this aircondition 300, be supplied to the cold and hot of thermal source refrigeration agent at the outdoor unit 50 of heat source side refrigerant circuit I, be supplied to by the heat exchange in refrigeration agent-refrigerant heat exchanger 52 and utilize side refrigeration agent, to make to utilize side refrigerant cools.Utilizing in side refrigerant circuit II, side refrigeration agent is utilized to be circulated as follows by refrigerated medium pump 1, each layer is sent to from basement by refrigeration agent, and return basement, what cool in refrigeration agent-refrigerant heat exchanger 52 utilizes side refrigeration agent to flow through via refrigerated medium pump 1 to utilize side heat exchanger 63,64,65, utilizing in side heat exchanger 63,64,65, part utilizes side refrigeration agent evaporation that indoor air is cooled.And the part flashing to gas-liquid two-phase flow utilizes side refrigeration agent, be back to whole liquid condition by refrigeration agent-refrigerant heat exchanger 52 cooling and flow into refrigerated medium pump 1, send after being pressurizeed by refrigerated medium pump 1.
Below to refrigerated medium pump 1 detailed description further.
The generalized section of refrigerated medium pump 1 shown in Figure 2, in the housing 21 of refrigerated medium pump 1, divided plate 22 is divided into rotor chamber 23 and motor room 24, is provided with impeller 10, is provided with motor 28 in motor room in rotor chamber 23.Between housing 21 with impeller 10, runner becomes the sprue 41 of refrigeration agent.
Motor 28 is made up of stator 29 and rotor 30, and impeller 10 is connected with the rotor 30 of motor 28 via live axle 31.While live axle 31 runs through the axis hole be formed on fragmenting plate 22, its lower end is configured on the base plate 21a of housing 21.
Fig. 3 is rotor chamber 23 sectional drawing of refrigerated medium pump 1, and Fig. 4 is the three-dimensional pattern figure of impeller 10.As shown in Figure 3, Figure 4, impeller 10 comprises the plectane portion 12 with certain thickness of slab, and extends and multiple blades 11 of equidistantly arrangement on sense of rotation u from the outer rim radial direction in plectane portion 12.
Housing 21 is formed with suction port 81 and exhaust port 82, and covers impeller 10 side and radial outside.And the runner between adjacent two blades 11,11 opens to the side runner of impeller 10 and radial outside runner.
In refrigerated medium pump 1, once impeller 10 is rotated via live axle 31 by the driving of motor 28, divide the both sides to plectane portion 12 from the liquid refrigerant of suction port 81 suction, carry out spiral motion towards circumferential direction respectively, by pressurized during each blade 11, discharge from exhaust port 82.Moulding pressure is configured to obtain the authorized pressure of liquid refrigerant needed for the lift utilizing side refrigerant circuit II to circulate.
Cross section of fluid channel shape between the side of blade 11 and case member 21 is semi-circular shape, and the cross section of fluid channel shape between the 1st side 113 of concrete blade 11 and case member 21 and the cross section of fluid channel shape between the 2nd side 114 and case member 21 are respectively semi-circular shape.
Fig. 5 is the partial enlarged drawing of the blade 11 of impeller 10.As shown in Figure 5, each blade 11 has the first blade part 111 and the second blade part 112 respectively.Here, the thickness of slab direction center line 122 of the outer circumferential face 121 in the first blade part 111 and the relative plectane portion 12 of the second blade part 112 has symmetrical shape.And the first blade part 111 and the 2 the second blade parts 112 are relative to comprising the center line 122 of outer circumferential face 121 and the imagination vertical surface dividing plectane portion 12 equally tilts towards sense of rotation u.
The partial enlarged drawing that the partial enlarged drawing that Fig. 6-1 is the partial enlarged drawing of the Y-direction plan view of blade 11, Fig. 6-2 is the X-direction side view of blade 11, Fig. 6-3 are the Z-direction front view of blade 11.As shown in Fig. 6-1 ~ 6-3, the first blade part 111 and the second blade part 112 one-tenth V-shaped;
The bottom of blade 11 is connected with plectane portion 12 radial direction, the tip edge line of blade 11 is the curve had on the ring surface of certain radius, the tip edge projection line of the internal surface 1112 of the first blade part 111 and center line 122 towards rotating square to angle be 60 °, the tip edge projection line of the internal surface 1122 of corresponding second blade part 112 and center line 122 towards rotating square to angle be 60 °; The tip edge projection line of the tip edge projection line of the outer surface 1111 of the first blade part 111 and the outer surface 1121 of the second blade part 112 is 120 ° along rotating reciprocal angle; Side margin line between the bottom of blade 11 and top is straight line.
In Fig. 6-2, A-A, B-B, C-C are the annulus profile increased gradually with axial line distance from bottom to top.
The C-C part annulus profile plan view that the B-B part annulus profile plan view that Fig. 7-1 is the A-A part annulus profile plan view of Fig. 6-2, Fig. 7-2 is Fig. 6-2, Fig. 7-3 are Fig. 6-2.As shown in Fig. 7-1 ~ 7-3, be positioned at the outer surface 1111 of the first blade part 111, internal surface 1112, the outer surface 1121, the internal surface 1122 that are positioned at the second blade part 112 are curved surface,, blade 11 from bottom to top (from A to C) annulus profile plan view in sideline degree of crook reduce gradually.As in Figure 6-1, when directly overlooking blade, plan view is quadrilateral.
The side margin line of Fig. 6-3 Leaf is straight line, in Fig. 8, D-G is from center line 122 to blade edge, and each section increased progressively successively with the distance of decentre line 122, gained sectional drawing D-D, E-E, F-F, G-G are quadrilateral, and wherein the angle of inclination of blade edge line reduces successively.
Such as, then pass through forging when manufacturing impeller with metal, with then integrally formed by injection moulding during resin manufacture impeller, and each side margin line of the first blade part and the second blade part is in line, can manufacture cost be reduced.
Once impeller 10 rotates, fluid sucks from suction port 81, after the fluid be inhaled into enters the runner between blade 11, contact with the first blade part 111, second blade part 112, the fluid be namely inhaled into flows along the 1st outer surface 1111 of the first blade part 111 side tilted towards sense of rotation and the 2nd outer surface 1121 of the second blade part 112 side.Because of CO
2the blades flows that the fluid edge that the viscosity such as refrigeration agent are low tilts, and the 1st outer surface 1111 being positioned at the first blade part 111 suction port side and the 2nd outer surface 1121 that is positioned at the second blade part 112 suction port side are curved surface, the separation losses of fluid at impeller inlet place reduces, and can improve the mobile performance of fluid.Its result, can not produce turbulent flow or the flow separation of fluid flowing, can improve the efficiency of impeller, and can improve the efficiency of pump entirety.
Meanwhile, low-energy refrigerant fluid enters at runner radius smaller part (bottom) between blade 11, through the acting effect of blade 11, obtains higher-energy, flows out from runner radius larger part (top); After high-octane refrigerant fluid flows out to sprue, carry out momentum transfer with the fluid of sprue, self-energy reduces; And then enter runner between next blade 11, repeat above-mentioned energy exchange processes.So just make overall refrigerant fluid energy increase, pressure increase.
Fig. 9-1 is sectional shape figure, Fig. 9-2 of half round runner is the ideograph representing fluid flowing in half round runner.As shown in fig. 9-1, the 1st side 113 of blade 11, the flow channel shape between the 2nd side 114 and case member 21 are respectively semicircle.
Such as, be 8 DEG C by temperature, inlet pressure is the liquid CO of 4.5Mpa
2refrigeration agent sucks with in the refrigerated medium pump of 3600rpm rotation, according to the flowing that CFD (Computational Fluid Dynamics) analyzes pump inner refrigerant, obtains the result represented by Fig. 9-2.Here, the sectional shape due to fluid course is semicircle, therefore roughly the same with the shape of case member 21 wall of fluid contact and the direction of eddy current, reduces eddy current loss.
As comparative example, Figure 10-1 represents that sectional shape figure, Figure 10-2 of orthogonal rectangle runner is the ideograph representing fluid flowing in orthogonal rectangle runner.As shown in Figure 10-1, the flow channel shape between the first side 113 of blade 11 and case member 21 and the flow channel shape between the second side 114 and case member 21 are respectively orthogonal rectangle, and blade 11 is the plate blade as prior art.
In the same manner as described above, temperature is 8 DEG C, inlet pressure is the liquid CO of 4.5Mpa
2refrigeration agent sucks with in the refrigerated medium pump of 3600rpm rotation, according to the flowing that CFD analyzes pump inner refrigerant, obtains the result represented by Figure 10-2., because the sectional shape of fluid course is orthogonal rectangle, therefore easily there is movement disorder in angular region here, produce loss.
Select four kinds of blades that the centerline dip angle of relative plectane portion outer circumferential face is different, investigate the impact that efficiency or the lift of pump are brought.The Y-direction partial enlarged drawing of Figure 11 to be the tip edge projection line of the tip edge projection line of the outer surface 1111 of the first blade part 111 and the outer surface 1121 of the second blade part 112 along the angle of sense of rotation (oppositely) be four kinds of blades of 100 °, 110 °, 120 °, 130 °, the comparative result that the comparative result that Figure 12 is each refrigerated medium pump efficiency of different blade shapes and runner combination, Figure 13 are each refrigerated medium pump lift of different blade shapes and runner combination.
Figure 12, in Figure 13, line a1, a2 represents the combination (A type) of orthogonal rectangle runner and planar blade, line b1, b2 represents half round runner and the combination (Type B) towards the angle of inclination that sense of rotation tilts being the blade shape of 100 °, line c1, c2 represents half round runner and the combination (C type) towards the angle of inclination that sense of rotation tilts being the blade shape of 110 °, line d1, d2 represents half round runner and the combination (D type) towards the angle of inclination that sense of rotation tilts being the blade shape of 120 °, line e1, e2 represents half round runner and the combination (E type) towards the angle of inclination that sense of rotation tilts being the blade shape of 130 °.Experimental result, obtains result as represented by table 1.
The testing result of the combination of table 1 different shaped blade shape
Known to Figure 12, Figure 13 and table 1, with the orthogonal rectangle runner of prior art and the combination of planar blade, namely A type pump is compared, half round runner and the combination of blade shape with the angle of inclination tilted towards sense of rotation, namely each side such as flow, efficiency of Type B, C type, D type, E type pump has better effect.Wherein, particularly half round runner and the combination of blade shape towards the angle of inclination that sense of rotation tilts being 120 °, i.e. the refrigerated medium pump of D type, has best effect in efficiency.
Claims (7)
1. a refrigerated medium pump, it is characterized in that, comprise housing (21), in housing (21), divided plate (22) is divided into rotor chamber (23) and motor room (24), being provided with impeller (10) in rotor chamber (23), is the sprue (41) of refrigeration agent between rotor chamber (23) and impeller (10); Rotor chamber (23) also offers the sidepiece and the suction port (81) of radial outside and exhaust port (82) that cover described impeller (10);
Motor (28) is provided with in motor room (24), motor (28) comprises stator (29) and rotor (30), and the live axle (31) be connected with rotor (30) is connected with impeller (10) through the axis hole be arranged on fragmenting plate (22);
Impeller (10) comprises plectane portion (12) and is arranged on multiple blades (11) of its outer rim, and blade (11) is uniform intervals arrangement in the sense of rotation of impeller (10); Runner between two adjacent blades (11) opens to the sidepiece runner of impeller (10) and radial outside runner;
When impeller (10) is rotated via live axle (31) driving by motor (28), the refrigerant fluid sucked from suction port (81) flows to the both sides of plectane portion (12) respectively, spiral motion is carried out respectively towards circumferential direction, by pressurized time each blade (11), discharge from exhaust port (82);
Described blade (11) comprises the first blade part (111) and the second blade part (112), and the first blade part (111) is symmetrical with the thickness of slab center line (122) of the outer circumferential face (121) in the second blade part (112) relative plectane portion;
First blade part (111), the second blade part (112) tilt towards sense of rotation relative to vertical surface respectively, and described vertical surface comprises thickness of slab center line (122) and divides plectane portion (12) equally;
Described first blade part (111) becomes V-shaped with the second blade part (112);
The bottom of blade (11) is connected with plectane portion (12) radial direction, the tip edge line of blade (11) is the curve on ring surface, the tip edge projection line of the internal surface (1112) of the first blade part (111) and center line (122) towards rotating square to angle be 60 °, the tip edge projection line of the internal surface (1122) of corresponding second blade part (112) and center line (122) towards rotating square to angle be 60 °; The tip edge projection line of the tip edge projection line of the outer surface (1111) of the first blade part (111) and the outer surface (1121) of the second blade part (112) is 120 ° along rotating reciprocal angle; Side margin line between the bottom of blade (11) and top is straight line.
2. refrigerated medium pump as claimed in claim 1, it is characterized in that, the cross section of fluid channel shape between the side of the blade (11) on described impeller (10) and housing (21) is semi-circular shape.
3. refrigerated medium pump as claimed in claim 2, it is characterized in that, first side (113) of the blade (11) on described impeller (10), the cross section of fluid channel shape between the second side (114) and housing (21) are semi-circular shape.
4. refrigerated medium pump as claimed in claim 1, it is characterized in that, be positioned at the outer surface (1111) of the first blade part (111), internal surface (1112), the outer surface (1121), the internal surface (1122) that are positioned at the second blade part (112) are curved surface, the degree of crook in the bending sideline of blade (11) annulus profile from bottom to top reduces gradually, and each side edge line of the first blade part (111) and the second blade part (112) is straight line.
5. refrigerated medium pump as claimed in claim 1, it is characterized in that, when impeller (10) rotates, after refrigerant fluid sucks from suction port (81), the refrigerant fluid be inhaled into contacts with the outer surface (1111) of the first blade part (111) and the outer surface (1121) of the second blade part (112); The outer surface (1111) of the refrigerant fluid be inhaled into along the first blade part (111) tilted towards sense of rotation and outer surface (1121) flowing of the second blade part (112).
6. refrigerated medium pump as claimed in claim 1, it is characterized in that, described plectane portion (12) and blade (11) are one of the forming.
7. based on the aircondition of claim 1 ~ 6 refrigerated medium pump described in any one, it is characterized in that, comprise heat source side refrigerant circuit and utilize side refrigerant circuit, the refrigeration agent in heat source side refrigerant circuit with utilize the refrigeration agent in the refrigerant circuit of side to carry out heat exchange in refrigeration agent-refrigerant heat exchanger (52);
The outdoor unit (50) of heat source side refrigerant circuit is connected with compressor, four-way switching valve, thermal source heat exchanger and expansion mechanism in turn via heat source side refrigerant piping (51);
Utilize side refrigerant circuit by utilize side refrigerant piping (61) to connect successively to utilize the reservoir vessel of side refrigeration agent (62), refrigerated medium pump (1) and be located at indoor play effect as vaporizer utilize side heat exchanger (63,64,65), enable to utilize side refrigeration agent to circulate;
Refrigerated medium pump (1) and refrigeration agent-refrigerant heat exchanger (52) are configured in basement.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210424548.XA CN103032338B (en) | 2012-10-30 | 2012-10-30 | Refrigerant pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210424548.XA CN103032338B (en) | 2012-10-30 | 2012-10-30 | Refrigerant pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103032338A CN103032338A (en) | 2013-04-10 |
| CN103032338B true CN103032338B (en) | 2015-05-27 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210424548.XA Expired - Fee Related CN103032338B (en) | 2012-10-30 | 2012-10-30 | Refrigerant pump |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113454339B (en) * | 2020-05-19 | 2023-02-03 | 华为数字能源技术有限公司 | Refrigerant pump and data center refrigerating system |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003161284A (en) * | 2001-11-27 | 2003-06-06 | Matsushita Electric Ind Co Ltd | Thin vortex pump and cooling system provided therewith |
| CN1683777A (en) * | 2004-04-13 | 2005-10-19 | 韩国汽车燃料***株式会社(Kafus) | Impeller for fuel pumps |
| CN200952477Y (en) * | 2006-09-21 | 2007-09-26 | 元山科技工业股份有限公司 | Micro-pump |
| CN101504010A (en) * | 2008-02-06 | 2009-08-12 | 株式会社Ihi | Inlet guide vane, turbo compressor, and refrigerator |
| CN102418711A (en) * | 2010-09-24 | 2012-04-18 | 谢夫勒科技有限两合公司 | Seal for a controllable coolant pump |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3964200B2 (en) * | 2001-12-26 | 2007-08-22 | 愛三工業株式会社 | Fuel pump |
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2012
- 2012-10-30 CN CN201210424548.XA patent/CN103032338B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003161284A (en) * | 2001-11-27 | 2003-06-06 | Matsushita Electric Ind Co Ltd | Thin vortex pump and cooling system provided therewith |
| CN1683777A (en) * | 2004-04-13 | 2005-10-19 | 韩国汽车燃料***株式会社(Kafus) | Impeller for fuel pumps |
| CN200952477Y (en) * | 2006-09-21 | 2007-09-26 | 元山科技工业股份有限公司 | Micro-pump |
| CN101504010A (en) * | 2008-02-06 | 2009-08-12 | 株式会社Ihi | Inlet guide vane, turbo compressor, and refrigerator |
| CN102418711A (en) * | 2010-09-24 | 2012-04-18 | 谢夫勒科技有限两合公司 | Seal for a controllable coolant pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103032338A (en) | 2013-04-10 |
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