CN203404133U - Cooling pump of machine tool - Google Patents
Cooling pump of machine tool Download PDFInfo
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- CN203404133U CN203404133U CN201320322848.7U CN201320322848U CN203404133U CN 203404133 U CN203404133 U CN 203404133U CN 201320322848 U CN201320322848 U CN 201320322848U CN 203404133 U CN203404133 U CN 203404133U
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Abstract
The utility model discloses a cooling pump of a machine tool. An impeller is a full-open spiral long-blade structure, the blade length is 1/6 to 1/4 of the outer diameter D2 of the impeller, an axial gap d1 between the impeller and a pump body is 0.1 mm to 0.3mm, annular bulges are arranged on a pump cover and used for adjusting an axial gap d2 between the pump cover and the impeller to be 0.1 mm to 0.3mm, a water inlet is formed in the pump body and takes a cut-water position A on the pump cover as a starting point circumferentially, and a radial position of the water inlet corresponds to a blade area of the impeller. According to the cooling pump of the machine tool, the new spiral impeller is strictly matched with the pump cover and an end face of the pump body, and the matched gaps between the impeller and the pump body and between the impeller and the pump cover are guaranteed so that the small-flow and high-lift cooling liquid conveying requirement is met and the efficiency is improved; a distance from the water inlet to the bottom of a cooling liquid box can be shortened with the increasing of a lift; the utilization rate of cooling liquid is increased; the specification requirements of high efficiency, small flow and high lift are met; and the cooling pump can be widely applied to the cooling of the machine tool.
Description
Technical field
The utility model belongs to coolant pump field, is specifically related to a kind of machine tool cooling pump technology that high efficiency high lift is carried that has.
Background technique
Machine tool cooling pump is installed on set cooling liquid casing top mostly, mainly pump cover 1, the pump housing 3, pump shaft 4, consists of, and impeller 2 is arranged in pump cover 1, coaxial with pump cover and the pump housing, and it is cooling that driven by motor vane rotary carries cooling liquid to be that machined part carries out.Its pump head part, as shown in Figure 1, is mainly comprised of pump cover 1, impeller 2, the pump housing 3 and pump shaft 4, immerses in cooling liquid, and its maximum radial dimension is subject to casing top circular hole size restrictions, to guarantee to install after coolant pump the impurity such as iron filings, does not enter casing.
Along with machine spindle speed significantly improves, the lift of machine tool cooling pump is required more and more higher, need to strengthen the pressure of cooling liquid, to guarantee the cooling effect to processing accessories, improve the machining accuracy of processed piece, protect cutter not to be burned simultaneously.Machine tool cooling pump is arranged on cooling liquid casing top, in casing, the general assembly length of pump is also subject to the restriction of pumping head, and pump head cooling liquid water intake directly has influence on the utilization ratio of cooling liquid to the degree of depth of bottom half, more little circulation and the renewal that is more conducive to cooling liquid of this distance.
Meanwhile, the required flow of machine tool cooling pump is conventionally less, and the conveying of small flow, high-lift cooling liquid belongs to typical low specific speed centrifugal pump category.Low specific speed centrifugal pump design theory is carried out single-stage Impeller Design routinely, can realize the obvious lifting of lift, but match power is large, efficiency is on the low side; Though as adopt multi-stage impeller design to raise the efficiency, need to increase water-guiding element, make whole pump structure complicated; Peripheral pump theoretically can be for the conveying of small flow, high-lift occasion, and there are relatively high efficiency and good suction capacity, but there is no in the market vortex type impeller for the report of machine tool cooling pump, because traditional peripheral pump is to radially all having comparatively strict requirement with axial clearance, machining accuracy and cost are higher, and have larger installation and maintenance difficulty.
Through retrieval, the patent relevant to a kind of machine tool cooling pump has as follows: machine tool cooling pump, and application number: 201210444813.0, be a kind of conventional machine tool cooling pump, main feature is to be furnished with cooling devcie of motor, can extend the working life of machine tool cooling pump.Middle lift machine tool cooling pump, application number: 201120311771.4, be a kind of conventional closed centrifugal blade wheel structure that adopts, on the pump housing, offer the machine tool cooling pump of guiding gutter, can make the lift of coolant pump obtain a little lifting.
Machine tool cooling pump of the prior art, impeller is mainly semi-open centrifugal impeller, be that impeller inlet side is open, the pump housing adopts annular or the design of spirality overflow section conventionally, between impeller blade and the pump housing, there is larger axis to cavity, when this just causes pump operation, high-pressure liquid dallies and has larger eddy loss in cavity, thus this type of lift of pump and efficiency all lower.
Summary of the invention
The utility model provides a kind of machine tool cooling pump, to improve single-stage lift and the efficiency of machine tool cooling pump.
In order to solve above technical problem, the technological scheme that the utility model adopts is as follows:
, mainly by pump cover (1), impeller (2), the pump housing (3), pump shaft (4), formed, coaxially arrange successively from below to up; Pump cover (1) and the pump housing (3) are affixed; Impeller (2) is positioned between pump cover (1) and the pump housing (3), and and pump cover (1) and the pump housing (3) between leave respectively axial clearance; Impeller (2) is affixed with pump shaft (4), and can circumferentially rotate relative to pump cover (1) and the pump housing (3) edge; The upper corresponding impeller width b2 of pump cover (1) position is provided with radially flow channels C; On the pump housing (3), offer water intake (5) and osculum (6), communicate with described flow channels; The entrance of described osculum (6), it circumferentially take the upper position B of throat of pump cover (1) is stop, its radial position is within pump cover (1) and the pump housing (3) maximum radial gap; Pump shaft (4) runs through impeller (2) and the pump housing (3), leaves axial clearance with pump cover (1); It is characterized in that: impeller (2) is standard-sized sheet vortex type linear leaf structure, the impeller outer diameter length that length of blade equals 1/6 ~ 1/4; Axial clearance between impeller (2) and the pump housing (3)
d1 is 0.1mm ~ 0.3mm; Pump cover (1) is provided with annular protrusion (8) and recessed flow channels D, for regulating axial clearance between pump cover (1) and impeller (2)
d2 to 0.1mm ~ 0.3mm; The water intake (5) of offering on the pump housing (3), it circumferentially take the upper cut water position A of pump cover (1) is starting point, its radial position is corresponding to the leaf area of impeller.
The working surface PP of described blade is plane, and the cross section of described blade is any in trapezoidal, triangle or semicircular structure.
At described flow channels C, be that sectional shape is radially flow channels of rectangle or trapezoidal spirality.
In described flow channels D cross section, be rectangle or semicircle.
Any during being shaped as of described water intake is fan-shaped, circular, square.
The utlity model has beneficial effect.The utility model by the pump housing and pump cover structure design improvement, utilizes Novel swirl impeller and pump cover and strict the coordinating of pump body end surface, guarantees the matching gap with impeller, thereby guarantees small flow, high-lift cooling liquid conveying requirement, and raising efficiency; By reducing cooling liquid water intake 5 to the axial dimension of bottom half, improve the utilization ratio of cooling liquid, thereby realize efficient, small flow, high-lift characteristic requirements; Can utilize single-stage impeller to realize desired small flow, high-lift conveying, compact structure is simple, and processing technology more easily realizes, and necessary electromotor power is less; And gas-entrained in processable liquid is there is no timely repairing in tank for coolant, also can of short duration work while comprising even in some cases the occasion of solid particle or abrasive dust, there is wide market prospects and promotional value.
Accompanying drawing explanation
Fig. 1 is the utility model machine tool cooling pump pump head part-structure schematic diagram.
In figure: 1. pump cover, 2. impeller, the 3. pump housing, 4. pump shaft, 5. water intake, 6. water outlet, 8. annular protrusion,
d1 is impeller and pump housing axial clearance size,
d2 is impeller and pump cover axial clearance size, and C is the radially flow channels of corresponding impeller width on pump cover, and D is the overcurrent runner that pump cover is recessed on part.
Fig. 2 is the utility model impeller 2 axis plane projection schematic diagram.
Fig. 3 is the utility model impeller 2 plane projection schematic diagram.
Fig. 4 is main the Hydraulic Design parameter.
Fig. 5 is the utility model pump cover 1 axis plane projection schematic diagram.
Fig. 6 is the utility model pump cover 1 plane projection schematic diagram.
Fig. 7 is the utility model pump housing 3 plane generalized sections.
B position is spiral flow channel throat position, corresponding impeller and pump cover maximum radial dimension;
θfor cut water cornerite, it is also angle between A, two positions of B.
Fig. 8 is the utility model pump housing 3 axial plane generalized sections.
Fig. 9 is the utility model machine tool cooling pump embodiment 2 structural representations, and wherein impeller cross section is trapezoidal, and overcurrent runner D is annular.
In figure: 1. pump cover, 2. impeller, 3. the pump housing, 4. pump shaft, 5. water intake, 6. water outlet, 8. annular protrusion, d1 is impeller and pump housing axial clearance size, d2 is impeller and pump cover axial clearance size, C is the radially flow channels of corresponding impeller width on pump cover, and D is the overcurrent runner that pump cover is recessed on part; D2 is impeller outer diameter, and b is width of blade; PP is front side of vane; D is unshrouded impeller center of gravity diameter, and b is width of blade, and c is runner D axial width, and h is runner D radial width, and y is the empty cutter of impeller end face place closure size, and d1 and d2 are respectively the axial clearance of impeller and the pump housing and pump cover; A position is spiral flow channel cut water position, corresponding impeller and pump cover smallest radial size; B position is spiral flow channel throat position, corresponding impeller and pump cover maximum radial dimension; θ is cut water cornerite, is also angle between A, two positions of B.
Embodiment
Below in conjunction with accompanying drawing, the utility model is further described.
The design parameter of following examples is: rated flow
q: 0.65 m
3/ h; Rated head
h: 19 m; The most high-lift 25m; Rotating speed
n=2900 r/min; Maximum match power
: 300W; The maximum radial dimension 110mm that allows of fuel tank.
embodiment one
As shown in Fig. 1 the utility model machine tool cooling pump pump head part-structure schematic diagram, the utility model is mainly comprised of pump cover 1, impeller 2, the pump housing 3, pump shaft 4, coaxially arranges successively from below to up; Pump cover 1 and the pump housing 3 are affixed by Cock screw; Impeller 2 between pump cover 1 and the pump housing 3, and and pump cover 1 and the pump housing 3 between leave respectively axial clearance
d1=0.1mm and
d2=0.1mm; Impeller 2 is affixed with pump shaft 4, and circumferentially rotates relative to pump cover 1 and the pump housing 3 edges; Corresponding impeller width on pump cover 1
bposition is provided with radially flow channels C, and is provided with annular protrusion 8 and recessed flow channels D; On the pump housing 3, offer water intake 5 and osculum 6, communicate with described flow channels C and D; Pump shaft 4 runs through impeller 2 and the pump housing 3, leaves axial clearance with pump cover 1.
Fig. 2 is the utility model impeller 2 axis plane projection schematic diagram, considers the application of machine tool cooling pump, in medium, unavoidably have a small amount of impurity and exist, thereby impeller 2 employing full-open type vortex linear leaf structures, blade profile is triangle; Fig. 3 is the utility model impeller 2 plane projection schematic diagram, and the working surface PP of blade is plane;
Fig. 4 is main the Hydraulic Design parameter schematic diagram, opposite opened impeller, rectangular cross-section flow channels D:
(1) width of blade
bby formula (1), calculate:
In formula
kfor width of blade coefficient, rectangularl runner unshrouded impeller
k=0.36; Get
b=5mm.
(2) by following relationship, calculate:
b/
c=1.07,
h=2
c,
So:
c=1.07
b=5.4 mm, get
c=6mm;
h=2
c=12 mm.
(3) the design is in order to realize the larger lifting of lift, different from conventional peripheral pump blade design, gets
e=
h=12mm
(4)
dfor unshrouded impeller runner center of gravity diameter, by formula (2) estimation, in formula
Ψfor head coefficient, to should design parameter
Ψ=4.6.
Get
d=75 mm.
(5) impeller outer diameter
d2=
d+ 1.5
h=0.075+0.018=0.093 m, gets
d2=96 mm; Can meet overall structure maximum radial dimension and be not more than 110mm requirement; Now length of blade is about
h+
e=24 mm are impeller outer diameter
d2 1/4.
(6) selection of the number of blade
Generally
z=24 ~ 60.Along with the increase of the number of blade, lift increases significantly, but impeller diameter and accuracy of manufacturing etc. are considered in also increase thereupon of power simultaneously, and this example is got
z=24.
(7) the empty cutter of impeller end face place closure size
ydetermine
For the occasion of carrying small flow, end face easily grinds, and requires this value can not be too large in structure, and this example is got
y=3mm.
Fig. 5 is the utility model pump cover 1 axial plane schematic diagram, and the sectional shape of overcurrent runner C is rectangle, and pump cover 1 is provided with annular protrusion 8 and recessed flow channels D, for regulating axial clearance between pump cover 1 and impeller 2
d2 to 0.1mm; Fig. 6 is the utility model pump cover 1 floor map, and A is spirality overcurrent runner C cut water position, corresponding impeller and pump cover smallest radial size; B is spirality overcurrent runner C throat position, corresponding impeller and pump cover maximum radial dimension,
θfor cut water cornerite, be also angle between A, two positions of B, the width of cut water is greater than the spacing of two blades, and this example is got
θ=60 degree, to guarantee effectively to separate outlet zone of high pressure and import low pressure area; In this example, recessed flow channels D is corresponding with runner C, by spiral flow channel, extends axially
cthe distance of=6mm.
Fig. 7 is the utility model pump housing 3 plane generalized sections, offers water intake 5 and osculum 6 on it, communicates with described flow channels C and D; Described water intake 5, it circumferentially take cut water position B on pump cover 1 is starting point, and its radial position is corresponding to the leaf area of impeller, and import adopts fan-shaped import, meets nominal inlet diameter
d, during for the one-sided runner of unshrouded impeller, nominal inlet diameter; Fig. 8 is the utility model pump housing 3 axial plane generalized sections, the entrance of described osculum 6, and it circumferentially take the position B of throat on pump cover 1 is stop, its radial position is within pump cover 1 and the pump housing 3 maximum radial gaps.
Embodiment two
Machine tool cooling pump in this embodiment is coaxially arranged from below to up successively by pump cover 1, impeller 2, the pump housing 3 and pump shaft 4 equally; Pump cover 1 and the pump housing 3 are affixed; Impeller 2 between pump cover 1 and the pump housing 3, and and pump cover 1 and the pump housing 3 between leave respectively axial clearance and be
d1=0.3mm and
d2=0.3mm; Impeller 2 is affixed with pump shaft 4, and circumferentially rotates relative to pump cover 1 and the pump housing 3 edges; Corresponding impeller width on pump cover 1
bposition is provided with radially flow channels C, and is provided with annular protrusion 8 and recessed flow channels D; On the pump housing 3, offer water intake 5 and osculum 6, communicate with described flow channels C and D; Pump shaft 4 runs through impeller 2 and the pump housing 3, leaves axial clearance with pump cover 1.
Fig. 2 is the utility model impeller 2 axis plane projection schematic diagram, considers the application of machine tool cooling pump, in medium, unavoidably have a small amount of impurity and exist, thereby impeller 2 employing full-open type vortex linear leaf structures, blade profile is trapezoidal; Fig. 3 is impeller 2 plane projection schematic diagram of the present invention, and the working surface PP of blade is plane.
Fig. 4 is main the Hydraulic Design parameter schematic diagram, opposite opened impeller, rectangular cross-section flow channels D:
(1) width of blade
bby formula (1), calculate:
In formula
kfor width of blade coefficient, rectangularl runner unshrouded impeller
k=0.36; Get
b=5 mm.
(2) by following relationship, calculate:
b/
c=1.07,
h=2
c,
So:
c=1.07
b=5.4 mm, get c=5mm;
h=2
c=10 mm;
(3) the design is in order to realize the larger lifting of lift, different from conventional peripheral pump blade design, gets
e=
h=10mm
(4) D is unshrouded impeller runner center of gravity diameter, by formula (2), calculate,
Ψfor head coefficient, to should design parameter
Ψ=4.6.
Get
d=75mm.
(5) impeller outer diameter
d2=
d+ 1.5
h=0.075+0.018=0.093 m gets
d2=100 mm; Can meet overall structure maximum radial dimension and be not more than 110mm requirement, now length of blade is about
h+
e=20mm is impeller outer diameter
d2 1/5.
(6) selection of the number of blade
Generally
z=24 ~ 60.Along with the increase of the number of blade, lift increases significantly, but impeller diameter and accuracy of manufacturing etc. are considered in also increase thereupon of power simultaneously, and this example is got
z=24.
(7) the empty cutter of impeller end face place closure size
ydetermine
For the occasion of carrying small flow, end face easily grinds, and requires this value can not be too large in structure, and this example is got y=3mm.
Fig. 5 is the utility model pump cover 1 axial plane schematic diagram, and the sectional shape of overcurrent runner C is trapezoidal, and pump cover 1 is provided with annular protrusion 8 and recessed flow channels D, for regulating axial clearance between pump cover 1 and impeller 2
d2 to 0.3mm; Fig. 6 is pump cover 1 floor map of the present invention, and A is spirality overcurrent runner C cut water position, corresponding impeller and pump cover smallest radial size; B is spirality overcurrent runner C throat position, corresponding impeller and pump cover maximum radial dimension;
θfor cut water cornerite, be also angle between A, two positions of B, the width of cut water is greater than the spacing of two blades, and this example is got
θ=60 degree, to guarantee effectively to separate outlet zone of high pressure and import low pressure area; In this example, recessed flow channels D and runner C throat position radial dimension, extend axially size by ring runner
cthe distance of=5mm, its schematic diagram as shown in Figure 9.
Fig. 7 is the utility model pump housing 3 plane generalized sections, offers water intake 5 and osculum 6 on it, communicates with described flow channels C and D; Described water intake 5, it circumferentially take cut water position A on pump cover 1 is starting point, and its radial position is corresponding to the leaf area of impeller, and import adopts circular import, meets nominal inlet diameter
d, during for the one-sided runner of unshrouded impeller, nominal inlet diameter; Fig. 8 is the pump housing 3 axial plane generalized sections of the present invention, the entrance of described osculum 6, and it circumferentially take the position B of throat on pump cover 1 is stop, its radial position is within pump cover 1 and the pump housing 3 maximum radial gaps.
Embodiment three
Machine tool cooling pump in the present embodiment is coaxially arranged from below to up successively by pump cover 1, impeller 2, the pump housing 3 and pump shaft 4; Pump cover 1 and the pump housing 3 are affixed; Impeller 2 between pump cover 1 and the pump housing 3, and and pump cover 1 and the pump housing 3 between leave respectively axial clearance
d1=0.2mm and
d2=0.2mm; Impeller 2 is affixed with pump shaft 4, and circumferentially rotates relative to pump cover 1 and the pump housing 3 edges; Corresponding impeller width on pump cover 1
bposition is provided with radially flow channels C, and is provided with annular protrusion 8 and recessed flow channels D; On the pump housing 3, offer water intake 5 and osculum 6, communicate with described flow channels C and D; Pump shaft 4 runs through impeller 2 and the pump housing 3, leaves axial clearance with pump cover 1.
Fig. 2 is the utility model impeller 2 axis plane projection schematic diagram, considers the application of machine tool cooling pump, in medium, unavoidably have a small amount of impurity and exist, thereby impeller 2 employing full-open type vortex linear leaf structures, blade profile is semicircle; Fig. 3 is impeller 2 plane projection schematic diagram of the present invention, and the working surface PP of blade is plane.
Fig. 4 is main the Hydraulic Design parameter schematic diagram, opposite opened impeller, circular cross-section flow channels D:
(1) width of blade
bby formula (1), calculate:
In formula
kfor width of blade coefficient, circular cross-section flow channels unshrouded impeller
k=0.3, get
b=4.5 mm.
(2) by following relationship, calculate:
c=
b=4.5 mm;
h=2
b=9 mm;
(3) the design is in order to realize the larger lifting of lift, different from conventional peripheral pump blade design, gets
e=0.67
h=6 mm
(4)
dfor unshrouded impeller runner center of gravity diameter, by formula (2), calculate,
Ψfor head coefficient, to should design parameter
Ψ=4.6.
Get
d=75mm.
(5) impeller outer diameter
d2=
d+ 1.5
h=0.075+0.018=0.088 m gets
d2=90 mm; Can meet overall structure maximum radial dimension and be not more than 110mm requirement, now length of blade is about
h+
e=15mm is impeller outer diameter
d2 1/6.
(6) selection of the number of blade
Generally
z=24 ~ 60.Along with the increase of the number of blade, lift increases significantly, but impeller diameter and accuracy of manufacturing etc. are considered in also increase thereupon of power simultaneously, and this example is got
z=24.
(7) the empty cutter of impeller end face place closure size
ydetermine
For the occasion of carrying small flow, end face easily grinds, and requires this value can not be too large in structure, and this example is got
y=3mm.
Fig. 5 is the utility model pump cover 1 axial plane schematic diagram, and the sectional shape of overcurrent runner C is plow-shape, and pump cover 1 is provided with annular protrusion 8 and recessed flow channels D, for regulating axial clearance between pump cover 1 and impeller 2
d2 to 0.2mm; Fig. 6 is pump cover 1 floor map of the present invention, and A is spirality overcurrent runner C cut water position, corresponding impeller and pump cover smallest radial size; B is spirality overcurrent runner C throat position, corresponding impeller and pump cover maximum radial dimension;
θfor cut water cornerite, be also angle between A, two positions of B, the width of cut water is greater than the spacing of two blades, and this example is got
θ=60 degree, to guarantee effectively to separate outlet zone of high pressure and import low pressure area; In this example, recessed flow channels D and runner C throat position radial dimension, extend axially by spiral flow channel
cthe distance of=4.5mm.
Fig. 7 is the utility model pump housing 3 plane generalized sections, offers water intake 5 and osculum 6 on it, communicates with described flow channels C and D; Described water intake 5, it circumferentially take cut water position A on pump cover 1 is starting point, and its radial position is corresponding to the leaf area of impeller, and import adopts square import, meets nominal inlet diameter
d, during for the one-sided runner of unshrouded impeller, nominal inlet diameter; Fig. 8 is the utility model pump housing 3 axial plane generalized sections, the entrance of described osculum 6, and it circumferentially take the position B of throat on pump cover 1 is stop, its radial position is within pump cover 1 and the pump housing 3 maximum radial gaps.
Working procedure of the present utility model is as follows: this pump is placed in cooler bin, and pump head immerses cooling liquid certain depth.Motor rotarily drives pump shaft 4 and rotates, pump shaft 4 impeller 2 are circumferentially rotated relative to pump cover 1 and the pump housing 3 edges, and form negative pressure at water intake 5 places, liquid is from entering between blade in the flow channels C and D of pump cover 1 and the pump housing 3 compositions, under impeller blade turning effort, make the liquid in impeller and in runner produce circular movement, in impeller, the peripheral velocity of liquid is greater than the peripheral velocity in runner C and D, will form the annularly flow from impeller to the similar vortex of runner; Liquid relies on this vortex motion, every through a blade acquisition primary energy, rotation along with impeller, when impeller rotates to the B of throat position from cut water A, under the interval action of cut water, highly pressurised liquid flows into osculum (6) with higher pressure and speed, along pipeline, introduces and needs cooling machine tool and the part place of processing.
Claims (5)
1. a machine tool cooling pump, pump cover (1), impeller (2), the pump housing (3) and pump shaft (4) coaxially arrange from below to up successively; Pump cover (1) and the pump housing (3) are affixed; Impeller (2) is positioned between pump cover (1) and the pump housing (3), and and pump cover (1) and the pump housing (3) between leave respectively axial clearance; Impeller (2) is affixed with pump shaft (4), and circumferentially rotates relative to pump cover (1) and the pump housing (3) edge; The upper corresponding impeller width b2 of pump cover (1) position is provided with radially flow channels C; On the pump housing (3), offer water intake (5) and osculum (6) communicates with described flow channels C; The entrance of described osculum (6), it circumferentially take the upper position B of throat of pump cover (1) is stop, its radial position is within pump cover (1) and the pump housing (3) maximum radial gap; Pump shaft (4) runs through impeller (2) and the pump housing (3), leaves axial clearance with pump cover (1); It is characterized in that: impeller (2) is standard-sized sheet vortex type linear leaf structure, the impeller outer diameter length that length of blade equals 1/6 ~ 1/4; Axial clearance between impeller (2) and the pump housing (3)
d1 is 0.1mm ~ 0.3mm; Pump cover (1) is provided with annular protrusion (8) and recessed flow channels D, for regulating axial clearance between pump cover (1) and impeller (2)
d2 to 0.1mm ~ 0.3mm; The water intake (5) of offering on the pump housing (3), it circumferentially take the upper cut water position A of pump cover (1) is starting point, its radial position is corresponding to the vane region of impeller.
2. a machine tool cooling pump as claimed in claim 1, is characterized in that: the working surface PP of described blade is plane, and the cross section of described blade is any in trapezoidal, triangle or semicircular structure.
3. a machine tool cooling pump as claimed in claim 1, is characterized in that: described flow channels C is that sectional shape is radially flow channels of rectangle or trapezoidal spirality.
4. a machine tool cooling pump as claimed in claim 1, is characterized in that: described flow channels D cross section is rectangle or semicircle.
5. a machine tool cooling pump as claimed in claim 1, is characterized in that: any during being shaped as of described water intake is fan-shaped, circular, square.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320322848.7U CN203404133U (en) | 2013-06-06 | 2013-06-06 | Cooling pump of machine tool |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320322848.7U CN203404133U (en) | 2013-06-06 | 2013-06-06 | Cooling pump of machine tool |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203404133U true CN203404133U (en) | 2014-01-22 |
Family
ID=49940071
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320322848.7U Withdrawn - After Issue CN203404133U (en) | 2013-06-06 | 2013-06-06 | Cooling pump of machine tool |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203404133U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103256256A (en) * | 2013-06-06 | 2013-08-21 | 江苏大学 | Cooling pump of machine tool |
| CN107355391A (en) * | 2017-08-15 | 2017-11-17 | 淳安千岛湖节能机电厂 | A kind of machine tool cooling pump |
-
2013
- 2013-06-06 CN CN201320322848.7U patent/CN203404133U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103256256A (en) * | 2013-06-06 | 2013-08-21 | 江苏大学 | Cooling pump of machine tool |
| CN107355391A (en) * | 2017-08-15 | 2017-11-17 | 淳安千岛湖节能机电厂 | A kind of machine tool cooling pump |
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