Cooling system and machining device

Abstract

The present invention relates to a cooling system comprising a spray unit for spraying a coolant. The present invention further relates to a machining device which comprises a cooling system of this type. The spray unit comprises a flow guide which is coupled on one side to a chamber and is coupled on the other side to one or more channels, where the chamber, the flow guide and the plurality of channels form a closed system for spraying from the channels pressurized coolant fed to the chamber, where the flow guide, the plurality of elongated channels and the chamber are manufactured as an integral part.

Claims

1. A cooling system for spraying a coolant on a work piece to be cooled, comprising: a reservoir for the coolant; a spray unit; a pump for pumping coolant from the reservoir to the spray unit; the spray unit comprising: a chamber which has an inlet for coupling the spray unit to a pipe for the coolant coming from the reservoir, as well as an outlet; at least a single elongated channel having an inlet and an outlet; a flow guide whose one end is attached to the chamber at the outlet and whose other end is attached to the channel at the inlet, which flow guide comprises a cavity that widens starting from a coupling between the channel and the flow guide toward the chamber over a non-zero length in a direction perpendicular to a longitudinal direction of the channel, wherein an inside of the flow guide is provided with a spiral-shaped rib or groove extending in the longitudinal direction of the channel.

2. A cooling system as claimed in claim 1, wherein the inside of the flow guide has the shape of a tuba or rope tornado.

3. A cooling system as claimed in claim 1, wherein the spiral shape of the groove is such that with a spiral shape projected on a planar surface the length of a part of the spiral that extends through a 90 degree angle is approximately 1.6 times the length of a following more narrowed part of the spiral that extends through a following 90 degree angle.

4. A cooling system as claimed in claim 1, wherein the channel is straight extending over part of the length from the outlet onward and has a constant cross section over this part.

5. A cooling system as claimed in claim 1, wherein the chamber, the flow guide and the channel are manufactured as an integral part and form a unit for spraying from the channel pressurized coolant fed to the chamber.

6. A cooling system as claimed in claim 1, wherein the spray unit comprises a multiplicity of elongated channels arranged in parallel and spaced apart from each other, which said channel forms part of.

7. A cooling system as claimed in claim 6, wherein said widening of the cavities is preferably continued at least to a point where cavities of adjacent channels are touching each other.

8. A cooling system as claimed in claim 7, wherein the cavities show a substantially constant cross-sectional shape seen in longitudinal direction starting from the coupling between the channels and the flow guide and ending at the point where cavities of adjacent channels are touching each other, where the size of the cross-sectional shape is increased from the coupling to the chamber onward.

9. A cooling system as claimed in claim 8, wherein the points where cavities of adjacent channels are touching each other are identical for each pair of adjacent channels.

10. A cooling system as claimed in claim 8 wherein the flow guide comprises a body that is tapering in a direction toward the channels, where the cavities are formed in the body and where the widening of the cavities is continued to beyond the point where cavities of adjacent channels are touching each other, beyond which point the cross-sectional shape of the cavities is not constant but is also determined by the body.

11. A grinding device, comprising a work piece, a tool and a cooling system, wherein the cooling system is a cooling system as claimed in claim 1, where the outlet of the channel is pointed to a contact zone between the work piece and the tool.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The invention will be described in more detail hereinafter while reference is made to the appended drawing figures, in which:

(2) FIGS. 1A and 1B show diagrammatic views of an embodiment of a spray unit of the cooling system according to the invention;

(3) FIG. 2 shows a partly exploded cross-sectional view of the spray unit shown in FIG. 1;

(4) FIGS. 3A and 3B show further sectional views of the spray unit shown in FIG. 1;

(5) FIG. 4 shows an embodiment of the cooling system according to the invention in which the spray unit shown in FIG. 1 may be utilized;

(6) FIG. 5 shows a general structure of a coolant flow;

(7) FIG. 6 shows in a three-dimensional view the course of spiral-shaped grooves in a spray unit of a further embodiment of the cooling system; and

(8) FIG. 7 shows the course of the spiral-shaped grooves shown in FIG. 6 projected on a planar surface.

DETAILED DESCRIPTION OF THE DRAWINGS

(9) While reference is made to FIGS. 1A and 1B, a spray unit 1 according to the invention comprises a chamber 2, a flow guide 3 and a multiplicity of adjacent channels 4 which in this case are formed by in essence hollow tubes. At the end of the channels 4 a reinforcement 5 is provided as a result of which channels 4 are secured better.

(10) On the inside of chamber 2 a thread 6 is visible by means of which spray unit 1 can be connected to a coolant pipe. However, the invention is not restricted to the use of thread; other coupling means may also be utilized.

(11) FIG. 1A shows cavities 7 which change into openings 8 of channels 4. Furthermore, a start of a spiral-shaped rib or ridge 9 is visible, which is shown in more detail in FIG. 2.

(12) As is apparant from FIG. 1A, FIG. 2 and the cross-sectional views of FIGS. 3A and 3B, the cavities 7 are widened from the coupling onward between flow guide 3 and channels 4, indicated in FIG. 3A by “A” up to point “B” where adjacent cavities are touching each other. Between points “A” and “B” cavities 7 have a constant circular cross section. Beyond point “B” the cross section changes because the shape is then also determined by body 3′ of flow guide 3. The body 3′ is then tapered in the direction of channels 4.

(13) The result of this is a highly advantageous transition between chamber 2 and channels 4, positively affecting the transition point between laminar flow and turbulent flow and the related atomization point of the coolant leaving the spray unit.

(14) The spray unit shown in FIGS. 1-3 is an integral part manufactured from a single material or a single combination of materials. In consequence, the transitions between the various parts are smooth and thus the above transition point may be further positively affected.

(15) In an example of embodiment of spray unit 1 chamber 2 has an inside diameter of between 12 and 16 mm, the length over which the cavities extend is situated between 2 and 5 times the inside diameter of the channels and the channels have an inside diameter between 0.1 and 2 mm. The number of channels to be used is generally determined by the width of the grinding disc. Depending on the inside diameter of the channels, more or fewer channels may be situated beside one another for realizing a coolant flow that can cover the whole width of the grinding disc.

(16) The cooling system shown in FIG. 4 comprises a coolant reservoir 20 which is connected to a pump 30 by means of a pipe 25. Through a pipe 35 pump 30 carries the liquid coolant from coolant reservoir 20 to spray unit 1.

(17) Spray unit 1 then squirts the coolant to a contact zone situated between a grinding disc 40 and a work piece 50 to be ground. By way of example grinding disc 40 rotates in the direction of rotation indicated by arrow 41.

(18) FIG. 4 diagrammatically shows a point “C” where atomization of the coolant takes place. Atomization provides a larger cooling effect since the many droplets in the mist have a larger cooling capacity for absorbing heat than a compact laminar flow of coolant. Furthermore, the many droplets are better capable of penetrating the contact zone.

(19) FIG. 5 shows a general structure of a coolant flow. The flow comprises a first part 101 in which there is a laminar flow, a second part 102 in which there is a turbulent flow and a third part 103 in which atomization takes place. In FIG. 5 point “C” indicates a separation between parts 102, 103 while point “D” indicates a separation between parts 101 and 102. In this context it is observed that in practice transitions cannot be defined in as definable a manner as suggested by FIG. 5. FIG. 5 further shows that the outside boundaries of the flow are increased in downstream direction. For example, the outside dimension of the flow when leaving the channels is 2 mm as indicated by arrow 104, whereas this dimension is 4 mm at the end of the mist indicated by arrow 105 and insofar it can be defined. The increase of the outside boundaries of the flow is effected in both directions perpendicular to the longitudinal direction of the channels.

(20) The shape of the coolant flow provides that lower coolant velocities than customary so far are needed. The coolant velocities are, for example, less than or equal to 50% of the peripheral velocity of the grinding disc, which velocities are sufficient for the coolant to reach the contact zone as a result of the form of this flow.

(21) From FIG. 4 is clear that if point “C” is closer to the outlet of spray unit 1, spray unit 1 is to be installed closer to grinding disc 90 and work piece 50 as a result of which spray unit 1 may touch work piece 50 when the work piece is rotated during grinding. This is also due to the fact that the atomization point must not be too far away from work piece 50 since the velocity of the coolant after atomization decreases very rapidly. If the coolant velocity is too low, the coolant will not be able to reach the contact zone owing to of the air flow and/or over-pressure caused by the grinding disc 40.

(22) The channels in the pipes and/or the cavities may be provided with a spiral-shaped groove having a Phi ratio (Golden ratio) spiral, where the end of the pipe is a straight opening whose length may vary and may be provided with a spiral without a Phi ratio. FIGS. 6 and 7 show the course of the spiral shape of a groove 60 having a Phi ratio. FIG. 6 gives a three-dimensional view of the course of the grooves 60 and FIG. 7 gives a diagrammatic view of the course of the grooves 60 as a projection on a planar surface. The length of a part L.sub.i of the spiral which extends through a 90 degree angle is here approximately 1.6 times the length L.sub.i+1 of a following more narrowed part of the spiral which extends through a following 90 degree angle. FIG. 6 also distinctly shows the tuba shape (or shape of a (rope) tornado) of the inside wall of the flow guide.

(23) The inner layers of water in an eddy have a much higher velocity than the outer layers. In a vortex the velocity times the jet is constant. As a result of the vortex the droplets of water are stretched and the water molecules become independent of each other thus increasing the capacity to absorb heat. These smaller water drops may penetrate in a simpler manner the air flow surrounding the grinding disc

(24) Albeit the invention has been described in the foregoing based on the drawings, it should be observed that the invention is not by any manner or means restricted to the embodiments shown in the drawings. The invention also extends to all embodiments deviating from the embodiment shown in the drawings within the framework defined by the claims.