GAS LASER OSCILLATOR

Abstract: The turboblower for lasers, consists of a shaft (17) to which turbo-vanes (16) are fixed at its one end, a pair of bearings (22, 23) supporting the shaft and a motor composed of a rotor (19) and a stator (20). Squeezed film dampers (36, 37) are provided around these bearings (22, 23). The vibration of the squeezed film damper bearings are prevented by a braking force caused by the non-elastic effect of the grease on the bearings. The damping coefficients of these squeezed film dampers are made different from each other.

Description: The present invention relates to a high-power gas laser oscillator device such as a machining CO₂ laser or the like, and more particularly, to improved turbo blower for use in a laser. Figure 3 shows an arrangement of a conventional CO₂ laser which includes an electric discharge tube 1 having an output coupling mirror 2 and a total reflection mirror 3 that are positioned at opposite ends of the electric discharge tube 1. Two metal electrodes 4 and 5 are arranged on the outer circumference of the electric discharge tube 1, and when a high-frequency voltage is applied between the metal electrodes 4 and 5 from a high-frequency power supply 6, a high-frequency glow discharge is produced in the electric discharge tube 1 for laser excitation. A laser beam axis in the electric discharge tube 1 is indicated at 13, and a laser beam axis extending out of the tube 1 from the output coupling mirror 2 is indicated at 14. To start the laser oscillator device, a gas in the device is first evacuated by a vacuum pump 12, and then a valve 11 is opened to introduce a predetermined amount of laser gas from a gas container 10 into the device until the pressure of the gas in the device reaches a prescribed pressure level. Subsequently, the device is continuously evacuated by the vacuum pump 12 and continuously replenished with the laser gas through the valve 11. The laser gas in the device is therefore continuously replaced with a fresh gas while the gas pressure in the device is kept at the prescribed pressure level, and accordingly, contamination of the laser gas in the device is prevented. In Fig. 3, the laser gas is circulated in the device by a Roots blower 9, whereby the laser gas is cooled. In a CO₂ laser, about 20% of the applied electric energy is converted into a laser beam and the rest is consumed to heat the laser gas, but theoretically, since the gain of laser oscillation is proportional to the minus (3/2)th power of the absolute temperature T, it is necessary to forcibly cool the laser gas to increase the oscillation efficiency. In the illustrated device, the laser gas flows through the electric discharge tube 1 in the direction indicated by the arrows at a speed of about 100 m/sec., and is introduced into a cooling unit 8. The cooling unit 8 removes most of the heat energy produced by the electric discharge from the laser gas. Further, since the Roots blower 9 heats the laser gas when compressing same, the laser gas from the Roots blower 9 is passed through a cooling unit 7 before the laser gas is again introduced into the electric discharge tube 1. The cooling units 7 and 8 will not be described in detail as they are well known in the art. The above conventional laser oscillator device has the following problem: First, since the Roots blower is a low-speed volumetric blower, it is large in size and weight, and thus the laser oscillator itself is large; second, the Roots blower emits a pulsating gas flow, and the laser oscillation characteristics are affected by this pulsating gas flow; and third, the Roots blower produces vibrations which adversely affect the spot positioning stability of the laser beam. If a turbo blower is used instead of the Roots blower, however, it may be damaged due to resonance when rotated at a high speed. According to a first aspect of the present invention; a gas laser oscillator device having an electric discharge tube for producing an electric discharge in a laser gas contained in the electric discharge tube for laser excitation, an optical resonator for effecting laser oscillation, and a gas circulating device having a gas blower and a cooling unit for forcibly cooling the laser gas, is characterised in that the blower comprises a turbo impeller rotatable in the laser gas and an electric motor for driving the turbo impeller, the electric motor having a pair of bearings each provided with a squeezed-film damper the squeezed-film damper comprising a sleeve which carries an outer race of the bearing and which is disposed within, but not fixed to, a surrounding bearing housing, there being a gap between the sleeve and the bearing housing providing a sealed space which is filled with grease or oil, each end of the sealed space being sealed by a respective O-ring, and the damping coefficient of the squeezed-film damper of the bearing closer to the turbo impeller being smaller than that of the other squeezed-film damper. According to another aspect of the invention, there is provided a turbo blower for a laser, the blower comprising a motor which includes a shaft having a distal end to which a turbo impeller is mounted, a pair of bearings for supporting the shaft, a rotor, and a stator, characterised in that the bearings are each provided with a squeezed-film damper, the squeezed-film damper comprising a sleeve which carries an outer race of the bearing and which is disposed within, but not fixed to, a surrounding bearing housing, there being a gap between the sleeve and the bearing housing providing a sealed space which is filled with grease or oil, each end of the sealed space being sealed by a respective O-ring; and the damping coefficient of the squeezed-film damper of the bearing closer to the turbo impeller being smaller than that of the other squeezed-film damper. Since a turbo blower is used, the volume thereof, which is in inverse proportion to the rotational speed, can be reduced. Further, vibration of the blower is prevented by a damping effect provided by the inelasticity of the grease, etc., of the squeezed-film dampers around the bearings. Moreover, the squeezed-film dampers provided around the bearings of the turbo blower of the laser serve to absorb the vibration of the bearings. Further, by making the damping coefficient of one squeezed-film damper smaller than that of the other, the mode of vibration of the shaft at a critical speed can be varied, to thereby reduce stress produced in a portion of the shaft close to the bearing, and thus permit a high-speed rotation of the blower. In the accompanying drawings: Fig. 1 is a diagram showing an entire arrangement of a gas laser oscillator device according to one embodiment of the present invention; Fig. 2 is a diagram showing an example of an arrangement of a turbo blower; and Fig. 3 is a diagram showing an arrangement of a conventional gas laser oscillator device. Figure 1 shows an entire arrangement of a gas laser oscillator device according to an embodiment of the present invention. Those parts in Fig. 1 which are substantially identical in structure and operation to those of Fig. 3 are denoted by identical reference numerals and will not be described in detail below. In Fig. 1, a turbo blower 15 is used instead of the Roots blower 9, and since the turbo blower has a much greater efficiency than the Roots blower, the heat produced by the compression of the laser gas is negligible, and accordingly, the cooling unit 7 shown at the downstream side in Fig. 3 can be omitted. Namely, the second cooling unit is omitted in Fig. 1, but may be provided if needed. Figure 2 shows an example of an arrangement of the turbo blower. The turbo impeller 16 is shown as a centrifugal impeller, but may be a mixed flow impeller or an axial-flow impeller. The impeller 16 is mounted to a shaft 17 and rotated at a high speed of about 100,000 r.p.m. by a motor 19 and 20 arranged in a casing 18, which is separate from a casing in which the laser gas flows. Accordingly, the volume of the turbo blower is smaller than that of a Roots blower, which rotates at a lower speed, as the volume is in inverse proportion to the rotational speed. The present invention is chiefly concerned in that the resonance of the blower during a high-speed rotation operation can be prevented. In Fig. 2, the illustrated embodiment employs ball bearings, which comprise inner races 22 and 23 secured to the shaft 17, and balls 24 and 25. Note, in practice, many more balls than illustrated are used. Numerals 26 and 27 denote outer races of the bearings secured to sleeves 28 and 29, respectively. The sleeves 28 and 29 are not secured to bearing housings 34 and 35. Note, if the sleeves are not secured to the housing, the following disadvantages arise; first-, second-, and third-order critical speeds of the shaft 17 occur sequentially when the rotational speed thereof is increased, and a rotating element, if not perfectly balanced during rotation, may be damaged due to centrifugal force when the rotational speed thereof passes across the critical speed. Generally, the third-order critical speed can be designed to be sufficiently high compared to the usual range of rotation speed, but measures must be taken against the vibration occurring at the first- and second-order speed. Accordingly, there is a demand for an elimination of the need to adjust the balance of rotation and to machine the housing with a high accuracy. The sleeves are not secured to the bearing housing's, and a gap of 10 to 100 µm is provided between the two elements, which gap is filled with grease to dampen the vibration of the sleeves due to the inelastic property thereof. In Fig. 2, the grease is indicated by hatching and numerals 36 and 37. The bearings are located in the laser gas, and therefore, to avoid contamination of the laser gas, grease having a small evaporation pressure is used as the damping material. Further, to prevent scattering of the grease, the grease-filled region is externally sealed by two pairs of O-rings 30, 31 and 32, 33. Although ball bearings are used in the illustrated example, plain bearings may be used instead, and further, oil may be used instead of grease. Due to the use of the dampers having the above structure, a gap of several tens of microns exists between the sleeve and the bearing housing. Accordingly, the extremely precise finish essential when machining the conventional housing becomes unnecessary, thus facilitating the machining process. In Fig. 2, a cooling water coil 21 is wound around the housings 34 and 35, to water-cool the electric motor. With the above-described arrangement, the vibration produced when the impeller 16 and the shaft 17 are rotated is reduced by a hydrodynamic damping effect of the squeezed-film dampers. The damping coefficient of the squeezed-film damper is expressed by the following formula: C = πµR(L/S)³ where π = ratio of the circumference to the diameter (3.14...) µ = viscosity R = radius of damper L = length of damper S = radial clearance. Therefore, the damping coefficient can be changed by varying the viscosity, the radius or length of the damper, or the radial clearance; the most practical means thereamong is to change the radial clearance. In connection with the mode of vibration of the shaft when the rotational speed passes across the critical speed, the amplitude of vibration is larger at the distal end of the shaft near the turbo impeller because the impeller is projected from the paired bearings, and accordingly, a large stress is produced at a portion 17a of the shaft close to the bearing. Therefore, by making the damping coefficient of the damper at the impeller side smaller than that of the other, vibration of the bearing at the impeller side is increased, and thus a stress produced in the shaft portion 17a close to that bearing is reduced. Particularly, damage to a portion 17b of the shaft 17 at which the diameter changes, due to a concentration of the stress thereat, can be prevented. The present invention is particularly useful for a high-frequency discharge pumping CO₂ laser. If a DC electric discharge is used for laser excitation, then a turbulent flow must be produced in the laser gas to obtain a uniform electric discharge. A Roots blower is best suited to such an application, since such a blower requires a high compression ratio. But if a high-frequency electric discharge is required for laser excitation, then it is not necessary to provide a turbulent flow in the laser gas, and accordingly, a turbo blower having a low compression ratio and a high discharge capacity is more effective for the purpose. As described above, a turbo blower is used in which squeezed-film dampers are provided for the rotary shaft of the turbo blower, and therefore, the size and weight of the blower, and thus the entire system, can be reduced. Further, since the vibration of the blower and the pulsating gas flow are eliminated, the laser has improved beam characteristics such as spot positioning stability and output stability during a high-speed operation, etc. Moreover, damage due to resonance, which is usually inevitable during a high speed rotation operation, can be avoided. The dampers are mounted to a pair of bearings, and the damping coefficient of one damper is different from that of the other, whereby vibration of the bearings is reduced, the spot positioning stability of the laser beam improved, and the service life of the bearings prolonged. Furthermore, the possibility of damage to the shaft is reduced, and therefore, it is possible to provide a small-sized high-efficiency turbo blower having an impeller which can be rotated at a high speed.

Claims: A gas laser oscillator device having an electric discharge tube (1) for producing an electric discharge in a laser gas contained in the electric discharge tube for laser excitation, an optical resonator (4,5) for effecting laser oscillation, and a gas circulating device having a gas blower (15) and a cooling unit (8) for forcibly cooling the laser gas, characterised in that the blower comprises a turbo impeller (16) rotatable in the laser gas and an electric motor (19,20) for driving the turbo impeller, the electric motor having a pair of bearings (22,24,26,23,25,27) each provided with a squeezed-film damper (36,37) the squeezed-film damper comprising a sleeve (28,29) which carries an outer race (26,27) of the bearing and which is disposed within, but not fixed to, a surrounding bearing housing (34,35), there being a gap between the sleeve and the bearing housing providing a sealed space which is filled with grease or oil (36,37), each end of the sealed space being sealed by a respective O-ring (30,31,32,33), and the damping coefficient of the squeezed-film damper (36) of the bearing closer to the turbo impeller (16) being smaller than that of the other squeezed-film damper (37). A device according to claim 1, wherein the bearings are ball bearings (22,24,26;23,25,27). A device according to claim 1, wherein the bearings are plain bearings. A turbo blower for a laser, the blower comprising a motor which includes a shaft (17) having a distal end (17a) to which a turbo impeller (16) is mounted, a pair of bearings (22,24,26;23,25,27) for supporting the shaft, a rotor (19), and a stator (20), characterised in that the bearings are each provided with a squeezed-film damper (36,37) the squeezed-film damper comprising a sleeve (2,8,29) which carries an outer race (26,27) of the bearing and which is disposed within, but not fixed to, a surrounding bearing housing (34,35), there being a gap between the sleeve and the bearing housing providing a sealed space which is filled with grease or oil (36,37), each end of the sealed space being sealed by a respective 0-ring (30,31,32,33); and the damping coefficient of the squeezed-film damper (36) of the bearing closer to the turbo impeller (16) being smaller than that of the other squeezed-film damper (37). A turbo blower, according to claim 4, wherein the damping coefficients are different by virtue of the gaps between the respective sleeves (28,29) and bearing housings (34,35) being different. A turbo blower according to claim 4 or claim 5, wherein the bearings are ball bearings, (22,24,26;23,25,27). A turbo blower according to claim 4 or claim 5, wherein the bearings are plain bearings. A device according to any one of claims 1 to 3, in which the blower (15) is a turbo blower according to any one of claims 5 to 7.

Inventors: FUNAKUBO TSUTOMU, KARUBE NORIO, FUNAKUBO, TSUTOMU, KARUBE, NORIO
Applicants: FANUC LTD, FANUC LTD.
Application year: 1989
Main classification: H01S3
IPC codes: F04D29, H02K5, F16C27, H01S3