US3604310A - Transducer for producing mechanical oscillations - Google Patents

Transducer for producing mechanical oscillations Download PDF

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Publication number
US3604310A
US3604310A US791250A US3604310DA US3604310A US 3604310 A US3604310 A US 3604310A US 791250 A US791250 A US 791250A US 3604310D A US3604310D A US 3604310DA US 3604310 A US3604310 A US 3604310A
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chamber
transducer
relative
piston member
pressure
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US791250A
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English (en)
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Keith Foster
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National Research Development Corp UK
National Research Development Corp of India
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National Research Development Corp UK
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
    • B06B1/183—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with reciprocating masses
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • a transducer adapted to be driven by pressure fluid to produce mechanical oscillations comprising a piston member and a cylinder member mounted for relative oscillating movement, the piston member having a face bounding a chamber in the cylinder member, valve means for cyclically pressurizing and depressurizing said chamber with pressure fluid to cause said relative oscillating movement, control means adapted to generate a first position signal as the members move relatively through a first relative position, and to generate a second position signal as the members move relatively through a second relative position, means to pass said position signals to control means including a bistable element which is adapted to control the valve means in response to said position signals the control means responding only to those first position signals, generated as the members move relatively in one sense through the first relative position, and only to those second position signals generated as the members
  • a transducer adapted to be driven by pressure fluid to produce mechanical oscillations, comprising a piston member and a cylinder member mounted for relative oscillating movement, the piston member having a face bounding a chamber in the cylinder member, valve means for cyclically pressurizing and depressurizing said chamber with pressure fluid to cause said relative oscillating movement, means adapted to generate a first position signal as the members move relatively through a first relative position, and to generate a second position signal as the members move relatively through a second relative position, and control means including a bistable element to control the valve means in response to said position signals, the control means responding only to those first position signals generated as the members move relatively in one sense through the first relative position, and only to those second position signals generated as the members move relatively in the opposite sense through the second relative position.
  • depressurized should be interpreted as meaning at a significantly lower pressure than pressurized, but that this significantly lower pressure is not necessarily zero.
  • the transducer may comprise means to feed each of the position signals through a respective logic gate, each gate being adapted to receive a respective control signal so that only those first position signals produced when the members move relatively in one sense through the first relative position are passed to the bistable element, and only those second position signals produced when the members move relatively in the opposite sense through the second relative position are passed to the bistable element.
  • pressure-sensing means to sense the pressure in the chamber, or a pressure related thereto, and to pass control signals to each said logic gate such that first position signals are only passed to the bistable element when the chamber is pressurized, and second position signals are only passed to the bistable element when the chamber is depressurized.
  • valve means may be adapted to pressurize and depressurize the further chamber at substantially 180 phase difference relative to the first-mentioned chamber
  • pressure-sensing means to sense the pressure in the first-mentioned and further chambers or pressures related thereto, and to pass control signals to each said logic gate, the gates being such that first position signals are only passed to the bistable element when the first-mentioned chamber is pressurized, and second posi tion signals are only passed to the bistable element when the further chamber is pressurized.
  • the valve means may be a shuttle valve, the bistable ele ment being adapted to control said valve means by means of pressure fluid signals.
  • a said logic gate may be adapted to receive a control signal for starting and stopping the transducer.
  • a resilient biasing means adapted to resiliently oppose said relative oscillating movement.
  • the resilient biasing means may comprise a fluid spring chamber adapted to contain fluid constituting a fluid spring, the pressure in said fluid in operation being applied to another face of the piston members.
  • the invention provides a transducer adapted to be driven by pressure fluid to produce mechanical oscillations, comprising a piston member and a cylinder member mounted for relative oscillating movement, the cylinder members having a chamber defined therein, the piston member having a face bounding said chamber; means for applying cyclic forces to the piston member and cylinder to produce said relative oscillating movement, said means including valve means or cyclically pressurizing and depressurizing said chamber with pressure fluid means to generate a transient first position signal as the members move relatively through a first relative position, and to generate a transient second position signal as the members move relatively through a second relative position, said positions not being extreme positions of said relative movement; control means to control the valve means in response to said position signals; and means to govern the control means to respond only to those first position signals generated as the members move relatively in one sense through the first relative position. and only to those second position signals generated as the members move relatively in the opposite sense through the second relation position.
  • the invention will described, merely by way of example, with reference to
  • FIG. 1 shows one embodiment of a transducer according to the invention, the invention
  • HO. 2 (a) and 2 (b) show position signal pulses plotted against time
  • FIG. 3 shows an alternative embodiment of the invention
  • FIG. 4 shows another embodiment of the invention.
  • a transducer adapted to be driven by pressure fluid to produce mechanical oscillations, comprising a piston member 10 mounted in a cylinder member 12 for relative sliding movement therewith.
  • the cylinder comprises a first chamber 14 which is bounded by an operative face 16 of the piston 10.
  • the cylinder also comprises a fluid spring chamber 18 which is bounded by an operative face 20 of the piston members which is opposed to the face 16.
  • the chamber 18 contains fluid constituting a fluid spring which urges the piston member 10 and cylinder 12 towards predetermined relative positions, thereby opposing relative movement thereof.
  • the piston member 10 comprises two relatively large diameter lands, 24, 26 which define a short groove 28, and that the operative face 20 is formed by the change in diameter between the large diameter portion 26 and a small diameter portion 30 which is effectively divided into two lands by an annular groove 31.
  • the portion 30 of the piston member extends out of the cylinder 12 via a bore 32, and is arranged to drive, for example, a rock drill bit or an agricultural grass mower (not shown).
  • the chamber 14 is connected via a valve 34 alternately to a source of pressure fluid at substantially constant pressure via a line 38, or to a low-pressure tank via a line 40,
  • the line 38 contains an accumulator 42 to maintain the pressure therein substantially constant.
  • the valve 34 comprises a shuttle valve 36, having two spaced-apart lands 44, 46, the end faces thereof bounding chambers 48, 50 respectively. Pressure fluid may be fed to either of chambers 48, 50 to more the valve member 36 from the one positioned to the other or vice versa. The fluid already in the opposite chamber is allowed to escape via restrictors 52, 54 to drains 56, 57.
  • the valve member 36 can take two positions, depending on which of the chambers 48, 50 is pressurized, the first position in which the chamber 50 is pressurized being shown in FIG. 1, wherein chamber 14 is connected to line 38. In the other position (not shown), the
  • chamber 48 is pressurized and chamber 14 is connected to line 40.
  • the relatively large diameter lands 24, 26 and the groove 31 of the piston member cooperate with spaced-apart ports 58, 59, 61, 63 in the cylinder wall.
  • Ports 58, 59 are connected to a line 60 which in turn is connected to line 38, and thus contains pressure fluid.
  • the ports 61, 63 are respectively connected via lines 62, 64 to chambers 48 and 50 of the valve 34.
  • the port 59 is located opposite the port 63 in the cylinder wall so that, during relative oscillating motion, this port is briefly connected with the port 63 via the groove 28.
  • the ports 58 and 61 are arranged opposite to each other and are briefly interconnected by the groove 31 during oscillation
  • the ports 58, 59, 61 63 and the grooves 28, 31 constitute control means.
  • the lines 62 and 64 are respectively connected to chambers 48 and 50 via a bistable e.g. a flip-flop element 72, which has a memory so that once a short pulse of pressure fluid has been applied to lines 62 or 64, the flip-flop 72 switches and remains in that position until a pulse of pressure fluid is applied to the other line.
  • a bistable e.g. a flip-flop element 72, which has a memory so that once a short pulse of pressure fluid has been applied to lines 62 or 64, the flip-flop 72 switches and remains in that position until a pulse of pressure fluid is applied to the other line.
  • the flip-flop may be a pure fluid device, for example, a wall attachment element, or may be built from two three-way piston valves in a manner well known in fluidics. Resistances 52 and 54 and drains 56 and 58 are not required if a wall attachment device is used, as these are incorporated in the element.
  • the flip-flop acts as a switch for a flow of pressure fluid supplied to the flip-flop along a line which, as is conventional, is not illustrated, the switching occurring upon receipt of a signal along line 62 or 64 upstream of the flip-flop and the switched flow, derived from the nonillustrated supply line, occurring along line 62 or 64 downstream of the flip-flop to the chamber 48 or 50 respectively.
  • the transducer operates in the following way: when the ports are in the positions shown in FIG. 1, the chambers 14 and 50 are pressurized and the piston member 10 is moving rightwards. As the piston member 10 passes rightwards through the position (herein called the first relative position) in which the ports 58 and 61 are connected, and a first position signal is produced on the line 62. This signal pulse causes the flip-flop 72 to switch to a state in which it passes pressure fluid along line 62 to the chamber 48 thereby pressurizing chamber 48 even though some portion of the pressure fluid flow towards chamber 48 passes through resistance 52 to drain 56.
  • the flip-flop cuts off pressure fluid flow along line 64 towards chamber 50 and hence chamber 50 is depressurized and drained through resistance 54 to drain 57 thereby allowing the shuttle valve 36 to move to its second position under the influence of pressure in chamber 48.
  • the chamber 14 is then depressurized and the fluid in the chamber 18 acts upon the piston member to move it leftwards. Due to the momentum of the piston member 10, it continues its rightward movement for a short time after the chamber 14 is depressurized. Consequently when the piston member does move leftward, another (redundant) position signal is produced on the line 62.
  • the flip-flop 72 since the flip-flop 72 has already switched in response to the previous position signal on the line 62, it ignores this redundant first position signal.
  • the relative positions of the ports 58, 59, 61 and 63 and the spacing of the grooves 28, 31 determines, with the mass of the piston member 12 and the elasticity of the fluid spring 18, both the frequency of the relative oscillating movement of the piston member and the cylinder, and the phase difference of the cyclic pressurization of the chamber 14 relative to the relative oscillating motion.
  • Makeup flow is supplied to the chamber 18 via a line 66 containing a nonreturn valve 68.
  • the makeup flow compensates for any leakage that may occur, for example, through the bore 32.
  • the makeup flow may be taken from the line 40, which may be maintained at a relatively low pressure (cg. 100 p.s.i., compared to a pressure of order 1,000 p.s.i. in the line 38).
  • the makeup flow would then occur when the pressure in the chamber 18 falls below 100 p.s.i.
  • the transducer as so far described may be controlled by means of a stop valve in one or other of lines 62 or 64, or by stop valve in the pressure fluid supply line 38.
  • a preferred means of control is illustrated in FIG. 1.
  • the lines 62 and 64 are respectively connected to the flip-flop element 72 via logic gates 74 and 75. These gates are AND" gates which may be used for starting and stopping the relative oscillating motion of the piston member and cylinder, depending upon the presence or absence of control signals applied to the gates via lines 77 and 78. For example, if a control signal is not present on line 78, the pressure fluid pulse from line 64 will not be allowed to pass the flip-flop element 72, so that the valve member 36 will not be pushed into its first position. The piston member 10 will thus stop at the left hand end of the cylinder 12.
  • line 78 may incorporate a pulse-shaping element 80, so that any control signal that is applied thereto is converted to a pulse whose time duration is shorten than the period of one cycle of the relative oscillating motion.
  • a control signal to be present in line 77 and that line 64 is pressurized, then, on application of such a pulse to line 78, only one cycle of relative oscillating motion will then occur before the piston member comes to rest again since by the time that line 64 is again pressurized, the control signal in line 78 has disappeared and the gate 75 does not permit pressure fluid pulse in line 64 to be fed to the flip-flop element 72.
  • the pulse-shaping element 80 can be incorporated in line 77.
  • the AND" gates and the pulse shaping element may be pure fluid devices of the types now well known, or may be produced by piston valves.
  • the AND" gates may be replaced by NOR gates, reversing the logic.
  • the timing of the position signals may have to be advanced to such a degree that the redundant first position signal produced as described above occurs after the nonredundant second position signal, and similarly the redundant second position signal occurs after the nonredundant first position signal.
  • the timing advance is necessary due to the finite time required to pressurize and depressurize the chamber 14.
  • FIG. 2(a) shows the occurrence of the first and second position signals P in time T as produced by a transducer such as that of FIG. 1 when operating at a moderate frequency.
  • the first and second nonredundant position signals P and P and the redundant first and second position signals P,', P are produced in the sequence P,, 1 P P P,, P,, P P etc.
  • the chaindotted lines E,, E indicate the times at which the piston member is at the right-hand extremity of its stroke, and the lines E E, indicate when it is at the left-hand extremity of its stroke.
  • the piston member 10 of course changes direction at the end of its stroke and it will be noted that the nonredundant signals P P occur relatively close in time to the change of direction of the piston member that they produce.
  • FIG. 2(b) illustrates the occurrence of the position signals in a transducer operating at a very high frequency, and it will be seen that the nonredundant signals P P occur well in advance of the resulting change in piston direction.
  • the signals are produced in the sequence P P P P,', P P P P, P etc. and consequently the flip-flop 72 would treat some of the redundant position signals as nonredundant and vice versa, resulting in the pressure cycles in the chamber 14 being wrongly timed, unless the transducer is modified as described hereafter.
  • FIG. 3 there is shown a modified transducer for use at high frequencies. Parts described with reference to FIG. 1 carry the same reference numerals.
  • the gates 74, 75 are arranged to receive control signals via respective lines 81, 82.
  • the lines 81, 82 are connected to a pressure sensor 84 which is arranged to sense the pressure in the chamber 14.
  • the sensor 84 is shown connected to the chamber 14 via a line 86, but it will be appreciated that it is described that this line is as short as possible, the sensor preferably being built into the wall of the chamber 14. Of course, a pressure related to the pressure in the chamber 14 could be sensed instead, provided its relationship thereto is a univalued function.
  • the sensor 84 is such that a control signal is provided on the line 81 only when the chamber 14 is pressurized, and a control signal is provided on the line 82 only when the chamber 14 is depressurized.
  • the transducer operates as follows. Assuming the piston member is moving rightwards form it left-hand extreme position E the chamber 14 is pressurized. Firstly, a nonredundant first position signal P, is produced on the line 62. Since the chamber 14 is pressurized, the AND gate 74 passes the first position signal to the flip-flop 72, which then initiates depressurization of the chamber 14. The next position signal produced is a redundant second position signal, P, on the line 64, as the groove 28 passes the ports 59, 63. However, since the chamber 14 takes a finite time to depressurize, the pressure therein is still sufficient at this time for the sensor to produce a control signal on the line 81, and not the line 82.
  • the AND" gate 75 does not pass the redundant signal to the flip-flop 72.
  • the piston member 10 then reaches the end of its stroke at E and begins to move in the opposite sense (leftwards).
  • a nonredundant second position signal P is then produced, and by this time the chamber 14 has depressurized sufficiently for the sensor 84 to produce a control signal on the line 82, and not on the line 81. Consequently the AND" gate 75 passes the second position signal to the flip-flop 72, which initiates pressurization of the chamber 14.
  • Control signal lines 77, 78 are provided as in the FIG. 1 embodiment, the logic gates 74, 75 having three inputs as shown in the drawing, (e.g. by making each logic gate of two twoinput gates in cascade).
  • the transducer is such that there is a marked difference in the duration of the leftward and rightward piston movements (e.g. if the transducer is operating a quick-return mechanism) it may be necessary to advance the timing of one of the position signals so that both nonredundant position signals occur when the piston member is moving in one direction. To permit this it is necessary to arrange that the chamber 14 is pressurized more quickly than it is depressurized (or vice versa, depending on the exact piston movement employed). This can be achieved for example by adjusting the relative flow areas of the inlet and outlet lines 38, 40.
  • the transducer is provided with a further chamber 15 bounded by a further operative face 17 of the piston member 10, opposed to the face 16.
  • a further fluid spring chamber 19 is provided, acting on a yet further face 21 of the piston member 10, opposed to the face 20 thereof.
  • the faces 20, 21 are of the same area. It will be appreciated that the fluid pressures in the chambers 18, 19 serve to resiliently bias the piston member against movement in either direction.
  • the chambers l4, 15 are cyclically pressurized and depres surized at 180 phase difference with each other, by means of a modified control valve 34, which employs a three-land shuttle valve 37, and has two spaced-apart ports connected to the low-pressure line 40 and has two further ports connected to the chambers 14 and 15 via lines 90, 92.
  • a modified control valve 34 which employs a three-land shuttle valve 37, and has two spaced-apart ports connected to the low-pressure line 40 and has two further ports connected to the chambers 14 and 15 via lines 90, 92.
  • the control circuit instead of a single pressure sensor 84 there are provided two sensors 94, 96 respectively arranged to sense the pressures in the chambers 14 and 15, or pressures functionally related thereto. Unlike the sensor 84, the sensors 94, 96 have only one output line 98, 100 respectively, upon which respective control signals are produced only when the chambers 14 and 15 respectively are pressurized.
  • the operation of the transducer is the same as that of the FIG. 3 transducer except that the AND" gate 75 receives signals indicative of high pressure in the chamber 15 instead of low pressure in the chamber 14. This is practicable because of the phase difference between the pressure cycles in the two chambers.
  • the flip-flop 72 is of the wall attachment type which renders it unnecessary to include resistances 52, 54 and drains 56, 58.
  • the flip-flop 72 receives the first position signal from AND gate 74, it switches application of fluid pressure from line 62 leading to chamber 48 to line 64 leading to chamber 50 whereby chamber 50 is pressurized and moves the valve 37 leftwards as seen in FIG. 4 while chamber 48 is depressurized and drains along line 62 to and through the bleeds or vents in the flipflop.
  • the flip-flop receives the second position signal from the AND" gate 75, it switches application of fluid pressure from line 64 leading to chamber 50 to line 62 leading to chamber 48 whereby chamber 48 is pressurized and moves the valve 37 rightwards as seen in FIG. 4 while chamber 50 is depressurized and drains along line 64 to and through the bleeds or vents in the flip-flop.
  • the AND gate 75 does not pass the redundant signal to flip-flop 72.
  • the piston member then reaches the end of its stroke at E and begins to move in the opposite sense (leftwards) due to the pressure in chamber 15.
  • a nonredundant second position signal P is then being produced and the high pressure in chamber causes the sensor 96 to produce a control signal on the line 100. Consequently, the AND" gate 75 passes the second position signal to flip-flop 72, which initiates pressurization of the chamber 14 and depressurization of the chamber 15.
  • the waveform of the cyclically applied pressure may be controlled.
  • the waveform is substantially a square wave, but alternative waveforms may be preferable if the transducer is not required to produce impacts.
  • the biasing means instead of being a fluid spring as hereinbefore described may in any of the embodiments be, for example, a mechanical spring, a magnetic spring, or when the working fluid is a liquid, a pneumatic spring.
  • the chamber would be divided into two portions by a flexible diaphragm, one portion containing gas under pressure, the other containing working fluid in contact with the face 20.
  • the chamber 19 would be similarly divided.
  • a transducer adapted to be driven by pressure fluid to produce mechanical oscillations, said transducer comprising:
  • a piston member and a cylinder member mounted for relative oscillating movement, the cylinder member having a chamber define therein, the piston member having a face bounding said chamber, means for applying cyclic forces to this piston member and cylinder to produce said relative oscillating movement,
  • said means including valve means for cyclically pressurizing and depressurizing said chamber with pressure fluid
  • control means including a bistable element to control the valve means in response to said position signals, the control means responding only to those first position signals generated as the members move relatively in one sense through the first relative position and only to those second position signals generated as the members move relatively in the opposite sense through the second relative position.
  • a transducer as in claim 1 comprising:
  • the logic gate being adapted in response to the gate control signal, to permit or prevent the passage of the position signal to the bistable element.
  • valve means is a shuttle valve, the bistable element, being adapted to apply pressure fluid signals to the valve means.
  • a transducer as in claim 1 wherein the means for applying comprises resilient biasing means to resiliently bias the piston member and cylinder member to relative movement in a predetermined sense.
  • a transducer as claimed in claim 5 wherein the resilient biasing means comprises a fluid spring chamber adapted to contain fluid constituting a fluid spring, another face of the piston member being subjected in operation to the pressure of said fluid.
  • means to govern the control means by receiving the position signals and passing to the control means the first position signals generated only during said relative movement in the first sense, and the second position signals generated only during relative movement in the second sense.
  • a transducer as in claim 7 wherein the governing means comprises:
  • a transducer as in claim 8 wherein the producing means comprises pressure sensing means to sense the pressure in the chamber, or a pressure related thereto the first logic gate passing first position signal to the bistable element only when the chamber is pressurized, the second logic gate passing second position signals to the bistable element only when the chamber is depressurized.
  • the means for applying comprises a further chamber bounded by a further face of the piston member, opposed to the first-mentioned face, the valve means being adapted to pressurize and depressurize the further chamber at substantially 180 phase difference relative to the first-mentioned chamber, and
  • the producing means comprises pressure-sensing means to sense the pressure in the first-mentioned and further chambers, or pressures related thereto, and to pass gate control signals to each said logic gate, the gates passing first position signals to the bistable element only when the first mentioned chamber is pressurized, the gates passing second position signals to the bistable element only when the further chamber is pressurized.
  • a transducer as in claim 1 wherein the means to generate comprises:
  • a transducer adapted to be driven by pressure fluid to produce mechanical oscillations comprising:
  • the cylinder member having a chamber defined therein
  • the piston member having a face bounding said chamber
  • said means including valve means for cyclically pressurizing and depressurizing said chamber with pressure fluid
  • control means to control the valve means in response to said position signals
  • control means to govern the control means to respond only to those positions signals generated as the members move relatively in one sense through the first relative position, and only to those second position signals as the members relatively in the opposite sense through the second relative position.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Percussive Tools And Related Accessories (AREA)
US791250A 1968-01-16 1969-01-15 Transducer for producing mechanical oscillations Expired - Lifetime US3604310A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3780621A (en) * 1971-06-07 1973-12-25 Atlas Copco Ab Hydraulic fluid actuated percussion tool
US3782246A (en) * 1969-07-11 1974-01-01 Koeppern & Co Kg Maschf Hydraulically operated vibration drives
US4050356A (en) * 1974-03-11 1977-09-27 Haeny & Cie Ag Apparatus for controlling a fluid medium

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4280396A (en) * 1978-05-18 1981-07-28 Control Concepts, Inc. Hydraulic oscillator

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3296941A (en) * 1965-02-15 1967-01-10 Beckman Instruments Inc Logic control system

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3296941A (en) * 1965-02-15 1967-01-10 Beckman Instruments Inc Logic control system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3782246A (en) * 1969-07-11 1974-01-01 Koeppern & Co Kg Maschf Hydraulically operated vibration drives
US3780621A (en) * 1971-06-07 1973-12-25 Atlas Copco Ab Hydraulic fluid actuated percussion tool
US4050356A (en) * 1974-03-11 1977-09-27 Haeny & Cie Ag Apparatus for controlling a fluid medium

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DE1902122A1 (de) 1969-09-04

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