KR950002139B1 - Pump - Google Patents

Abstract

The apparatus comprises driving members (4,5) rotated by a driver (1) and their perypheral faces having gears, or friction parts (13,14) made of rubber, and non-friction parts having the smaller diameter alternately arranged; driver members (6,7) which are supported by stoppers (21,22) and a spacer (S) and contact with the parts (13,14) of the driving members (4,5) on spirally grooved shaft (8) to be driven. The device generating the oil pressure has two pistons at both ends of the shaft (8) to generate the oil pressure.

Description

Rotary motion / constant linear reciprocating motion switching device and hydraulic generator using the same

1 is a perspective view showing the configuration of a switching device according to the present invention.

2 is a perspective view showing the configuration of a hydraulic pressure generating apparatus according to the present invention.

3 is a partial perspective view showing an extract of the main part of the present invention.

4 is a perspective view showing an extract of the spiral axis of FIG.

5 is a view for explaining the process of generating the hydraulic pressure according to the present invention,

a is a schematic diagram of the hydraulic line.

b is a timing diagram of hydraulic generation.

6 is a perspective view showing another embodiment of the hydraulic pressure generating apparatus according to the present invention.

7 is a perspective view showing an extract of the spiral axis of FIG.

8 is a perspective view showing yet another embodiment of a hydraulic pressure generating apparatus according to the present invention.

9 is a perspective view showing still another embodiment of a hydraulic pressure generating apparatus according to the present invention.

* Explanation of symbols for main parts of the drawings

1: drive means 4, 5: drive member

6, 7: driven member 8: spiral shaft

9, 10: spiral groove 11, 12: protrusion

13, 14: friction elements 15, 16: guide plate

25, 26: piston 27, 28: hydraulic cylinder

29, 30: fluid storage tank 33: confluence pipe

The present invention relates to a rotational motion / constant linear reciprocating motion switching device and a hydraulic generating device using the same, and more particularly, a switching device for converting a rotational motion into a constant speed linear reciprocating motion or converting a linear motion into a rotational motion and using the same. It relates to a hydraulic generator that can minimize the pulsation.

A representative example of a device for converting a linear reciprocating motion into a rotary motion or a rotational motion for a linear reciprocating motion is a crank mechanism.

The crank mechanism has a structure in which a crank pin is provided at a position away from the center crank shaft, and a crank rod is connected to the pin. Therefore, the rotational movement of the crankshaft is converted into the linear reciprocating motion of the crank rod, or conversely, the linear reciprocating motion of the crank rod is converted into the rotational motion of the crank shaft. However, the crank mechanism has a disadvantage in that the linear reciprocating speed of the crank rod is not constant because the crank rod and the crank shaft are arranged to be offset from each other.

On the other hand, the hydraulic apparatus is provided with a pump for generating power, an actuator such as a cylinder or a motor that actually performs work, a control valve for controlling the actuator, and an accessory device that performs an auxiliary role.

In such a hydraulic device, the pump is a volumetric pump that enables the generation of high pressure, and mainly a vane, a gear, a plunger type, and the like, and a screw pump is used under special conditions such as a large capacity or a high viscosity liquid. However, the hydraulic pressure generated by the hydraulic pump or the hydraulic motor is accompanied by pulsation due to structural or operational characteristics.

Since the pulsation phenomenon causes the actuator to operate irregularly, the pulsation phenomenon should be fundamentally removed from the automation system. Hydraulic pressure is a method of solving the pulsation phenomenon, and conventionally relies on an accumulator or other mechanism.

However, the method described above is considered to be undesired because it is a factor that complicates the structure of the hydraulic system and also requires a means for controlling newly added equipment.

SUMMARY OF THE INVENTION An object of the present invention is to provide a rotary motion / constant linear reciprocating motion switching device capable of converting a rotary motion into a constant speed linear reciprocating motion, or a linear reciprocating motion into a rotary motion, and a hydraulic generator using the same.

In order to achieve the above object, the present invention is to rotate the driven member by rotating the plurality of driven members supported on the spiral shaft through a plurality of friction elements that are equally arranged in a position in which the outer circumferential surface is staggered, these driven members As the projections formed inside the center of the meshed with the spiral grooves extending in opposite directions from the outer circumference of the spiral shaft to transmit power, the rotational motion of the drive member is converted into the constant velocity linear reciprocating motion of the spiral shaft, Or a rotational / constant linear reciprocating switching device for converting the constant linear reciprocating motion of the spiral shaft into the rotational motion of the drive member, or by mounting pistons at both ends of the spiral shaft, the piston being disposed inside the hydraulic cylinder. Constant linear reciprocating motion of the spiral shaft And in that said one piston to a pumping action feature.

Hereinafter, preferred embodiments of the present invention will be described in more detail with reference to the accompanying drawings.

The rotational motion / constant linear reciprocating motion switching device according to the present invention includes a driving means (1) made of a hydraulic motor and the like as shown in FIG. 1, and a rotation driving part (2) which is rotated by receiving the rotational force of the driving means (1). And a linear motion part 3 for converting the rotational motion of the rotary drive part 2 into a constant velocity linear reciprocating motion.

The rotary drive unit 2 includes a plurality of drive members (4) (5) provided on the output shaft of the drive means (1). The linear motion portion 3 is provided through a plurality of driven members 6 and 7 connected to the driving members 4 and 5 so as to transmit power, and through the centers of the driven members 6 and 7. It becomes the spiral shaft 8.

The spiral shaft 8 of the linear motion portion 3 is engraved with a pair of spiral grooves 9 and 10 on its outer circumference, and the spiral directions of these spiral grooves 9 and 10 are opposite to each other so as to be opposite to each other. When (9) is the right screw, the other spiral groove (10) should be engraved with the left screw.

In response to the pair of spiral grooves 9 and 10 described above, the plurality of driven members 6 and 7 interlock the spiral shaft 8 by fitting the projections 11 and 12 formed on the inner circumferential surface of the central shaft hole. Can be combined.

Here, the plurality of driven members 6 and 7 is divided into two groups, one of the driven members 6 in the spiral groove 9 of the right screw, and the other of the driven members 7 in the left screw spiral. Is combined with the groove 10.

The driving members 4 and 5 and the driven members 6 and 7 described above form a pair for transmitting power to each other. On the other hand, the plurality of driven members (6) (7) divided into two groups is a drive member (4) because the linear movement of the spiral shaft (8) is possible only when the other group is idle when the group is driven to follow the rotation And the driven member (6) group, and the drive member (5) and the driven member (7) group should be intermittent of the power to alternate the power transmission operation and idle.

According to the present invention, it is possible to alternately control power between the plurality of driving members 4, 5 and the driven members 6, 7 by group. That is, the outer circumferential surfaces of all the driving members 4 and 5 are divided into a plurality of friction elements 13 and 14 to be in contact with the driven members 6 and 7 so as to transmit power, and slightly to prevent power transmission. Alternatingly formed into portions having a small diameter, these friction elements 13 and 14 are arranged in staggered positions so that the other group is in a power non-transmission state when one group is in a power transmission state.

The friction elements 13 and 14 described above have the same effect even if they are added to the driven members 6 and 7. In the case of power transmission by gear connection as in the illustrated embodiment, the friction elements ( 13) 14 are substantially sector gears having semi-circular teeth, and a plurality of driven members 6 and 7 which are in contact with these friction elements 13, 14 are constituted by pinion gears.

In addition, when the friction elements 13 and 14 become rubber pad surfaces, the plurality of driven members 6 and 7 in friction contact with them are substantially friction wheels in which rubber pads are wrapped around the outer circumferential surface.

The relationship between the plurality of driven members 6, 7 and the spiral shaft 8 constituting the linear motion portion 3 described above should be set as follows. The plurality of driven members 6 and 7 can only rotate in place and cannot be moved on the spiral shaft 8, and the spiral shaft 8 can be linearly moved but not driven.

In order to satisfy the above conditions, this embodiment protrudes the guide plates 15 and 16 on the outer circumferential sides of the spiral shaft 8 and at the same time separate guiders 17 around the spiral shaft 8. The guide plates 15 and 16 are erected so that the guide plates 15 and 16 are alternately piggybacked on the linear movement of the spiral shaft 8 and alternately guided in the guide grooves 19 and 20 of the guiders 17 and 18. As a result, the driven rotation of the spiral shaft 8 is suppressed. The driven members 6 and 7 are supported by the stoppers 21 and 22 and the spacers S disposed therebetween so as to rotate in place.

The above-described anti-rotation structure of the spiral shaft 8 is not limited to the arrangement of the guide plates 15 and 16. For example, a straight key groove is formed on the outer periphery of the spiral shaft 8, and on the other hand, The rotation of the spiral shaft 8 can also be prevented by adding a key that engages the key groove to the journal bearings 23 and 24 supporting both ends of the spiral shaft 8.

In the rotary motion / constant linear reciprocating motion switching device of the present invention configured as described above, when one group of driven members 6 is rotated and driven, the spiral shaft 8 is linearly moved only in one direction, and the other group When the driven member 7 rotates, the helical shaft 8 also moves linearly in the other direction as opposed to the above, thereby performing a linear reciprocating motion.

With the above-described configuration, the rotational motion / constant linear reciprocating motion switching device of the present invention alternately rotates the rotational force of the drive means 1 via the drive members 4 and 5 of the rotational drive part 2. 3) The projections 11 and 12 formed in the central shaft hole of the driven members 6 and 7 are rotated when driven to and driven by the driven members 6 and 7, respectively. As the driven shafts alternately follow the spiral grooves 9 and 10 formed in the opposite direction to (8), the spiral shaft 8 exhibits a linear reciprocating motion at a constant constant speed.

FIG. 2 is a perspective view showing an embodiment of a hydraulic pressure generating device constructed by the present invention, in which parts identical to those of FIG. 1 are denoted by the same reference numerals to avoid overlapping descriptions.

The hydraulic generator illustrated in FIG. 2 has pistons 25 and 26 on both side ends of the spiral shaft 8, each of which corresponds to the hydraulic cylinders 27 and 28. It is installed to be able to move forward and backward.

By such a configuration, the continuous constant rotational motion of the drive means 1 is transmitted to the linear motion part 3 via the rotational drive part 2 to appear as a constant velocity linear reciprocating motion of the spiral shaft 8, and as a result The pistons 25 and 26 at both ends of the furnace alternately generate hydraulic pressure while moving back and forth in the hydraulic cylinders 27 and 28.

That is, as shown in FIG. 3, the drive members 4 and 5 of the rotary drive unit 2 are provided with friction elements 13 and 14 only in the outer circumferential circle, and these friction elements 13 and 14 are also provided. Are alternately symmetrically arranged so that the driven members 6 and 7 of the linear motion portion 3 in friction contact therewith are alternately driven to rotate.

On the other hand, since the spiral grooves 9 and 10 engraved on the outer circumference of the spiral shaft 8 form screws opposite to each other as depicted in Fig. 4, when one driven member 6 is driven to rotate, one helix The groove 9 is pushed by the projection 11 of the driven member 6 so that one piston 25 advances and compresses the inside of one hydraulic cylinder 27 while the other piston 26 on the opposite side is The other hydraulic cylinder 28 is reversed, and at this time, the other driven member 7 is in a state where the gear connection with the driving member 5 is peeled off, but the central shaft hole is projected by the spiral groove 10. As it is promoted, it is idle.

This action continues and as soon as the follower rotation of one follower member 6 is finished, this time the follower rotation of the other follower member 7 begins and one follower member 6 is idling so that the spiral shaft 8 Only the direction remains as it is, the same as the above action is propelled by the other driven member (7) this time the hydraulic pressure is generated in the other hydraulic cylinder (28).

In this way, the hydraulic generator according to the present invention is the hydraulic cylinder (27) (28) because the spiral shaft (8) is a constant linear reciprocating motion in the axial direction, as long as the drive means (1) continues to rotate in one direction Alternately generate hydraulic pressure.

The hydraulic cylinders 27 and 28 are fluid storage tanks 29 (see Fig. 5A) via inlet check valves 31 and 32 provided in the hydraulic cylinders 27 and 28, respectively. 30 may be attached to a hydraulic system connected via the outlet check valves 35 and 36 so that the fluid may be supplied from 30 and connected to the output pipe 34 via the conduit 33. .

Therefore, when one of the hydraulic cylinders 27 is in an uncompressed state, the fluid of the fluid storage tank 29 flows in through the inlet check valve 31 and the outlet side check is performed in the other fluid cylinder 28 which is in a compressed state. The hydraulic pressure is discharged via the valve 35 to be supplied to the output pipe 34 through the conduit 33, and the hydraulic pressure is alternately supplied.

The generated hydraulic pressure alternates the timing of the flow rate Q ₁ coming out of one hydraulic cylinder 27 and the timing of the flow rate Q ₂ coming out of the other hydraulic cylinder 28 as shown in FIG. Therefore, the output flow rate becomes constant, so that high quality hydraulic pressure without pulsation can be obtained.

Here, the flow rate Q ₁ that appears while the rotary drive unit 2 operates to 0.5T

Q ₁ = ωp · ρ / 2π · A.

In addition, since one reciprocating motion per rotation of the rotary drive unit 2 is 2 · Np / Nm = ρ / S, the rotational speed ωρ of the rotary drive unit 2 is

ωρ = ωm · nm / 2 · Np.

Therefore, Q1 = ωm · Nm / (2 · Np) · ρ / 2π · A, and similarly, the flow rate Q ₂ that appears while the rotary drive unit 2 operates from 0.5T to T

Q ₂ = ωm · Nm / (2 · Np) · ρ / 2π · A.

Where ωρ is the rotational speed of the drive member 4 or 5, ρ is the pitch of the spiral groove 9 or 10, A is the area of the piston 25 or 26, and Nm is the gear of the drive member 4 or 5 Np is the number of dimensions of the driven member 6 or 7, S is the stroke of the piston 25 or 26, and ωm is the rotational speed of the rotary drive unit 2.

On the other hand, the total flow rate Qt discharged through the output pipe 34 becomes Q ₁ + Q ₂ and the flow rate is shown as follows.

Therefore, since the rotational speed of the rotational drive unit 2 is proportional to the rotational speed of the drive means 1, and the output flow rate is proportional to the rotational speed of the rotational drive unit 2, when the rotational speed of the drive means 1 is made constant. The output flow rate also becomes constant.

The flow rate in the case of one reciprocation of the pair of pistons 25 and 26 during one rotation of the rotary drive unit 2 becomes the total flow rate Qt = Q ₁ + Q ₂ . And when the pair of pistons 25 and 26 make two reciprocating movements at the time of one rotation of the rotary drive part 2, the dimension Np of the driven member 6 and 7 Np: of the drive member 4 and 5 The dimension Nm = 1: 4, and the pair of driving members 4 and 5 is required.

6 is another embodiment of the hydraulic generator according to the present invention, in which the pistons 25 and 26 are rotated one rotation of the driving means 1 with a pair of two or more driving members 4 and 5. In the city, a reciprocating hydraulic generator is shown.

In the illustrated embodiment, the drive members 4, 5 each have two friction elements 13, 14 in positions opposing the outer circumferential surface, and also have a spiral groove 9 which is engraved on the spiral shaft 8. (10) has a structure formed to cross each other so as to be opposite to each other over the entire length of the spiral shaft (8) as shown in FIG.

In this embodiment, the linear reciprocating motion of the spiral shaft 8 can be lengthened, and even if both driven members 6 and 7 are arranged adjacent to each other, each of the dedicated spiral grooves 9 and 10 will ride. When the follower member 6 is driven to rotate, the other follower member 7 operates in a direction interfering with each other while idling in the opposite direction, so that the spacer S may be omitted.

In addition, the hydraulic generator of the present invention may be arranged in a pair of linear movement portion (3) for the rotary drive unit 2 reciprocating one rotation.

8 shows an example in which a pair of linear motion units 3 are arranged in one rotary drive unit 2 as another embodiment of the present invention.

In this embodiment, a pair of linear motion parts 3 are disposed on the outer periphery of the rotary drive part 2, and each linear motion part 3 is provided with hydraulic cylinders 27 and 28 at both ends thereof. It has one spiral shaft (8).

The hydraulic generator configured as described above operates in the same manner as in the above-described embodiment, but since the hydraulic pressure is generated in the four hydraulic cylinders 27 and 28 in total, when the timing diagram is drawn as shown in FIG. By using the cycles of 0.5T, 0.75T, and T, there is an advantage that it is possible to obtain a high-quality hydraulic pressure that has no pulsation phenomenon or to use two hydraulic lines having a cycle of 0.5T and T.

9 is a further embodiment of the present invention, which shows an example of an oil pressure generating device having three linear motion parts 3. This embodiment has a structure in which three pairs of driven members 6 and 7 are arranged around a pair of drive members 4 and 5 to linearly reciprocate the three spiral shafts 8.

Therefore, the hydraulic cylinders 27 and 28 are also arranged in three pairs to generate hydraulic pressure. In addition, the outer peripheral surface of the pair of drive members 4 and 5 is divided into six equal parts so that the friction elements 13 and 14 are formed only in three places, and these friction elements 13 and 14 are formed at an equilateral angle.

The hydraulic generator of this structure has an advantage that the pulsation of the hydraulic pressure can be further reduced since the number of times of hydraulic generation is at least six times when the rotation driving unit 2 rotates once.

As described above, the hydraulic pressure generating apparatus according to the present invention converts the rotational force of the driving means rotated in a predetermined direction into the linear reciprocating motion at a constant speed by transferring the rotating driving parts to the linear movement part alternately. Since the hydraulic pressure is constantly generated and output at a constant pressure, it is possible to obtain a high quality hydraulic pressure without any pulsation.

Therefore, it can be applied directly to the automation line without having a conventional accumulator or other hydraulic maintenance means.

Although the above-described embodiment has been described as an example in which the hydraulic pressure is generated by the movement of the piston inside the hydraulic cylinder, on the contrary, the rotary driving unit may be driven by rotating the piston by applying hydraulic pressure from the outside of the hydraulic cylinder.

Claims (2)

It holds a plurality of driving members 4 and 5 which are rotated by the driving means 1, and the outer peripheral surfaces of these driving members 4 and 5 are friction elements 13 and 14 which are gears or rubber pads. The friction elements 13 of the one driving member 4 and the friction elements 14 of the other driving member 5 are alternately arranged to be divided into a plurality of parts alternately arranged in a power non-transmission portion having a slightly smaller diameter. A plurality of driven members 6 supported by the rotary drive unit 2, the stoppers 21, 22, and the spacers S, which are in frictional contact with the friction elements 13 and 14, and are driven alternately. (7) and projections (11) (12) formed in the center of these driven members (6) and (7) in spiral grooves (9) (10) engraved in opposite directions on the outer circumference of the spiral shaft (8). Rotating motion / constant, each of which is made up of a rotary motion part 3 which is fitted so that the spiral shaft 8 cannot be rotated by a pair of guiders 17 and 18. Line reciprocating motion conversion devices. It holds a plurality of driving members 4 and 5 which are rotated by the driving means 1, and the outer peripheral surfaces of these driving members 4 and 5 are friction elements 13 and 14 which are gears or rubber pads. The friction elements 13 of the one driving member 4 and the friction elements 14 of the other driving member 5 are alternately arranged to be divided into a plurality of parts alternately arranged in a power non-transmission portion having a slightly smaller diameter. A plurality of driven members 6 supported by the rotary drive unit 2, the stoppers 21, 22, and the spacers S, which are in frictional contact with the friction elements 13 and 14, and are driven alternately. Spiral grooves 9, 10 having projections 11, 12 formed in the center of the plurality of driven members 6, 7 engraved in opposite directions on the outer periphery of the spiral shaft 8; And the linear motion portion 3 which is fitted so as to be respectively fitted so that the spiral shaft 8 cannot be rotated by a pair of guiders 17 and 18, Rotational motion / constant linear reciprocating motion, characterized in that it consists of hydraulic cylinders 27, 28 for generating hydraulic pressure by receiving the pistons 25, 26 mounted on both ends of the shaft 8 in a retractable manner. Hydraulic generator using switching device.