JPH05557B2 - - Google Patents

Description

Detailed Description of the Invention (Field of Industrial Application) The present invention relates to an electromagnetic reciprocating compressor, and particularly to an electromagnetic reciprocating compressor suitable for obtaining highly compressed fluid in a short time. be.

(Prior Art) FIG. 4 is a schematic cross-sectional view showing an example of a conventional electromagnetic reciprocating compressor.

In the figure, piston 1, piston rod 3,
The armature 4 and the armature 4 are each fixed integrally.

The cylinder 2 has a compression chamber 2C and a suction port 2A.
and a discharge port 2B. The piston 1 is slidably inserted into the compression chamber 2C,
In addition, the compression coil spring 5 causes the cylinder 2 to
is biased in the direction.

Arranged around the armature 4 is a fixed iron core 6 having magnetic poles at symmetrical positions and around which a coil 7 is wound.

In the electromagnetic reciprocating compressor having the above configuration, when a half-wave alternating current or pulse current is applied to the coil 7, the piston 1 vibrates in the directions of arrows A and B, and when the piston 1 moves in the direction of A, the fluid is suctioned. It is sucked into the compression chamber 2C from the port 2A, and the piston 1 moves to B.
When it moves in the direction, it is discharged from the discharge port 2B.

Now, in this type of compressor, the discharge performance can be improved by moving the piston head closer to the cylinder head and by increasing the flow rate during low pressure discharge, but the high pressure discharge type compression In the machine, it is necessary to reduce the piston diameter and to move the piston head closer to the cylinder head than in a low pressure discharge type.

The compressor shown in FIG. 4 has a discharge port 2B on the side surface of the cylinder 2 (on the side surface of the compression chamber 2C), so that in the process of sliding the piston head 1' toward the cylinder head 2', The piston head is
The discharge port 2B is closed, the compression chamber 2C is sealed, the fluid pressure in the compression chamber 2C is increased, and the piston head 1' is increased by the action of the fluid cushion.
Collision between the cylinder head 2' and the cylinder head 2' can be prevented.

However, during start-up, the fluid spring action is not sufficient due to the low fluid pressure, so it is inevitable that the piston head will strike the cylinder head. Further, during low-pressure driving, the piston cannot enter into a sufficient resonance state, so a satisfactory discharge flow rate cannot be obtained, and the discharge performance cannot necessarily be said to be good.

Incidentally, an electromagnetic reciprocating compressor is designed so that the natural frequency of the piston and the frequency of the power supply supplied to the coil of the fixed core almost match, and during operation, the piston resonates with the frequency of the power supply. However, it is still insufficient to convert electrical energy into mechanical energy efficiently.

(Problems to be Solved by the Invention) The above-described conventional techniques had the following problems.

Conventional electromagnetic reciprocating compressors generally use a multi-stage compression method to compress fluid to a high degree, but since the compression chambers provided in each cylinder are all independent, low-pressure drive is not possible. Sometimes the above-mentioned striking of the cylinder head by the piston head is unavoidable.

In addition, when the compression ratio of the fluid is increased, the flow rate decreases, so conventional multi-stage compression type compressors are designed to prevent piston head impact, which is a factor that improves discharge performance, and to prevent piston head impact during low-pressure discharge. It was not possible to increase the flow rate sufficiently.

(Purpose) The present invention aims to compensate for the deterioration in discharge performance caused by the lack of fluid spring action and the inability of the piston to achieve sufficient resonance during low-pressure driving in conventional electromagnetic reciprocating compressors, and to The present invention aims to solve the problem of increasing the discharge flow rate at the same time, maintaining the required discharge flow rate after reaching a set pressure, and preventing the piston head from hitting the cylinder head.

(Means for Solving the Problems) In order to solve the above-mentioned problems, the present invention provides a piston, a cylinder, etc., which have at least two compression chambers with the same fluid suction timing and fluid discharge timing. When the pressure of the fluid discharged from the compression chambers is low, such as during startup, the compression chambers are connected in parallel until a predetermined pressure is reached, and the pressure is increased to a predetermined pressure. When the pressure reaches a certain level, the switching valve is controlled in accordance with the signal from the pressure sensor to sequentially disconnect the compression chambers.

(Function) When the pressure of the fluid to be discharged is low, such as during startup, multiple compression chambers are connected in parallel by fluid pipes, and fluid is repeatedly sucked and discharged at the same time.
While supplementing the discharge flow rate that is insufficient with only one compression chamber with the pressurized fluid discharged from another compression chamber, the compression ratio is gradually increased, and when a predetermined pressure is detected by the pressure sensor, the fluid that communicates with some or one of the compression chambers is gradually increased. The pipeline is closed and the fluid continues to be pressurized at the required discharge flow rate, and when the pressurized fluid is consumed and the pressure drops below the set pressure, the closed fluid pipeline is reopened and the original The state is restored and this action is repeated thereafter.

(Example) The present invention will be described in detail below with reference to the drawings.

FIG. 1 is a schematic diagram showing the configuration of an embodiment of the present invention.

In FIG. 1, the piston of the electromagnetic reciprocating compressor according to the present invention is composed of a first piston 12 and a second piston 13. The first piston 12 has a smaller diameter than the second piston 13, and is fixed and integrated on the same side of the piston rod 3 so as to share a central axis, and the pressure receiving area of the second piston 13 is It is formed larger than that of one piston 12.

The cylinder 21 includes a first cylinder 26 and a second cylinder 27 having different diameters so that the first piston 12 and the second piston 13 individually compress the fluid. The first cylinder 26 and the second cylinder 27 each have an inlet port 22, 24 and a discharge port 2 with valves.
3, 25, but at least the discharge port 2
3 and 25 are provided on the cylinder wall.

Note that the suction port 23 is connected to the cylinder heads 26', 2
7', the cylinder wall, or the piston heads 12', 13'.

The valved discharge ports 23 and 25 are individually connected through fluid pipes 51 and 52, and the fluid pipes 51 and
52 are integrated by a fluid line 50 leading to a pressure tank or pressurized air consumption source (neither shown).

The switching valve 31 is provided in the middle of the fluid pipe line 52, and is, for example, a three-way valve including an input port 31A, an output port 31B, and a discharge port 31C.
It is a port solenoid valve.

In FIG. 1, the input port 31A and the output port 31B of the switching valve 31 are normally in a connected state, and when the electromagnet is energized, the input port 31A and the discharge port 31 are connected.
C becomes connected.

The input port 31A is connected to the discharge port 25 of the cylinder 21, and the output port 31B is connected to the discharge port 23 of the cylinder 21, a pressure tank, etc. through the fluid conduits 50, 51, and 52.

The pressure sensor 32 is provided in the fluid conduit 50,
The pressure of the fluid in the fluid pipeline 50 from the discharge port 23 and the output port 31B to the pressure tank etc. is set to a preset pressure P1 (P1<P3, where the pressure
P3 is the maximum pressure obtained when the discharge ports 23 and 25 are connected in parallel).

When the pressure sensor 32 detects the set pressure P1, the control device 33 energizes the electromagnet of the switching valve 31 so that the input port 31A becomes the discharge port 31C.
Switch so that it is connected to the side.

In one embodiment of the present invention having the above configuration, when a half-wave AC or pulse current is applied to the coil 7 wound around the fixed iron core 6, the excitation of the fixed iron core 6 causes the piston to move in the direction of arrow A (the first 1), when the fixing device 6 is demagnetized, it moves in the direction of arrow B by the elastic force of the compression coil spring 5, and by repeating this, the piston vibrates.

Then, the first piston 12 and the second piston 1
3, the fluid is transferred to the suction ports 22, 24.
It is sucked into the first cylinder 26 and the second cylinder 27, compressed, and discharged from the discharge ports 23 and 25.

As described above, the input port 31A and the output port 31B of the switching valve 31 are always connected, so that the first cylinder 26 and the second cylinder
The cylinders 27 are connected in parallel, so that the pressurized fluid discharged from the outlets 23, 25 of both cylinders flows through fluid lines 51, 52 and 50 to a pressure tank or directly to a source of consumption of pressurized fluid.

Therefore, for example, the amount of fluid discharged toward the pressure tank is the sum of the amounts of fluid that are individually pressurized and discharged within the compression chambers a and b of the first and second cylinders 26 and 27.

Next, the pressure within the fluid conduit 50 is set to a set pressure.
When P1 is reached, the pressure sensor 32 detects the pressure.
Upon sensing P1, the control device 33 energizes the electromagnet of the switching valve 31, and connects the input port 31A and the discharge port 31.
Switch so that C is connected.

Thereby, the compression chamber b of the second cylinder 27 is opened, and only the compression chamber a of the first cylinder 26 continues to be connected to the pressure tank or the pressurized fluid consumption source.

Next, the characteristics of one embodiment of the present invention will be explained using FIGS. 2 and 3.

FIG. 2 is a characteristic curve showing the relationship between discharge flow rate and pressure in one embodiment of the present invention.

In FIG. 2, the broken line L and the curve M are the characteristic curves of the first cylinder 26, and the curve Q and the broken line R are the characteristic curves of the first cylinder 26,
A characteristic curve when the second cylinders 26 and 27 are connected in parallel is shown. For example, the pressure P1 at the intersection of the curve LM and the curve QR is the pressure sensor 32.
This is the set pressure detected by.

Therefore, the curve LM and the curve Q shown in FIG.
- When the switching valve 31 is switched at the pressure P1 at the intersection of -R, the subsequent characteristic curve will be the characteristic curve M for the first cylinder 26, and the discharge flow rate will be the same as the discharge pressure.
Even if it rises from P1 to P2, it does not decrease sharply like curve R.

In addition, if the set pressure is lower than P1 above,
After the discharge flow rate is rapidly decreased as Q ₀ →L ₀ shown in Figure 2, the pressure and flow rate change along the curve L-M, and when they are greater than P1, R ₀ →M ₀ in the same figure.
Accordingly, after the discharge flow rate is rapidly increased, the pressure and flow rate change along the curve M.

As described above, in one embodiment of the present invention, the flow rate is large when the pressure is low, and therefore piston shock does not occur at startup, and after reaching the set pressure P1, the flow rate does not decrease rapidly, which is different from the conventional electromagnetic reciprocating pump. Compared to dynamic compressors, fluid can be highly compressed in a short time.

FIG. 3 is a characteristic curve showing the relationship between discharge pressure and operating time in one embodiment of the present invention.

In FIG. 3, the curve Q' shows the characteristics of one embodiment of the present invention, the broken line curve U shows the characteristics when the first cylinder 26 and the second cylinder 27 are connected in parallel, and the broken line curve L' shows the characteristics when the first cylinder 26 and the second cylinder 27 are connected in parallel. , first cylinder 26
It shows the characteristics when only is working.

Therefore, when comparing curves Q' and L', characteristic curve Q' takes longer time to reach high pressure fluid due to the present invention.
It is shortened to T ₂ −T ₁ (=T ₂ ′−T ₁ ′), and the set pressure can be increased in a short time.

(Modifications) (1) In the above description, the pressure in the fluid pipeline 50 from the first cylinder 26 and the second cylinder 27 to the pressure tank or pressurized fluid consumption source is
When the set pressure P1 is reached, the compression chamber b of the second cylinder 27 is opened, and only the compression chamber a of the first cylinder 26 continues to be connected to the pressure tank or pressurized fluid consumption source. The invention is not particularly limited to this, but if the locking pressure is to be kept low, the first cylinder 2
It is also possible that the compression chamber a of the second cylinder 27 is opened and only the compression chamber b of the second cylinder 27 is subsequently connected to a pressure tank or a pressurized fluid consumption source.

(2) The electromagnetic reciprocating compressor has two cylinders 2.
6 and 27 on the same side, the present invention is not particularly limited to this, and any fluid compression means that simultaneously performs suction and compression may have three or more cylinders. may be configured. That is, the individual cylinder heads may be formed to have different pressure-receiving areas or to have the same area.

In addition, although the pistons 12 and 13 have been described as having different diameters arranged in a stepped shape, a plurality of normally used cylindrical piston heads of the same diameter or different diameters and a plurality of piston heads that house the pistons may be used. It is also possible to provide independent fluid compression means consisting of a plurality of cylinders, suction ports and discharge ports, and to drive each piston of the fluid compression means with one armature.

In this case, as in the previous embodiment, the compression chambers are sequentially separated each time the fluid pressure increases to the set pressure, and each time the fluid pressure decreases to the set pressure as the pressurized fluid is consumed, the compression chambers are sequentially compressed. All you have to do is connect the rooms.

(3) The pressure sensor 32 is connected to the discharge ports 23 and 2.
5, the pressure of the fluid in the fluid conduit 50 connected to a pressure tank or a source of pressurized fluid has been described as being detected, but the pressure of the fluid introduced into the pressure tank may also be detected.

(4) Although the discharge ports 23 and 25 have been described as being provided on the side surfaces of each compression chamber, the present invention is not limited to this, and the discharge ports 23 and 25 may be provided on each cylinder head 26', 27'. Also good.

(5) Although the suction ports 22 and 24 have been described as being provided on the side surfaces of each compression chamber, they may also be provided on each cylinder head 26', 27' in the same way as the discharge ports 23 and 25. Alternatively, it may be provided on the piston head.

(Effects of the Invention) According to the present invention, the following effects are achieved.

That is, the electromagnetic reciprocating compressor of the present invention, which has at least two fluid compression means that repeat suction and compression at the same time, operates by connecting the compression chambers in parallel when the pressure of the fluid is low, so that the set pressure is obtained quickly, and thereafter the compression chambers are sequentially separated, so that even if the pressure of the fluid to be discharged increases, the amount of fluid to be discharged will not decrease rapidly. Therefore, (1) Even if the discharge fluid is highly compressed, the lock pressure becomes high, so a stable discharge amount can be obtained.

(2) Since the discharge flow rate is high when the pressure of the discharge fluid is low, the piston head does not hit the cylinder head, and energy loss and noise can be prevented.

Further, at this time, since the degree of decrease in the spring constant of the fluid spring due to the fluid in the compression chamber becomes small, the degree of change in the natural frequency of the vibration system of the electromagnetic reciprocating compressor of the present invention also becomes small. Therefore, the vibration system of the electromagnetic reciprocating compressor can enter a resonant state in a relatively short time, so that the electrical energy supplied to the coil of the fixed core can be effectively utilized.

[Brief explanation of the drawing]

Fig. 1 is a schematic diagram showing the configuration of an embodiment of the present invention, Fig. 2 is a characteristic curve showing the relationship between discharge flow rate and pressure in an embodiment of the invention, and Fig. 3 is a diagram showing the relationship between discharge flow rate and pressure in an embodiment of the invention. A characteristic curve showing the relationship between discharge pressure and operating time. FIG. 4 is a schematic cross-sectional view showing an example of a conventional electromagnetic reciprocating compressor. 4... Armature, 5... Compression coil spring, 6... Fixed iron core, 7... Coil, 12...
First piston, 12'...Piston head, 13
...Second piston, 13'...Piston head,
21...Cylinder, 22, 24...Suction port, 2
3, 25...discharge port, 26...first cylinder, 2
6'... Cylinder head, 27... Second cylinder,
27'...Cylinder head, 31...Switching valve, 3
2...Pressure sensor, 33...Control device, 50,5
1, 52...Fluid pipe line, a, b...Compression chamber.

Claims (1)

[Scope of Claims] 1. A fluid compression means having a piston, a cylinder having a compression chamber for accommodating the piston, an inlet for introducing fluid into the compression chamber, and an outlet for discharging fluid from the compression chamber; An electromagnetic reciprocating compressor comprising an armature that is mechanically and integrally fixed to a piston, and an electromagnetic device that energizes the armature, wherein the fluid compression means has the same fluid suction timing and compression timing. at least two sets of fluid pipes, which connect the discharge ports of each compression chamber of the fluid compression means in parallel to a pressure tank or a pressurized fluid consumption source; and a fluid pipe line for detecting the pressure of the fluid in the fluid pipe line. a pressure sensor disposed in a fluid line between a pressure measurement point in the fluid line and at least one compression chamber; and a control for controlling the switching valve in response to a signal from the pressure sensor. further comprising a device, the control device sequentially disconnects the compression chambers as the pressure increases, and connects the compression chambers sequentially as the pressure decreases after the fluid pressure increases. An electromagnetic reciprocating compressor, characterized in that the switching valve is controlled so as to.