JPH02180382A - One-way valve device - Google Patents

Abstract

PURPOSE:To make it possible to use the device in the title in substitute for the inlet valve or the exhaust valve of a pump or the like by providing a piston ring between a piston and a cylinder with a valve function to positively let operating fluid flow in one direction while restraining operating fluid from leaking in the reverse direction. CONSTITUTION:A sealing property is heightened as a ring 5 pressure-contact to the surface opposite to a peripheral groove 3a with sliding frictional resistance between the periphery of piston rings 4 and 5 and the inner wall of a cylinder 2 during the compression stroke. Additionally, as the pressure at the side of a discharge chamber 7 presses the piston rings 4 and 5 on the cylinder 2 through a tension ring 6, the sealing property between the piston rings 4 and 5 and the cylinder 2 is heightened. Accordingly, it is possible to prevent fluid from leaking from the discharge chamber 7 to the atmospheric space and it is possible to discharge fluid after a lead valve 10 is opened. On the other hand, the piston ring 4 makes pressure-contact to the surface opposite to the peripheral groove 3a with the frictional resistance between the piston rings 4 and 5 and the cylinder 2 at the time of expansion stroke, and the opposite side is separated and a clearance is generated. Accordingly, when the capacity of the discharge chamber 7 increases because of the movement of the cylinder 2 and the pressure decreases to a lower level than that in the space on the opposite side, operating fluid flows to the side of the discharge chamber 7 through grooves 6a and 4a from a clearance between the piston ring 5 and the peripheral groove 3a.

Description

[Detailed Description of the Invention] <Industrial Application Field> The present invention is applied to various types of pumps and engines that include a cylinder and a piston, and is installed between the inner wall of the cylinder and the outer wall of the piston, and The present invention relates to a one-way valve device that facilitates the flow of fluid between two spaces in only one direction.

<Prior Art> Conventionally, a compressor must be equipped with a suction valve, and a vacuum pump must be equipped with an exhaust valve.

In addition, in a Stirling engine, the gas sealed within the system is repeatedly compressed and expanded, so gas leaks little by little from the compression chamber with each cycle, and as the amount of gas leakage increases, the range of pressure change in the compression chamber decreases. This reduces the amount of work done, which in turn reduces output, so multi-stage piston rings are installed to prevent gas leaks.

Also, in reciprocating internal combustion engines, etc., leakage of combustion gas from the combustion chamber leads to a decrease in power, and since this combustion gas is harmful, piston rings are similarly installed in multiple stages to prevent gas leakage from the combustion chamber. We are trying to suppress this issue as much as possible.

<Problems to be Solved by the Invention> However, the suction valve and exhaust valve in the compressor and vacuum pump also require a drive mechanism, resulting in a complicated structure, an increase in size, and an increase in cost.

On the other hand, in the Stirling engine, the current piston ring causes a large amount of gas leakage, and when the power is used, the output decreases significantly. In particular, since the Stirling engine has a sealed cycle, it is desirable to operate without lubrication due to contamination of the working gas and problems with the heat exchanger, but in this case, gas leakage increases and output decreases.

Similarly, in the case of internal combustion engines, the piston rings have a limited ability to prevent gas leakage, resulting in a significant drop in output due to an increase in harmful blow-by gas.

The present invention was made in view of such conventional problems, and improves the structure of the piston ring etc. provided between the piston and the cylinder to suppress leakage of working fluid in one direction as much as possible. At the same time, the configuration is based on a completely new idea of having a valve function that actively allows working fluid to flow in the reverse direction.It is an innovative design that not only solves the various problems mentioned above, but can also be applied over a wide range of areas. The purpose of the present invention is to provide a one-way valve device with such functions.

Means for Solving the Problems> For this reason, the present invention provides a valve body that slides in pressure contact with one of the outer wall of a piston that moves within a cylinder and the inner wall of the cylinder by an elastic force, and the other is formed with a valve body that slides in pressure contact with one of the outer wall of a piston that moves within a cylinder and the inner wall of the cylinder. The valve body is inserted into a groove formed on the valve body to form two spaces on both sides of the valve body, while a gap is formed between the valve body and the groove on the side opposite to the sliding side of the valve body and in the direction in which the two spaces are lined up. The opposing surfaces of the valve body and groove on one side in the direction in which the two spaces are arranged are in contact with each other, so that the space on one side and the sliding side of the valve body are separated from each other. The surface shape has a high sealing property that blocks the gap on the opposite side, and the opposing surfaces on the other side are connected to the space on the other side and the side opposite to the sliding side of the valve body, both when they are in contact and when they are not in contact. The configuration is such that the surface is formed into a surface shape that maintains a large gap between the gap and the gap.

Furthermore, a second invention includes a valve body that slides in elastic pressure contact with one of the outer wall of a piston moving in a cylinder and an inner wall of the cylinder, and is inserted into a groove formed in the other. On both sides, two spaces are formed in which the magnitude relationship of pressure is reversed by the movement of the piston, and from between the facing surfaces of the valve body and the groove on one side in the alignment direction of the two spaces, to the valve body sliding side. a first gap forming means that forms and maintains a large gap communicating between the opposing surfaces on the opposite side, and a part of the opposing surface between the valve body and the groove on the other side in the alignment direction, which is constantly pressed by elastic force. the pressure contact means, and when the pressure in the space on the other side is greater than the pressure in the space on the opposite side, by receiving the pressure and moving the pressure contact part to the side opposite to the sliding side of the valve body, and second gap forming means for forming a gap communicating from a side closer to the valve body sliding side than the press-contact portion to a gap on one side in the arrangement direction of the spaces.

Effect> In the first invention, when the valve body and the groove are in contact with each other in the direction in which the two spaces are lined up, and the opposite surfaces are formed in a surface shape with high sealing properties, the opposite side Since there is a gap between the surfaces that leads to the gap on the opposite side of the valve body from the sliding side, the pressure that enters the gap on the opposite side pushes the valve body toward the sliding side and the sliding surfaces are mutually connected. The sealing performance of the product is strengthened. Therefore, in this case, the sealing properties between the valve body and the groove and between the sliding surfaces of the valve body are enhanced, and as a result, the flow of fluid between the two spaces is effectively prevented.

On the other hand, contrary to the above, when the facing surfaces of the valve body and the groove are in contact with each other on the side where a gap is always maintained, the gap between the sliding side of the valve body and the opposite side is Since gaps are formed leading to the space, fluid can easily flow between the two spaces through these gaps.

In the second invention, by the first gap forming means, a large gap is always formed on one side in the direction in which the two spaces of the valve body and the groove are lined up, leading to the gap on the sliding side of the valve body and the gap on the opposite side. has been done. On the other hand, the opposing surfaces on the other side in the alignment direction are always in slight (and partially pressed) contact with each other due to elastic force by the pressure contact means.

Therefore, if the pressure in the space on one side is higher than the pressure in the space on the other side, the pressure difference between the spaces will cause the facing surfaces of the valve bodies on the other side in the alignment direction to be brought into pressure contact with each other. The force is added to the pressure contact force by the pressure contact means to ensure sealing between the valve body and the groove, and the pressure on the high pressure side is introduced to the gap on the side opposite to the sliding side of the valve body, thereby increasing the pressure of the valve. Since the body is pressed against the sliding side, the sealing performance between the sliding surfaces is also improved, so that fluid flow between the two spaces is prevented.

In addition, when the moving direction of the piston is reversed from the above state, the sliding frictional resistance of the valve body acts in the direction of pressing the valve body against one side in the direction in which the spaces are arranged, but even in this case, the valve body is pressed by the pressure contact means. Since at least a portion of the body is pressed against the body by elastic force to ensure sealing performance, fluid on the high pressure side can be prevented from leaking to the low pressure side.

Further, when the pressure relationship between the two spaces is reversed due to the cyclic movement of the piston, the second gap forming means receives the pressure of the high pressure side space and moves the pressure contact portion of the valve body by the pressure contact means to the valve body sliding portion. By moving it to the side opposite to the moving side, a gap communicating with the gap on one side in the arrangement direction of the spaces is formed on a side closer to the valve body sliding side than the press-contact portion.

Thereby, the fluid on the high pressure side easily flows into the low pressure side space through the gap.

<Example> Embodiments of the present invention will be described below based on the drawings.

FIG. 1 shows an embodiment of the first invention, in which a one-way valve device according to the invention is applied to a compressor.

In the figure, a reed valve lO that opens only in one direction of the discharge port is installed at the discharge port 1, and a one-way valve device according to the present invention is installed between the cylinder 2 and the piston 3 inserted into the cylinder 2. be done. That is, the peripheral wall of the piston 3 has a peripheral groove 3a.
Two piston rings 4, 5 are formed in the circumferential groove 3a, and two piston rings 4, 5 are mounted on top of each other in the axial direction of the piston 3, and two piston rings 4, 5 are mounted on the inner peripheral surface side of these piston rings 4.5. A tension ring 6 is inserted into the tension ring 6 to force the outer circumferential surface of the cylinder 5 to expand so as to elastically press the outer peripheral surface of the cylinder 2 against the inner wall of the cylinder 2. Note that the piston ring 4.5 and the tension ring 6 have an abutment, which can be expanded to fit into the circumferential groove 3a.

The piston ring 4.5 and the tension ring 6 constitute a valve body in the first invention, and a discharge chamber 7 is provided on both sides of the valve body through a gap between the cylinder 2 and the piston 3.
A side space and an opposite side space are defined, and the circumferential groove 3a also constitutes the groove in the first invention. Also, the thickness in the axial direction of the overlapping piston rings 4 and 5, and the tension ring 6
The axial thickness of is narrower than the axial width of the circumferential groove 3a, and there is a gap CI between the tension ring 6 and the circumferential groove 3a.
is formed. That is, each member is formed to a size that provides a gap between the valve body and the groove on the sliding side of the valve body and in the direction in which the two spaces are lined up.

Furthermore, the piston ring 4 and the tension ring 6 have
Grooves 4a are provided at a plurality of locations in the radial direction on the discharge port 1 side.

6a is formed, and these grooves 4a, 6a allow the facing surfaces of the piston ring 4 and tension ring 6 on the side where the grooves are formed and the circumferential groove 3a to connect to the space on the discharge chamber 7 side both when they are in contact and when they are not in contact. The shape is such that the gap communicating with the gap CI is kept large.

On the other hand, the piston ring 5 is connected to the piston ring 4 and the circumferential groove 3.
Both side surfaces facing the inner wall of a are formed as flat surfaces, and the center part of the annular member is cut in the axial direction leaving a part in the circumferential direction as shown in FIG. A joint 5a that cuts a part of the outside and a part of the inside of the cut surface in the circumferential direction
, 5b are formed at positions shifted by approximately 180 degrees. As a result, the opposing surfaces between the piston rings 4 and 5 and the opposing surfaces between the piston ring 5 and the circumferential groove 3a are formed in a shape that provides a high sealing performance during contact. Alternatively, instead of the piston ring 5, a spiral ring 5' which is radially stacked and wound in a spiral shape multiple times as shown in FIG. A similar effect can be obtained.

The operation of a compressor equipped with such a one-way valve device will be explained.

During the compression stroke in which the piston 2 moves in the direction of the discharge chamber 7, as shown in FIG. The opposite side surface is in pressure contact with the opposing surface of the circumferential groove 3a, thereby improving the sealing performance of the pressure contact portion.

In addition, the pressure on the discharge chamber 7 side is high, and this pressure
, 6a to the gap C2, and the tension ring 6
Since it acts in the direction of pressing the piston ring 4.5 toward the inner wall of the cylinder 2 through the piston ring 4.5, the sealing performance of the sliding surface between the piston ring 4.5 and the inner wall of the cylinder is also improved.

Therefore, leakage of the working fluid from the discharge chamber 7 to the atmospheric space side during such a discharge stroke can be effectively prevented, and the reed valve 1
0 can be pushed open and the working fluid can be efficiently discharged.

On the other hand, during the expansion stroke in which the piston 2 moves to the side opposite to the discharge chamber 7, the piston ring 4
, Due to the sliding friction resistance between the outer peripheral surface of 5 and the inner wall of cylinder 2,
The side surface of the piston ring 4 on the discharge chamber 7 side is in pressure contact with the opposing surface of the circumferential groove 3a, and the discharge chamber 7 between the piston ring 5 and the circumferential groove 3a
The opposing surfaces on the opposite side are separated from each other, creating a gap.

Therefore, when the displacement of the piston 2 expands the volume of the discharge chamber 7 and lowers the pressure from the space on the opposite side, the working fluid in the space on the opposite side flows from the gap between the piston ring 5 and the circumferential groove 3a to the gap C3 and further. is groove 6 of tension ring 6
a. It easily flows toward the discharge chamber 7 through the groove 4a of the piston ring 4.

Thereby, the working fluid can be sucked into the discharge chamber 7 through the one-way valve device during the expansion stroke, and there is no need to provide a separate suction valve, and it is only necessary to install a set of one-way valve devices. It is inexpensive, reduces friction loss, and reduces power consumption.

Further, the inverse characteristic of such a one-way valve device can be used to apply it to a vacuum pump.

FIG. 2 shows an example applied to a vacuum pump,
The suction port 11 is provided with a reed valve 15 that opens only in the direction of the vacuum chamber 14 defined by the cylinder 12 and the piston 3.
is installed, and the circumferential groove 13 formed in the circumferential wall of the piston 13
In the case of the compressor, the piston rings 4, 5 and the tension ring 6 are installed with the left and right sides reversed.

In this case, during the suction stroke in which the piston 2 moves to the side opposite to the vacuum chamber 14, the reed valve 15 is opened and gas ( During the exhaust stroke in which the piston 13 moves toward the vacuum chamber 14, the gas sucked into the vacuum chamber 14 is discharged to the atmospheric pressure space via the one-way valve device.

In the case of such a vacuum pump as well, the conventionally necessary exhaust valve is no longer necessary, and a sufficient function can be obtained just by installing one set of one-way valve devices, so that it is inexpensive, has low friction loss, and can reduce power consumption.

Furthermore, even if a spiral ring 4', which is stacked in the axial direction and wound multiple times in a spiral shape, is used instead of the piston ring 4, as shown in Fig. 3, a gap is ensured when making contact with the facing surface of the circumferential groove 3a. You can get the same effect.

Figure 4 shows a rotation speed of 60 Orp using a single cylinder compression tester.
In the figure, ■ shows the case where a conventional piston ring with no fluid flow direction was used, and ■ shows the case where the piston ring 4°5 and the tension ring 6 were used.
The case of the first embodiment is shown in which the compressor is fitted into the circumferential groove 3a with a compressor function. As is clear from the figure, in the case of this example device, high pressure can be obtained in the compression stroke due to the high sealing function, while in the expansion stroke, the characteristic is that the inflow of air is good and the negative pressure can be kept low. There is.

In these embodiments, the valve body was constructed using a total of three ring members, two piston rings and one tension ring, but by increasing the width of the piston ring 4 and making the abutment step-like, the sealing performance could be improved. It is also possible to omit the piston ring 5 and to omit the tension ring 6 by forming the piston ring 4 itself from a material with strong expansion elastic force.

FIG. 5 shows an embodiment in which the one-way valve device according to the first invention is used in a rotary compressor.

In the figure, a rotor 52 that rotates around a central axis 53 of the cylinder 51 with a part of its outer peripheral surface sliding on the inner peripheral surface of the cylinder 51 is installed in a cylinder 51, and a slit 58 formed on the cylinder 51 side is shown. A reciprocating vane 57 is provided. The vane 57 is connected to the end surface 64 of the slit 58.
The tip of the coil spring 59 is pressed against the outer circumferential surface of the rotor 52 by a coil spring 59, which has one end engaged with the coil spring 59. At the same time as the gas is sucked in, the gas is discharged from the discharge chamber 66 configured in the same manner. The discharge port 55 is provided with a reed valve 54 that opens only in the direction of the discharge port 55 .

The vane 57 is the valve body in the first invention, and the slit 58
constitutes a groove, a plurality of notches 57a are intermittently formed in parallel with the reciprocating direction of the vane 57, and the side surface of the suction chamber 65 is flat with high sealing performance when in contact with the opposing surface of the slit 58. It is formed into a shape.

Next, the effect will be explained.

Atmospheric air is sucked in through the suction port 56 to expand the volume of the suction chamber 65, which has a pressure substantially equal to atmospheric pressure, while simultaneously discharging gas from the discharge chamber 66 and reducing the volume.

From this state, the rotor 52 rotates clockwise so that the volume of the discharge chamber 66 further decreases, and when the rotor 52 comes into contact with the discharge port 55, the discharge stroke ends.

The next discharge stroke is started from the time when the discharge stroke ends. Further, the rotor 52 continues to rotate, and the rotor 52 continues to rotate.
The suction stroke continues until the suction port 2 contacts the suction port 56, and from the time the suction stroke ends, the suction stroke is started in the same way as the above-mentioned discharge stroke.

In this way, in rotary compressors,
The suction stroke and the discharge stroke are performed continuously.

To explain the operation of the one-way valve device under such operation, the pressure A on the discharge chamber 66 side becomes higher than the pressure (atmospheric pressure) B in the suction chamber 65 on the opposite side, so the vane 57 It moves to the opposite side and comes into pressure contact with the slit side surface 67, improving the sealing performance between the contact surfaces.

As a result, a gap C2 is formed inside the slit 58 on the opposite side of the sliding side of the vane 57 with the rotor 52 through the gap formed between the slit 58 and the side surface of the vane 57 on the discharge chamber 66 side. The pressure is maintained at approximately the same pressure as the pressure in the discharge chamber 66. Since a force proportional to the pressure acts as a force when the vanes 57 are pressed against the rotor 52, the sliding surfaces are also brought into pressure contact with each other with an appropriate force, resulting in good sealing performance.

Also, due to a change in the discharge pressure in the discharge chamber 66, the vane 57
Even if the gap C! is inclined with respect to the axial direction of the slit 58, the gap C! Since the discharge pressure is reliably guided to the position, stable pressing force is obtained, and stable sealing performance is obtained when pulling.

By the way, in the first invention, especially when applied to a piston that reciprocates, when the side where the gap amount is always kept large is high pressure, the direction of movement of the piston is switched and immediately after it moves to the low pressure side. While the pressure magnitude relationship has not been reversed yet, the fluid on the high pressure side leaks to the low pressure side through the gap.

This is because when the cycle motion frequency of the piston is low, such as during start-up, the leakage flow rate accounts for a large proportion of the fluid pumping flow rate, so the efficiency decreases a little, but if the frequency is lowered, Since the decrease in efficiency is suppressed to a very small extent, it is possible to reduce the efficiency by
This poses no problem in terms of efficiency for compressors and vacuum pumps that operate at medium to high speeds (00 rpm) or higher.

However, leakage from one-way valve devices is not a problem if the working fluid leaks into the atmosphere such as air, or if the working fluid circulates in a sealed system such as in a heat pump, but this is not a problem for internal combustion engines, etc. If the
In this case, the efficiency decreases significantly, so it is necessary to maintain high sealing performance immediately after the piston movement direction is switched. In such a case, the second invention is applied.

FIG. 6 shows an embodiment of the second invention.

In the figure, a circumferential groove 31 formed in the circumferential wall of the piston 31
Bias rings 33, 34 whose outer circumferential surfaces slide on the inner wall of the cylinder 32 are mounted on the cylinder 32 in an overlapping manner in the axial direction. 32 and are formed on tapered surfaces 33a, 34a whose inner diameters continuously decrease in the direction of the compression chamber 35 defined on the right side in the figure.

Furthermore, a plurality of grooves 33b and 34b are formed radially in the radial direction on the side surface of the bias ring 33 on the compression chamber 35 side and on the side surface of the bias ring 34 on the side opposite to the compression chamber 35, respectively.

Furthermore, on the inner peripheral side of the bias ring 33, 34,
Bias ring 3 formed on tapered surfaces 36a and 37a whose outer peripheral surfaces are in pressure contact with the inner peripheral surfaces of bias rings 33 and 34.
6.37 are mounted one on top of the other in the radial direction.

A plurality of grooves 36b are formed radially in the radial direction on the side surface of the bias ring 36 on the compression chamber 35 side.
The outer peripheral surface of 7 is a pressure receiving surface 3 that receives the pressure of the space opposite to the compression chamber 35 through the circumferential groove 34b of the bias ring 34.
7b is formed. Also, bias ring 36.3
7, the side surface 36C137c opposite to the compression chamber 35 and the circumferential groove 3
The opposing surfaces 1a are formed into flat surfaces that provide high sealing performance when they come into contact with each other.

The amount is also expanded to the inner peripheral surface side of the bias ring 36 on the inner peripheral side so that the outer peripheral surface of the bias ring 33, 34 is pressed against the inner wall of the cylinder 2 with elastic force via the bias ring 36, 37. By pressing the tapered surfaces 36a and 37a of the bias rings 36 and 37 against the tapered surfaces 33a and 34a of the bias rings 33 and 34, the compression chamber 3 is formed in the bias rings 36 and 37.
A tension ring 38 is inserted into the tension ring 38, which applies a component force in the opposite direction to that of the tension ring 38 to press the side surface into contact with the circumferential groove 31a.

Note that the bias rings 33, 34, 36, and 37 are each formed with abutments, and are mounted so that these abutments are spaced apart in the circumferential direction to prevent leakage from the abutments.

Next, the function of this product will be explained.

During the compression stroke in which the piston 31 moves toward the compression chamber 35, the side surface of the bias ring 34, 36, 37 on the opposite side to the compression chamber 35 comes into pressure contact with the side surface of the circumferential groove 31a on the opposite side to the compression chamber 35, and in this state. , the high pressure fluid in the 35 compression chambers flows through the groove 33b.
and the tension ring 38 and the circumferential groove 31 via the groove 36b.
It flows into the gap C5 with a. As a result, in addition to the expansion urging force of the tension ring 38, the bias ring 36.3
7, the force pressing the outer circumferential surface of the bias ring 33.34 against the inner wall of the cylinder 2 is strengthened, and the reaction force from the tapered surface of the bias ring 33.34 causes the side surface 36c37c of the bias ring 36.37 to be pushed into the circumferential groove 31a. The force that presses against the surface is strengthened.

Therefore, the higher the pressure P on the compression chamber side, the more
The bias ring 33, 34, 36, 37 improves the sealing performance and can reliably prevent leakage to the low pressure side space.

On the other hand, during the expansion stroke in which the piston 31 moves to the side opposite to the compression chamber 35, the bias rings 33, 34 move within the circumferential groove 31a toward the compression chamber 35 due to sliding frictional resistance with the inner wall of the cylinder 32, and the bias rings 33, 34 The side surface is the circumferential groove 31
A is pressed against the opposing surface of the compression chamber 3 through the circumferential groove 31a.
Communication between the 5 side and the gap Off is maintained.

Here, for example, during the combustion stroke of an internal combustion engine, even though it is an expansion stroke, the pressure P on the compression chamber 35 side is overwhelmingly higher, and therefore, due to the high pressure that has entered the gap C3,
Bias ring 33.34.36.3 proportional to the pressure
Since the sealing performance is improved by 7, it is possible to reliably prevent combustion gas from leaking into the low-pressure side space.

Furthermore, during the intake stroke immediately after the end of the exhaust stroke of the internal combustion engine, the compression chamber 35 side pressure P+ may be slightly higher, but even in this case, the bias ring 36° 37
In addition to the pressure introduced into the gap C3 from the side, the tension ring 3
8, the diameter is expanded while receiving the reaction force from the tapered surface, and the side opposite to the compression chamber 35 is formed into the circumferential groove 31a.
Since the pressure contact state is maintained, leakage to the low pressure side space can be reliably prevented.

On the other hand, in the subsequent suction stroke, when the pressure P2 in the space opposite to the compression chamber 35 becomes higher than the pressure P in the compression chamber 35, the pressure P2 on the high pressure side acts on the pressure receiving surface 37c of the bias ring 37. The bias rings 37 and 36 are deformed in the direction of decreasing their diameters, and as a result, the bias rings 37 and 36 are
3.34 Taper surfaces 33a, 34a and bias ring 3
A gap is formed between the tapered surfaces 35a and 37a of 6.37, and the working fluid on the high pressure side flows into the compression chamber 35 through this gap.
Flow into the side. Further, a part of the high-pressure side working fluid flows into the compression chamber 35 side space while expanding the gap between the sliding surface of the bias ring 33, 34 and the inner wall of the cylinder 32.

In this way, in the one-way valve device according to this embodiment, when the pressure on the compression chamber 35 side is high, the pressure P is high.

A sealing force proportional to the pressure is generated to reliably prevent leakage to the low pressure side, and when the pressure is not so high and a small sealing force is required, the sliding between the bias rings 33, 34 and the inner wall of the cylinder 32 Since dynamic frictional resistance is also small, driving force can be reduced and operating costs can be reduced.

Furthermore, when the pressure P2 on the side opposite to the compression chamber 35 is higher, the fluid can easily flow toward the compression chamber 35, which improves suction efficiency and reduces operating costs.

In this example, the bias ring is 33.34°3.
6 and 37 are the valve body in the second invention, the circumferential groove 31a constitutes a groove, the grooves 33b and 36b are the first gap forming means, the tension ring 38 and the tapered surfaces 33a and 34a.

36a and 37a constitute a pressure contact means, and the pressure receiving surface 37c and the tapered surfaces 33a, 34a, 36a, and 37a constitute a second gap forming means.

FIG. 7 shows a second embodiment of the second invention.

In the figure, a circumferential groove 41a formed in the circumferential wall of the piston 41
The spiral ring 42 is spirally wound multiple times in the radial direction, and the tension ring 44 is attached to the innermost side of the spiral ring 42 and provides an elastic force that presses the spiral ring 42 against the inner wall of the cylinder 43. It is inserted.

The spiral ring 42 is formed by applying an elastic force that causes the adjacent circumferential surfaces of each winding portion to be slightly shifted in the axial direction. Due to the elastic force in the axial direction of the spiral ring 42, in a natural state, the spiral ring 42 The side surface 42a on the side of the compression chamber on the outer circumferential side is in pressure contact with the opposing surface of the circumferential groove 41a, and the side surface 42b on the side opposite to the compression chamber on the inner circumferential side is in pressure contact with the opposing surface of the circumferential groove 41a.
It is attached in pressure contact with the opposing surface of the Further, a plurality of grooves 42c are formed in the radial direction on the side surface 42a of the spiral ring 42 on the compression chamber side.

In this state, when the piston 41 moves toward the compression chamber, the frictional resistance of the sliding surface between the outer peripheral surface of the spiral ring 42 and the inner wall of the cylinder 43 and the inertial force of the piston 41 overcome the elastic force of the spiral ring 42. , the entire surface of the side surface 42b of the spiral ring 42 on the side opposite to the compression chamber is pressed against the opposing surface of the circumferential groove 41a.

In this case, the high pressure fluid on the compression chamber side
The high pressure fluid on the compression chamber side flows into the gap C4 between the inner circumferential surface of the tension ring 44 and the circumferential groove 41a through the gap between the side surface 42a and the opposing surface of the circumferential groove 41a. Thereby, the sealing performance between the side surface 42b of the spiral ring 42 and the facing surface of the circumferential groove 41a is ensured, and the outer peripheral surface of the spiral ring 42 is pressed against the inner wall of the cylinder 43, thereby strengthening the sliding sealing performance. This reliably prevents the high-pressure fluid on the compression chamber 45 side from leaking into the low-pressure side space.

On the other hand, during the expansion stroke in which the piston 42 moves to the side opposite to the compression chamber, the elastic force in the axial direction of the spiral ring 42 causes the outer periphery of the side surface 42a of the spiral ring 42 on the compression chamber side and the circumferential groove to The surface facing the circumferential groove 41a is in pressure contact with the inner peripheral side of the side surface 42b and the surface facing the circumferential groove 41a is in pressure contact with each other.

As a result, when the pressure on the compression chamber side is high, the contact surfaces of the spiral ring 42 and the sliding surfaces with the inner wall of the cylinder 43 come into pressure contact with each other to ensure high sealing performance, thereby preventing leakage to the low pressure side. On the other hand, when the pressure on the side opposite to the compression chamber 45 becomes higher, the pressure
side surface 4 due to the elasticity acting on each surface shifted in the axial direction of
While moving the pressure contact part 2a to the side opposite to the sliding side with the inner wall of the cylinder 43, the fluid flows toward the compression chamber while creating a gap between the contact surfaces of the respective winding parts.

Therefore, this device also provides the same functionality as the embodiment described above.

In this embodiment, the groove 42c constitutes the first gap forming means, and the elastic function of the spiral ring 42 itself, which shifts in the axial direction, constitutes the pressure contact means, and the pressure receiving surface formed to shift in the axial direction and the radial direction The shape that is wound in an overlapping manner constitutes the second gap forming means.

As described above, the second invention can ensure high sealing performance against low to high operating speeds and low to high working fluid pressures, and is widely applicable to Stirling engines, internal combustion engines, and the like.

The first point explained above. In the embodiment of the second invention, an uneven surface is formed on the valve body side to form a gap between one contact surface with the groove, but the same function can be achieved even if the groove side is formed as an uneven surface. Of course, this can be obtained.

In addition, in an embodiment applied to a device in which a piston reciprocates, a circumferential groove is formed on the cylinder side, and a piston having a straight shape in the axial direction is slid on the inner circumferential side of a valve body fitted into the circumferential groove. It may be configured to be inserted freely.

Further, the one-way valve device according to the present invention can be formed of any material, whether organic or inorganic, and can be formed into an appropriate shape depending on the location of application.

<Effects of the Invention> As explained above, according to the present invention, fluid flows from one of the two spaces defined on both sides of the one-way valve device interposed between the piston and the cylinder to the other. It has a high sealing performance to prevent flow, but by having a structure that allows for easy flow in the opposite direction, it can be used in place of the intake and exhaust valves of pumps such as compressors and vacuum pumps. Furthermore, in addition to the above-mentioned functions, the second invention can more reliably seal fluid leakage from the high-pressure side to the low-pressure side, making it possible to apply it to Stirling engines and internal combustion engines, and making the structure more compact. In addition to cost reduction, it is possible to promote reduction in operating costs and quietness due to reduction in drive friction.

Furthermore, the application is not limited to these pumps, engines, etc., but can be applied to any device that has a piston and cylinder and requires sealing properties, such as shock absorbers, and its uses are limitless. It is something that can be disseminated.

[Brief explanation of the drawing]

FIG. 1(A) is a cross-sectional view showing the configuration of a first embodiment according to the first invention of the present invention, and FIG. 1(B) is an enlarged view of the main part of FIG. 1(A) during the compression stroke. , Figure (C) is an enlarged view of the main part during the expansion stroke, Figure (D) is a front view of the piston ring used in the above device, and Figure (E) is a view of the piston ring that can be used in the same device. FIG. 2 is a front view showing another piston ring, FIG. 2 is a sectional view showing the configuration of the second embodiment according to the first invention, and FIG. 3 is another example of a piston ring that can be used in these embodiments. FIG. 4 is a diagram showing the operating characteristics of the first embodiment in comparison with the conventional example, and FIG. 5(A) is a perspective view.
1 is a sectional view showing the configuration of the third embodiment of the first invention, FIG. Enlarged view of main parts of A), No. 6
Figure (A) is an enlarged view of the main parts of the first embodiment of the second invention during the compression stroke, Figure (B) is an enlarged view of the main parts during the expansion stroke, and Figure 7 (A) is , Figure (B) is an enlarged view of the main part during the compression stroke of the second embodiment of the second invention, Figure (C) is an enlarged view of the main part during the expansion stroke, and Figure (C) is It is a front view of the spiral ring. 2, 12.32.43.51...Cylinder 3.
13.31°41...Piston 3a, 13a,
31a, Na... Circumferential groove 4.5... Piston ring
4a, 33a, 36b. 42c...Groove 4', 5'...Spiral ring 6, 38.44...Tension ring 7...Discharge chamber 14...Vacuum chamber 33, 34, 36.37.
・・Bias ring 33a, 34a, 36a, 37
a... Tapered surface 37c... Pressure receiving surface 57... Vane 57a... Notch 58... Slit 59... Coil spring 65... Suction chamber 6
6...Compression chamber c,,c,,c,,c4...Gap Fig. 1 (D) v, Fig. 2 Fig. 1 (E) Fig. 3 Fig. 4 Crank angle eg Fig. 6 (A ) P2 < P+ between 9a6 (B) p2>F'.

Claims (2)

[Claims] (1) A valve body that slides in pressure contact with one of the outer wall of the piston moving in the cylinder and the inner wall of the cylinder due to elastic force is inserted into a groove formed in the other, and both sides of the valve body are fitted. two spaces are formed in the valve body, and the valve body and the groove are formed to have a size with a gap on the side opposite to the sliding side of the valve body and in the direction in which the two spaces are lined up; Said 2 with groove
Opposing surfaces on one side in the direction in which the two spaces are lined up have a surface shape that has a high sealing property that blocks the space on one side from the gap on the opposite side to the valve body sliding side by contact between the two, and the other side The opposing surfaces on both sides are formed in a surface shape that maintains a large gap between the space on the other side and the gap on the side opposite to the valve body sliding side, both when the two are in contact and when they are not in contact. Features a one-way valve device. (2) A valve body that slides in pressure contact with one side of the outer wall of the piston moving in the cylinder and the inner wall of the cylinder is fitted into a groove formed on the other side, and the valve body is inserted into a groove formed on the other side, and Two spaces are formed in which the magnitude relationship of pressure is reversed by the movement of the piston, while the valve body and the groove form a space between opposing surfaces on one side in the direction in which the two spaces are arranged, opposite to the sliding side of the valve body. a first gap forming means for forming and maintaining a large gap communicating between opposing surfaces on one side; and a pressure contact means for constantly pressing a part of the opposing surface between the valve body and the groove on the other side in the alignment direction by elastic force. and, when the pressure in the space on the other side is higher than the pressure in the space on the opposite side, by receiving the pressure and moving the pressure contact part to the side opposite to the valve body sliding side,
A one-way valve device comprising: second gap forming means for forming a gap communicating from a side closer to the valve body sliding side than the pressure contact portion to a gap on one side in the arrangement direction of the spaces.