Flow regulator

The present disclosure provides a flow regulator capable of regulating flow resistance of a fluid by adjusting helical pitch of the flow regulator. The flow regulator comprises: a channel, a rod, and a helical coil. The channel has a fluid inlet and a fluid outlet for a fluid flowing in and out of the flow regulator, respectively. The rod has a fore end and a rear end opposite to each other. The fore end is inside the channel, and the rear end is closer to the fluid outlet than the fluid inlet. The helical coil winds around the rod, and the helical pitch of the helical coil is adjustable for regulating flow resistance of the fluid. The channel further has a narrowed section where part of the helical coil located therein substantially occupies an annular space between the rod and an inner wall of the channel.

CROSS REFERENCE TO RELATED APPLICATION

This application claims the priority benefit of Taiwan Patent Application No. 103124749, filed on Jul. 18, 2014. The entirety of the above-mentioned patent application is incorporated herein by reference and made a part of this specification.

TECHNICAL FIELD

The present disclosure relates to a flow regulator. In particular, the present disclosure provides a flow regulator which is capable of regulating flow resistance of a fluid.

BACKGROUND

Conventionally, there are two types of flow regulators, which are common type flow regulator and compensating type flow regulator. In a common type flow regulator, a flow can be controlled and managed through the assembly of channels, capillary openings and/or grooves that are specifically designed and formed inside the flow regulator. On the other hand, a compensating type flow regulator is generally embedded with a pressure feedback regulating device for detecting and compensating the flow rate and pressure inside a fluid system in an automatic manner. It is noted that the pressure feedback regulating device is a flexible/movable mechanism that is generally composed of membranes, sliding shafts, and slide blocks.

However, although a common type flow regulator is simple in structure and is comparatively easy to be used for adjusting flow resistance, the structure for adjusting flow resistance requires precision machining, and this kind of flow regulator is not equipped with an automatic compensating function. On the other hand, although a compensating type flow regulator is equipped with the desired automatic compensating function, it is difficult to be used for adjusting flow resistance.

SUMMARY

A flow regulator is introduced herein.

In a first aspect, the present disclosure provides a flow regulator, which comprises: a channel, a rod, and a helical coil. The channel has a fluid inlet and a fluid outlet for a fluid flowing in and out of the flow regulator, respectively. The rod has a fore end and a rear end opposite to each other. The fore end is inside the channel, and the rear end is closer to the fluid outlet than the fluid inlet. The helical coil winds around the rod, and the helical pitch of the helical coil is adjustable for regulating flow resistance of the fluid. The channel further has a narrowed section where part of the helical coil located therein substantially occupies an annular space between the rod and an inner wall of the channel.

In a second aspect, the present disclosure provides a flow regulator, which comprises: a channel, a rod, a first helical coil, a slide block, and a force provider. The channel has a fluid inlet and a fluid outlet for a fluid flowing in and out of the flow regulator, respectively. The rod has a fore end and a rear end opposite to each other. The fore end is inside the channel, and the rear end is outside the channel. The first helical coil winds around the rod, and a helical pitch of the first helical coil is adjustable for regulating flow resistance of the fluid. The slide block is fit on the rod. The force provider provides a force to the slide block. The channel further has a narrowed section where part of the first helical coil substantially occupies an annular space between the rod and an inner wall of the channel, and the slide block is movable toward or away from the fluid outlet along the rod.

In a third aspect, the present disclosure provides a flow regulator, which comprises: a channel, a rod, a helical coil, and an adjusting element. The channel has a fluid inlet and a fluid outlet for a fluid flowing in and out of the flow regulator, respectively. The rod has a fore end and a rear end opposite to each other, and the fore end is inside the channel. The helical coil winds around the rod, and a helical pitch of the helical coil being adjustable for regulating flow resistance of the fluid. The adjusting element is fit on the channel and closer to the rear end of the rod than the fore end. The channel further has a narrowed section where part of the helical coil substantially occupies an annular space between the rod and an inner wall of the channel, and the helical pitch of the helical coil is adjustable by a movement of the adjusting element toward or away from the rear end of the rod.

Several exemplary embodiments will be described in details below accompanying with figures. The present disclosure will become more fully understood from the detailed description given herein below and the accompanying drawings which are given by way of illustration only, and thus are not limitative of the present disclosure.

DETAILED DESCRIPTION

First Aspect

First of all, a first aspect of the present disclosure is described accompanying withFIG. 1toFIG. 4B. In the first aspect, the present disclosure provides a flow regulator capable of regulating flow resistance of a fluid by adjusting helical pitch of the flow regulator.

FIG. 1is a schematic diagram showing a flow regulator1, in accordance with a first exemplary embodiment of the present disclosure. InFIG. 1, a flow regulator1comprises a channel11, a rod13, and a helical coil15. The channel11has a fluid inlet111and a fluid outlet113for a fluid flowing in and out of the flow regulator1, respectively. The rod13has a fore end131and a rear end133opposite to each other. The rod13is inserted into the channel11such that the fore end131is inside the channel11. AsFIG. 1shown, the rear end133is closer to the fluid outlet113than the fluid inlet111. The helical coil15winds around the rod13, and a helical pitch d1of the helical coil15is adjustable for regulating flow resistance of the fluid.

Further, the channel11has a narrowed section, which falls in the area denoted by an effective regulating length L1inFIG. 1, where part of the helical coil15located therein substantially occupies an annular space between the rod13and inner wall of the channel11. Since in the narrowed section (the area corresponding to L1), there is not enough space between the rod13and the inner wall of the channel11for the fluid passing through, the fluid has to flow through the spacing in the helical coil15(defined by the helical pitch d1), and the flow resistance of the fluid is thus affected by the dimension of the helical pitch d1.

Furthermore, according to the first exemplary embodiment shown inFIG. 1, one end of the helical coil15is connected to the fore end131of the rod13, and the other end of the helical coil15is connected to the inner wall of the channel11close to the fluid outlet113. The rod13may have external threads (not shown) on it such that it may revolve with these threads and move along the axial direction of the channel11(parallel to a straight line from the fore end131to the rear end133of the rod13). Therefore, the helical pitch d1of the helical coil15may be adjusted by moving the rod13more into or more out of the channel11.

FIG. 2is a schematic diagram showing a flow regulator2, in accordance with a second exemplary embodiment of the present disclosure. InFIG. 2, a flow regulator2comprises a channel21, a rod23, and a helical coil25. The channel21has a fluid inlet211and a fluid outlet213for a fluid flowing in and out of the flow regulator2, respectively. The rod23has a fore end231and a rear end233opposite to each other. The rod23is inserted into the channel21such that the fore end231is inside the channel21. AsFIG. 2shown, the rear end233is closer to the fluid outlet213than the fluid inlet211. The helical coil25winds around the rod23, and a helical pitch d2of the helical coil25is adjustable for regulating flow resistance of the fluid.

Further, the channel21has a narrowed section, which falls in the area denoted by an effective regulating length L2inFIG. 2, where part of the helical coil25substantially occupies an annular space between the rod23and inner wall of the channel21. Since in the narrowed section (the area corresponding to L2), there is not enough space between the rod23and the inner wall of the channel21for the fluid passing through, the fluid has to flow through the spacing in the helical coil25(defined by the helical pitch d2), and the flow resistance of the fluid is thus affected by the dimension of the helical pitch d2.

Furthermore, according to the second exemplary embodiment shown inFIG. 2, one end of the helical coil25is connected to the inner wall of the channel21close to the fluid inlet211, and the other end of the helical coil25is connected to the rear end233of the rod23. The rod23may have internal threads (not shown) on the rear end233such that it may revolve with these threads and move along the axial direction of the channel21(parallel to a straight line from the fore end231to the rear end233of the rod23). Therefore, the helical pitch d2of the helical coil25may be adjusted by moving the rod23more into or more out of the channel21.

The present disclosure provides a flow regulator which is capable of regulating flow resistance of a fluid, and the flow resistance may be adjusted by the change of the helical pitch of the helical coil. In the following, the working principle of the flow regulator will be explained along withFIG. 1. Please be noted that the working principle of the flow regulator can be apply to all the exemplary embodiments of the present disclosure.

Please refer back toFIG. 1. A fluid may flow in and out of the channel1of the flow regulator1through the fluid inlet111and the fluid outlet113. In the flow regulator1, flow rate Q of the fluid can be calculated by the following simplified formula:

wherein

Q is the flow rate;

d is the helical pitch of the helical coil15, as d1shown inFIG. 1;

μ is the dynamic viscosity of the fluid;

L is the effective regulating length of the helical coil15along the rod13, as L1shown inFIG. 1, which corresponds to the narrowed section of the channel11;

g is the gap between the rod13and the inner wall of the channel11in the narrowed section;

Pinis an inlet pressure measured at the fluid inlet111; and

Poutis an outlet pressure measured at the fluid outlet113.

Here, please be noted that g is a fixed value in compliance with the designed dimension of the channel11and the rod13.

From the above formula (1), it is clear that the flow rate Q is highly related to the helical pitch d and the effective regulating length L. To be more specific, the smaller the helical pitch d (which indicates that the helical coil15is compressed tighter) and/or the longer the effective regulating length L is, the smaller the flow rate Q will be. On the contrary, the larger the helical pitch d (which indicates that the helical coil15is released looser) and/or the shorter the effective regulating length L is, the bigger the flow rate Q will be. Besides, the helical pitch d has a higher impact over the effective regulating length L on the flow rate Q.

Further, the relation between the flow rate Q and the flow resistance R can be defined by the following formula:

The formula (2) shows that the flow rate Q and the flow resistance R are in inverse proportion while the flow rate Q and the pressure difference (Pin−Pout) are in direct proportion. In addition, when the fluid source provides constant fluid (the value of the inlet pressure Pinis constant) the relation between the flow rate Q of the fluid leaving the flow regulator1and the outlet pressure Poutcan be expressed as follows: the bigger the flow resistance R is, the smaller the flow rate Q and the outlet pressure Poutwill be; and vice versa.

From the above two formulas (1) and (2), it will be readily understood to a person having ordinary skills in the art that one can adjust the helical pitch d1of the flow regulator1to have a required flow resistance R. To be more specific, if the helical pitch d1of the flow regulator1is set larger, the flow rate Q of the fluid leaving the channel11through the fluid outlet113and the outlet pressure Poutwill become bigger, and thus the flow resistance will R be smaller. On the contrary, if a bigger flow resistance R is required, the helical pitch d1of the flow regulator1needs to be set smaller, and the flow rate Q of the fluid leaving the channel11through the fluid outlet113and the outlet pressure Poutwill thus become smaller.

Next, please refer toFIGS. 3A and 3B. The operation of adjusting the helical pitch d1of the flow regulator1is described below with these figures.

FIGS. 3A and 3Bare schematic diagrams showing how to adjust the helical pitch d1of the flow regulator1by moving the rod13, in accordance with the first exemplary embodiment. Since one end of the helical coil15is connected to the fore end131of the rod13, and the other end of the helical coil15is connected to the inner wall of the channel11close to the fluid outlet113, the helical pitch d1of the flow regulator1may be altered by the movement of the rod13along the axial direction of the channel11. InFIGS. 3A and 3B, the helical pitch d1of the helical coil15in the flow regulator1is respectively defined as d11and d12. Compared with the condition shown inFIG. 3B, the rod13with the helical coil15inFIG. 3Ais inserted more into the channel11(in other words, the rear end133of the rod13inFIG. 3Ais closer to the fluid outlet113of the channel11.) Therefore, the helical pitch d11inFIG. 3Awould be larger than the helical pitch d12inFIG. 3B. Further, the flow resistance R inFIG. 3Awould be smaller than that inFIG. 3B, according to the working principle set out before. From the above-mentioned, it can be readily understood that one may adjust the flow resistance R of the flow regulator1by simply moving the rod13more into or more out of the channel11.

Now, please refer toFIGS. 4A and 4B. The operation of adjusting the helical pitch d2of the flow regulator2is described below with these figures. It should be noted that the working principle of the flow regulator1also apply to the flow regulator2.

FIGS. 4A and 4Bare schematic diagrams showing how to adjust the helical pitch d2of the flow regulator2by moving the rod23, in accordance with the second exemplary embodiment. Since one end of the helical coil25is connected to the inner wall of the channel21close to the fluid inlet211, and the other end of the helical coil25is connected to the rear end231of the rod23, the helical pitch d2of the flow regulator2may be altered by the movement of the rod23along the axial direction of the channel21. InFIGS. 4A and 4B, the helical pitch d2of the helical coil25in the flow regulator2is respectively defined as d21and d22. Compared with the condition shown inFIG. 4A, the rod23with the helical coil25inFIG. 4Bis inserted more into the channel21(in other words, the rear end233of the rod23inFIG. 4Bis closer to the fluid outlet213of the channel21). Therefore, the helical pitch d21inFIG. 4Awould be larger than the helical pitch d22inFIG. 4B, and the flow resistance R inFIG. 4Awould be smaller than that inFIG. 4B, according to the working principle set out before. From the above-mentioned, it can be readily understood that one may adjust the flow resistance R of the flow regulator2by simply moving the rod23more into or more out of the channel21.

Second Aspect

Secondly, a second aspect of the present disclosure is described accompanying withFIG. 5toFIG. 8C. In the second aspect, the present disclosure provides a flow regulator not only capable of regulating flow resistance of a fluid but also equipped with an automatic compensation function, and the automatic compensation function is achieved mainly by a movement of a slide block of the flow regulator.

FIG. 5is a schematic diagram showing a flow regulator3, in accordance with a third exemplary embodiment of the present disclosure. InFIG. 5, a flow regulator3comprises a channel31, a rod33, a first helical coil35, a second helical coil36, an adjusting element37, and a slide block39. The channel31has a fluid inlet311and a fluid outlet313for a fluid flowing in and out of the flow regulator3, respectively. The rod33has a fore end331and a rear end333opposite to each other. The rod33is inserted into the channel31such that the fore end331is inside the channel31and the rear end333is outside the channel31, and the rod33is movable along an axial direction of the channel31(parallel to a straight line from the fore end331to the rear end333of the rod33). The first helical coil35winds around the rod33, and a helical pitch d3of the first helical coil35is adjustable for regulating flow resistance of the fluid. The second helical coil36and the adjusting element37, which are used together as a force provider, provide a force to the slide block39. The adjusting element37is fit on the rod33and may move toward or away from the rear end333of the rod33. The second helical coil36winds around the rod33. The slide block39is fit on the rod33. To be specific, the rod33penetrates through the slide block39, and the slide block39is connected with the rod33in a way such that the movement of rod33will not lead the slide block39to move together.

Further, the channel31has a narrowed section, which falls in the area denoted by an effective regulating length L3inFIG. 5, where part of the first helical coil35located therein substantially occupies an annular space between the rod33and inner wall of the channel31. Since in the narrowed section (the area corresponding to L3), there is not enough space between the rod33and the inner wall of the channel31for the fluid passing through, the fluid has to flow through the spacing in the first helical coil35(defined by the helical pitch d3), and the flow resistance of the fluid is thus affected by the dimension of the helical pitch d3.

Besides, the slide block39may move toward or away from the fluid outlet313along the rod33. There may be a seal (not shown), such as an O-ring, mounted on the slide block39for coupling the slide block39to the channel31, or the slide block39itself is such designed that it is coupled to the channel31tightly enough. Either way, the fluid will not flow into a space between the slide block39and the adjusting element37in the channel31. In this embodiment, the fluid flows into the channel31through the fluid inlet311, passes through the spacing in the first helical coil35in the narrowed section (the area corresponding to L3), and then flows out of the channel31through the fluid outlet313without leaking into the space between the slide block39and the adjusting element37in the channel31.

Furthermore, according to the third exemplary embodiment shown inFIG. 5, the slide block39comprises a regulating side391and a compensating side393opposite to each other. One end of the first helical coil35is connected to the fore end331of the rod33, and the other end of the first helical coil35is connected to the regulating side391of the slide block39. In addition, one end of the second helical coil36is connected to the compensating side393of the slide block39, and the other end of the second helical coil36is connected to the adjusting element37. The automatic compensation function is achieved by the dynamic relations among the first helical coil35, the second helical coil36, and the movable slide block39. The working principle of how to achieve the automatic compensation function will be explained in detail later.

FIG. 6is a schematic diagram showing a flow regulator4, in accordance with a fourth exemplary embodiment of the present disclosure. InFIG. 6, a flow regulator4comprises a channel41, a rod43, a first helical coil45, a controllable pressure regulator48, and a slide block49. The channel41has a fluid inlet411and a fluid outlet413for a fluid flowing in and out of the flow regulator4, respectively. The rod43has a fore end431and a rear end433opposite to each other. The rod43is inserted into the channel41such that the fore end431is inside the channel41and the rear end433is outside the channel41, and the rod43is movable along an axial direction of the channel41(parallel to a straight line from the fore end431to the rear end433of the rod43). The first helical coil45winds around the rod43, and a helical pitch d4of the first helical coil45is adjustable for regulating flow resistance of the fluid. The controllable pressure regulator48, which is used as a force provider, provides a force to the slide block49, and is in fluid communication with the channel41through an opening415of the channel41. The slide block49is fit on the rod43. To be specific, the rod43penetrates through the slide block49, and the slide block49is connected with the rod43in a way such that the movement of rod43will not lead the slide block49to move together.

Further, the channel41has a narrowed section, which falls in the area denoted by an effective regulating length L4inFIG. 6, where part of the first helical coil45located therein substantially occupies an annular space between the rod43and inner wall of the channel41. Since in the narrowed section (the area corresponding to L4), there is not enough space between the rod43and the inner wall of the channel41for the fluid passing through, the fluid has to flow through the spacing in the helical coil45(defined by the helical pitch d4), and the flow resistance of the fluid is thus affected by the dimension of the helical pitch d4.

Besides, the slide block49may move toward or away from the fluid outlet413along the rod43. To be specific, the slide block49may move between the fluid outlet413and the opening415of the channel41. There may be a seal (not shown), such as an O-ring, mounted on the slide block49for coupling the slide block49to the channel41, or the slide block49itself is such designed that it is coupled to the channel41tightly enough. Either way, the fluid will only flows in a space between the fluid inlet411and the slide block49in the channel41. In this embodiment, the fluid flows into the channel41through the fluid inlet411, passes through the spacing in the first helical coil45in the narrowed section (the area corresponding to L4), and then flows out of the channel41through the fluid outlet413; in other words, the fluid only flows in the space between the fluid inlet411and the slide block49in the channel41.

Furthermore, according to the fourth exemplary embodiment shown inFIG. 6, the slide block49comprises a regulating side491and a compensating side493opposite to each other. One end of the first helical coil45is connected to the fore end431of the rod43, and the other end of the first helical coil45is connected to the regulating side491of the slide block49. In addition, the opening415of the channel41is closer to the compensating side493than the regulating side491of the slide block49. The automatic compensation function is achieved by the dynamic relations among the first helical coil45, the controllable pressure regulator48, and the movable slide block49. The working principle of how to achieve the automatic compensation function will be explained in detail later.

Moreover, inFIG. 6, the dash line denotes the flow communication associated with the controllable pressure regulator48, and the same fluid source (not shown) provides fluid to the channel41through the fluid inlet411and to the controllable pressure regulator48. However, in another example, the controllable regulator48may has a separate fluid source, and thus the dash line (denoting the fluid communication) will not appears to link the controllable pressure regulator48and the fluid inlet411. Besides, the controllable pressure regulator48may be chose from any type of controllable pressure regulators known in the art.

The present disclosure provides a flow regulator not only capable of regulating flow resistance of a fluid but also equipped with an automatic compensation function. In the second aspect, the automatic compensation function is achieved mainly by the movement of the slide block. In the following, the working principle of how to achieve the automatic compensation function will be explained along withFIG. 5andFIG. 6, respectively.

Please refer back toFIG. 5. When the flow regulator3is in equilibrium, forces applied to both the regulating side391and the compensating side393of the slide block39will be balanced, and can be expressed as the following formula:
F3+P3′×A3=F3′(3)

wherein

F3is a first force provided by the first helical coil35;

F3′is a second force provided by the second helical coil36;

P3′is an outlet pressure measured at the fluid outlet313; and

A3is an effective area on which the outlet pressure P3′is applied.

Both F3and (P3′×A3) are applied to the regulating side391of the slide block39, and F3′is applied to the compensating side393of the slide block39.

The first force F3from the first helical coil35and the second force F3′from the second helical coil36may be adjusted simply by respectively changing the helical pitches of the first helical coil35and the second helical coil36. Further, since the slide block39is connected to the first helical coil35at the regulating side391and connected to the second helical coil36at the compensating side393, the change of the helical pitch d3of the first helical coil35would result in moving the slide block39toward or away from the fluid outlet313and thus changing the helical pitch of the second helical coil36; and vice versa.

In addition, from to the above formula (3), it is clearly that the outlet pressure P3′is affected by the first force F3from the first helical coil35and the second force F3′from the second helical coil36. Therefore, the outlet pressure P3′at the fluid outlet313, where the fluid flows out of the channel31, may be altered by changing the helical pitches of the first helical coil35or the second helical coil36. On the other hand, when a pressure of a subsequent chamber (not shown) connected to the channel31through the fluid outlet313is changed and thus affecting the outlet pressure P3′at the fluid outlet313, through the dynamic relations among the first helical coil35, the second helical coil36, and the movable slide block39, the flow resistance R is varied because of the alteration of the helical pitch d3of the first helical coil35, and the effect causing by the pressure change in the subsequent chamber is automatic compensated consequently.

Now, please refer toFIG. 6. Similar to the above description for the flow regulator3, when the flow regular4is in equilibrium, forces applied to both the regulating side491and the compensating side493of the slide block49will be balanced, and can be expressed as the following formula:
F4+P4′×A4=F4′(4)

wherein

F4is a first force provided by the first helical coil45;

F4′is a second force provided by the controllable pressure regulator48;

P4′is an outlet pressure measured at the fluid outlet413; and

A4is an effective area on which the outlet pressure P4′is applied.

Here, please be noted that, different from the flow regulator3, according to the fourth embodiment, F4′is provided by the controllable pressure regulator48, instead of another helical coil. Both F4and (P4′×A4) are applied to the regulating side491of the slide block49, and F4′is applied to the compensating side493of the slide block49.

The first force F4from the first helical coil45may be adjusted simply by changing the helical pitch d4of the first helical coil45, and the second force F4′may be altered by setting the controllable pressure regulator48to a required pressure. Further, since the slide block49is connected to the first helical coil45at the regulating side391and subject to the force F4′provided by the controllable pressure regulator48at the compensating side493, the change of the helical pitch d4of the first helical coil45would definitely result in moving the slide block49toward or way from the fluid outlet413; and vice versa.

In addition, from to the above formula (4), it is clearly that the outlet pressure P4′is affected by the first force F4from the first helical coil45and the second force F4′from the controllable pressure regulator48. Therefore, when the controllable pressure regulator48is set to a certain pressure, the outlet pressure P4′at the fluid outlet413, where the fluid flows out of the channel41, may be altered by changing the helical pitch d4of the first helical coil45. On the other hand, when a pressure of a subsequent chamber (not shown) connected to the channel41through the fluid outlet413is changed and thus affecting the outlet pressure P4′at the fluid outlet413, through the dynamic relations among the first helical coil45, the controllable pressure regulator48, and the movable slide block39, the flow resistance R is varied because of the alteration of the helical pitch d4of the first helical coil45, and the effect causing by the pressure change in the subsequent chamber is automatic compensated consequently.

To be more specific, since the force F4′provided by the controllable pressure regulator48is a constant value after the setting, when the outlet pressure P4′becomes bigger, the slide block49will move away from the fluid outlet413, and thus increasing the helical pitch d4of the first helical coil45. The flow resistance R is therefore decreased. On the other hand, when the outlet pressure P4′becomes smaller, the slide block49will move toward the fluid outlet413, and thus decreasing the helical pitch d4of the first helical coil45. The flow resistance R is therefore increased.

Next, please refer toFIG. 7A˜7C. The operation of adjusting the helical pitch d3of the flow regulator3is described below with these figures. It should be noted that as the operation of adjusting the helical pitch d4of the flow regulator4is similar to that of the flow regulator3, it will not be described further herein.

FIGS. 7A and 7Bare schematic diagrams showing how to adjust the helical pitch d3of the flow regulator3by moving the rod33, in accordance with the third exemplary embodiment. Since one end of the helical coil35is connected to the fore-end331of the rod33, and the other end of the helical coil35is connected to the slide block39, the helical pitch d3of the flow regulator3may be altered by the movement of the rod33along the axial direction of the channel31.

InFIGS. 7A and 7B, the helical pitch d3of the first helical coil35is respectively defined as d31and d32, and the effective regulating length L3thereof is respectively defined as L31and L32. Compared with the condition shown inFIG. 7A, the rod33with the first helical coil35inFIG. 7Bis inserted more into the channel31(in other words, the fore-end331of the rod33is closer to the fluid inlet311). Therefore, the helical pitch d32and the effective regulating length L32inFIG. 7Bwould be larger than the helical pitch d31and the effective regulating length L31inFIG. 7A. As the working principle set out before, the larger the helical pitch d3or the shorter the effective regulating length L3is, the smaller the flow resistance R will be, and the helical pitch d3has more effect on the flow resistance R than the effective regulating length L3does. Therefore, the flow resistance R inFIG. 7Bis smaller than that inFIG. 7A. One the other hand, when a bigger flow resistance R in required, the rod33may be moved more out of the channel31(in other words, the fore-end331of the rod33is away from the fluid inlet311) than the rod33inFIG. 7Adoes. In such circumstance, the helical pitch d3and the effective regulating length L3of the flow regulator3will be smaller, and the bigger flow resistance R is achieved as a result.

FIGS. 7A and 7Care schematic diagrams showing how to adjust the helical pitch d3of the flow regulator3by moving the adjusting element37, in accordance with the third exemplary embodiment. If a required flow resistance R cannot be achieved by the movement of the rod33, the adjusting element37may be further moved along the rod33to adjust the flow resistance R.

InFIGS. 7A and 7C, the helical pitch d3of the first helical coil35is respectively defined as d31and d33, and the effective regulating length L3thereof is respectively defined as L31and L33. Compared with the condition shown inFIG. 7A, the adjusting element37inFIG. 7Cis moved more toward the rear end333of the rod33. In such circumstance, due to the force difference between the first and second helical coil35and36, the slide block39will move more away from the fluid outlet313, and the helical pitch d33inFIG. 7Cis thus be larger than the helical pitch d31of the first helical coil35inFIG. 7A. As the working principle set out before, the larger the helical pitch d3is, the smaller the flow resistance R will be. Therefore, the flow resistance R inFIG. 7Cis smaller than inFIG. 7A.

From the above description with reference toFIG. 7A˜7C, it is clear that the flow resistance R of the flow regulator3can be varied by moving the rod33more into or away from the channel31. Further, in the condition when the required flow resistance R cannot be achieved by the movement of the rod33, the flow resistance R can be altered by moving the adjusting element37more toward or away from the rear end333of the rod33. Here, it should be noted that the operation for adjusting the flow resistance R of the flow regulator3also apply to the flow regulator4, too.

Next, please refer toFIG. 8A˜8C. The operation demonstrating how the automatic compensation function of the flow regulator3works is described below with these figures. It should be noted that as the operation demonstrating how the automatic compensation function of the flow regulator4works is basically the same as the flow regulator3, it will not be described further herein.

FIG. 8A˜8C are a series of schematic diagrams showing how the helical pitch d3of the first helical coil35of the flow regulator3varies automatically along with the pressure change of the outlet pressure P3′measured at the fluid outlet313of the channel31, in accordance with the third exemplary embodiment of the present disclosure. Since the operation of the flow regulator3follows previously mentioned formula (3): (F3+P3′×A3=F3′), and the movable slide block39is subject to (F3+P3′×A3) at the regulating side391and F3′at the compensating side393, the slide block39may move toward or away from the fluid outlet313as any of these forces changes.

InFIGS. 8A, 8B, and 8C, the helical pitch d3of the first helical coil35is respectively defined as d34, d35, and d36, and the outlet pressure measured at the fluid outlet313of the channel31is respectively defined as P34′, P35′, and P36′.

First, please refer toFIGS. 8A and 8B, which shows how the slide block39moves when the outlet pressure P34′changes to P35′. To be more specific, when the pressure of the subsequent chamber (not shown) connected to the flow regulator3through the fluid outlet313is increased, the outlet pressure P34′inFIG. 8Awill increase to P35′inFIG. 8B(i.e. P35′>P34′). Owing to the higher pressure P35′at the fluid outlet313, the slide block39inFIG. 8Bwill be forced to move away from the fluid outlet313, and the helical pitch d34of the first helical coil35thus becomes larger (i.e. d35>d34), compared with the condition inFIG. 8A. In such circumstance, the first force F3provided by the first helical coil35decreases (i.e. F35<F34), the second force F3′provided by the second helical coil36increases (i.e. F35′>F34′), and the final position of the rod33is determined by the force difference between the first and the second force F3and F3′.

As the working principle set out before, the larger the helical pitch d3is, the smaller the flow resistance R will be. Therefore, the flow resistance R inFIG. 8Bis smaller than inFIG. 8A. As the flow resistance R gets smaller, the flow rate Q and the overall pressure in the flow regulator3will becomes larger in an automatically compensating manner.

Next, please refer toFIGS. 8A and 8C, which shows how the slide block39moves when the outlet pressure P34′changes to P36′. To be more specific, when the pressure of the subsequent chamber (not shown) connected to the flow regulator3through the fluid outlet313is decreased, the outlet pressure P34′inFIG. 8Awill decrease to P36′inFIG. 8C(i.e. P36′<P34′). Owing to the lower pressure P36′at the fluid outlet313, the slide block39inFIG. 8Cwill be forced to move toward the fluid outlet313, the helical pitch d36of the first helical coil35thus becomes smaller (i.e. d36<d34), compared with the condition inFIG. 8A. In such circumstance, the first force F3provided by the first helical coil35increases (i.e. F36>F34), the second force F3′provided by the second helical coil36decreases (i.e. F36′<F34′), and the final position of the rod33is determined by the force difference between the first and the second force F3and F3′.

As the working principle set out before, the smaller the helical pitch d3is, the bigger the flow resistance R will be. Therefore, the flow resistance R inFIG. 8Cis bigger than inFIG. 8A. As the flow resistance R gets bigger, the flow rate Q and the overall pressure in the flow regulator3will becomes smaller in an automatically compensating manner.

From the above description with reference toFIG. 8A-8C, it is clear that the flow resistance R of the flow regulator3can be varied automatically along with the pressure change in the subsequent chamber (not shown) connected to the channel31through the fluid outlet313of the flow regulator3, which in turn causes the flow rate Q and overall pressure of the flow regulator3to be changed in an automatically compensating manner. Here, it should be noted that the automatic compensation function works for the flow regulator3also apply to the flow regulator4, too.

Third Aspect

Thirdly, a third aspect of the present disclosure is described accompanying withFIG. 9toFIG. 17B. In the third aspect, the present disclosure provides a flow regulator not only capable of regulating flow resistance of a fluid but also equipped with an automatic compensation function, and the automatic compensation function is achieved mainly by a movement of a rod of the flow regulator.

FIG. 9is a schematic diagram showing a flow regulator5according to a fifth exemplary embodiment of the present disclosure. InFIG. 9, a flow regulator5comprises a channel51, a rod53, a helical coil55, and an adjusting element57. The channel51has a fluid inlet511and a fluid outlet513for a fluid flowing in and out of the flow regulator5, respectively. The rod53has a fore end531and a rear end533opposite to each other. The rod53is inserted into the channel51such that at least the fore end531is inside the channel51, and the rod53is movable along an axial direction of the channel51(parallel to a straight line from the fore end531to the rear end533of the rod53). The helical coil55winds around the rod53, and a helical pitch d5of the helical coil55is adjustable for regulating flow resistance of the fluid. The adjusting element57is fit on the channel51, and closer to the rear end533than the fore end531of the rod53.

Further, the channel51has a narrowed section, which falls in the area denoted by an effective regulating length L5inFIG. 9, where part of the helical coil55located therein substantially occupies an annular space between the rod53and inner wall of the channel51. Since in the narrowed section (the area corresponding to L5), there is not enough space between the rod53and the inner wall of the channel51for the fluid passing through, the fluid has to flow through the spacing in the helical coil55(defined by the helical pitch d5), and the flow resistance of the fluid is thus affected by the dimension of the helical pitch d5.

Furthermore, according to the fifth exemplary embodiment shown inFIG. 9, the adjusting element57is further fit on the rod53. In one example, the adjusting element57may have internal threads (not shown) on it such that the adjusting element57may revolve with these threads and move along the axial direction of the channel51. The adjusting element57may have different structure in other example as long as it may move along the axial direction of the channel51. Moreover, one end of the helical coil55is connected to the fore end531of the rod53, and the other end of the helical coil55is connected to the adjusting element57. Therefore, the helical pitch d5of the helical coil55may be adjusted by moving the adjusting element57toward or away from the rear end533.

The present disclosure provides a flow regulator which is not only capable of regulating flow resistance of a fluid but also equipped with an automatic compensation function. In the fifth exemplary embodiment, the automatic compensation function is achieved mainly by the movable rod53with the helical coil55winding on it. In the following, the working principle of how to achieve the automatic compensation function will be explained along withFIG. 9.

Please refer toFIG. 9again. When the flow regulator5is in equilibrium, forces applied to the fore end531of the rod53is balanced, and can be expressed as the following formula:
P5×A5=F5(5)

wherein

F5is a force provided by the helical coil55;

P5is an inlet pressure measured at the fluid inlet511; and

A5is an effective area on which the inlet pressure P5is applied.

Here, please be noted that the effective area A5may be regarded as the cross sectional area of the fore end531of the rod53.

As the fore end531of the rod53is subject to the force F5and the inlet pressure P5, altering the force F5by adjusting the helical pitch d5of the helical coil55may affect the magnitude of the pressure applied to the effective area A5. On the other hand, the change of the inlet pressure P5would result in moving the rod53toward or away from the fluid inlet513. Further, since one end of the helical coil55is connected to the fore end531of the rod53, and the other end of the helical coil55is connected to the adjusting element57, which is fixed to a certain position under a normal condition, the helical pitch d5of the helical coil55will be changed due to the movement of the rod53, and thus the flow resistance R of the fluid is altered, as the working principle set out before. In brief, when the inlet pressure P5changes, through the movement of the rod53, the flow resistance R is varied because of the alteration of the helical pitch d5of the helical coil55, and the effect causing by the pressure change is automatic compensated consequently.

FIG. 10is a schematic diagram showing a flow regulator6according to a sixth exemplary embodiment of the present disclosure. InFIG. 10, a flow regulator6comprises a channel61, a rod63, a helical coil65, and an adjusting element67. The channel61has a fluid inlet611and a fluid outlet613for a fluid flowing in and out of the flow regulator6, respectively. The rod63has a fore end631and a rear end633opposite to each other. The rod63is inserted into the channel61such that the fore end631and the rear end633are both inside the channel61, and the rod63is movable along an axial direction of the channel61(parallel to a straight line from the fore end631to the rear end633of the rod63). The helical coil65winds around the rod63, and a helical pitch d6of the helical coil65is adjustable for regulating flow resistance of the fluid. The adjusting element67is fit on the channel61, and closer to the rear end633than the fore end631of the rod63.

Further, the channel61has a narrowed section, which falls in the area denoted by an effective regulating length L6inFIG. 10, where part of the helical coil65located therein substantially occupies an annular space between the rod63and inner wall of the channel61. Since in the narrowed section (the area corresponding to L6), there is not enough space between the rod63and the inner wall of the channel61for the fluid passing through, the fluid has to flow through the spacing in the helical coil65(defined by the helical pitch d6), and the flow resistance of the fluid is thus affected by the dimension of the helical pitch d6.

Furthermore, according to the sixth exemplary embodiment shown inFIG. 10, the fore end631of the rod63has passages631aand631bfor the fluid passing through, and an cross sectional area of the fore end631is larger than an cross sectional area of the rear end633such that the rod63may keep its position in the middle with respect to the radial direction of the channel61(perpendicular to the straight line from the fore end631to the rear end633of the rod63). In one example, the fore end631of the rod63may contact the inner wall of the channel61; however, in another example, there may be space between the fore end631of the rod63and the inner wall of the inner wall of the channel61. In this embodiment, the fluid flows into the channel61through the fluid inlet611, passes through the passages631aand631b, then in the narrowed section (the area corresponding to L6), the fluid flows through the spacing in the helical coil65, and finally, the fluid flows out of the channel61through the fluid outlet613. InFIG. 10, the flow of the fluid is represented by a continuous dash line with arrow. In addition, one end of the helical coil65is connected to the fore end631of the rod63, and the other end of the helical coil65is connected to the adjusting element67. Therefore, the helical pitch d6of the helical coil65may be adjusted by moving the adjusting element67toward or away from the rear end633(and toward or away from the fluid outlet613in this embodiment, to be specific).

The present disclosure provides a flow regulator which is not only capable of regulating flow resistance of a fluid but also equipped with an automatic compensation function. In the sixth exemplary embodiment, the automatic compensation function is achieved mainly by the movable rod63with the helical coil65winding on it. In the following, the working principle of how to achieve the automatic compensation function will be explained along withFIG. 10.

Please refer toFIG. 10again. When the flow regulator6is in equilibrium, forces applied to the rod63is balanced, and can be expressed as the following formula:
F6+P6′×A6′=P6×A6(6)

wherein

F6is a force provided by the helical coil65;

P6is an inlet pressure measured at the fluid inlet611;

P6′is an outlet pressure measured at the fluid outlet613;

A6is an effective area on which the inlet pressure P6is applied; and

A6′is an effective area on which the outlet pressure P6′is applied.

Here, please be noted that the effective area A6may be regarded as the cross sectional area of the fore end631of the rod63minus the cross sectional area of the passages631aand631b, and the effective area A6′may be regarded as the cross sectional area of the rear end633of the rod63.

As the rod63is subject to the inlet pressure P6and the force F6at the fore end631, and the outlet pressure P6′at the rear end633, the change of the outlet pressure P6′, which is affected by an pressure of a subsequent chamber (not shown) connected to the channel61through the fluid outlet613, would result in moving the rod63toward or away from the fluid outlet613. Further, since one end of the helical coil65is connected to the fore end631of the rod63and the other end is connected to the adjusting element67, which is fixed to a certain position under a normal condition, the helical pitch d6of the helical coil65will be changed due to the movement of the rod63, and thus the flow resistance R of the fluid is altered, as the working principle set out before. In brief, when the outlet pressure P6′changes, through the movement of the rod63, the flow resistance R is varied because of the alteration of the helical pitch d6of the helical coil65, and the effect causing by the pressure change is automatic compensated consequently.

FIG. 11is a schematic diagram showing a flow regulator7according to a seventh exemplary embodiment of the present disclosure. InFIG. 11, a flow regulator7comprises a channel71, a rod73, a first helical coil75, a second helical coil76, and an adjusting element77. The channel71has a fluid inlet711and a fluid outlet713for a fluid flowing in and out of the flow regulator7, respectively. The rod73has a fore end731and a rear end733opposite to each other. The rod73is inserted into the channel71such that the fore end731and the rear end733are both inside the channel71, and the rod73is movable along an axial direction of the channel71(parallel to a straight line from the fore end731to the rear end733of the rod73). The first helical coil75winds around the rod73, and a helical pitch d7of the helical coil75is adjustable for regulating flow resistance of the fluid. The adjusting element77is fit on the channel71, and closer to the rear end733than the fore end731of the rod73.

Further, the channel71has a narrowed section, which falls in the area denoted by an effective regulating length L7inFIG. 11, where part of the helical coil75located therein substantially occupies an annular space between the rod73and inner wall of the channel71. Since in the narrowed section (the area corresponding to L7), there is not enough space between the rod73and the inner wall of the channel71for the fluid passing through, the fluid has to flow through the spacing in the helical coil75(defined by the helical pitch d7), and the flow resistance of the fluid is thus affected by the dimension of the helical pitch d7.

Furthermore, according to the seventh exemplary embodiment shown inFIG. 11, a cross sectional area of the rear end733is larger than effective cross sectional area of the fore end731. To be specific, the rear end733of the rod73contacts the inner wall of the channel. There may be a seal (not shown), such as an O-ring, mounted on the rear end733of the rod73for coupling the rear end733to the channel71, or the rear end733itself is designed to couple to the channel71tightly enough. Either way, the fluid will not flow to a space between the rear end733of the rod73and the adjusting element77in the channel71. In this embodiment, the fluid flows into the channel71through the fluid inlet711, passes through the spacing in the first helical coil75in the narrowed section (the area corresponding to L7), and then flows out of the channel71through the fluid outlet713without flowing to the space between the rear end733of the rod73and the adjusting element77in the channel71.

Moreover, asFIG. 11shown, one end of the first helical coil75is connected to the inner wall of the channel71, and the other end of the first helical coil75is connected to the rear end733of the rod73. The second helical coil76is connected to the rear end733of the rod73at one end and to the adjusting element77at the other end. Therefore, the helical pitch d7of the first helical coil75may be adjusted by moving the adjusting element77toward or away from the rear end733.

The present disclosure provides a flow regulator which is not only capable of regulating flow resistance of a fluid but also equipped with an automatic compensation function. In the seventh exemplary embodiment, the automatic compensation function is achieved by the dynamic relations among the movable rod73, the first helical coil75, and the second helical coil76. In the following, the working principle of how to achieve the automatic compensation function will be explained along withFIG. 11.

Please refer toFIG. 11. When the flow regulator7is in equilibrium, forces applied to the rod73is balanced, and can be expressed as the following formula:
P7×A7+P7′×A7′+F7=F7′(7)

wherein

F7is a first force provided by the first helical coil75;

F7′is a second force provided by the second helical coil76;

P7is an inlet pressure measured at the fluid inlet711;

P7′is an outlet pressure measured at the fluid outlet713;

A7is an effective area on which the inlet pressure P7is applied; and

A7′is an effective area on which the outlet pressure P7′is applied.

Here, please be noted that the effective area A7may be regarded as the cross sectional area of the fore end731of the rod73, and the effective area A7′may be regarded as the cross sectional area of the rear end733of the rod73minus the cross sectional area of the fore end731of the rod73.

The first force F7from the first helical coil75and the second force F7′from the second helical coil76may be adjusted simply by respectively changing the helical pitches of the first helical coil75and the second helical coil76. Further, since one side of the rear end733of the rod73is connected to the first helical coil75, and the other side of the rear end733is connected to the second helical coil76, the change of the helical pitch d7of the first helical coil75would result in moving the rear end733(and the whole rod73) toward or away from the fluid outlet713and thus changing the helical pitch of the second helical coil76; and vice versa.

In addition, from to the above formula (7), it is clearly that the outlet pressure P7′would be affected by the first force F7from the first helical coil75and the second force F7′from the second helical coil76. Therefore, the outlet pressure P7′at the fluid outlet713, where the fluid flows out of the channel71, may be altered by changing the helical pitches of the first helical coil75or the second helical coil76. On the other hand, when an pressure of a subsequent chamber (not shown) connected to the channel71through the fluid outlet713is changed and thus affecting the outlet pressure P7′at the fluid outlet713, through the dynamic relations among the movable rod73, the first helical coil75, and the second helical coil76, the flow resistance R is varied because of the alteration of the helical pitch d7of the first helical coil75, and the effect causing by the pressure change in the subsequent chamber is automatic compensated consequently.

In the following, the operation of adjusting the helical pitch of the flow regulator and the operation demonstrating how the automatic compensation function of the flow regulator works in accordance with the fifth, sixth, and seventh exemplary embodiments of the present disclosure will be respectively described in details with reference toFIG. 12AtoFIG. 17B.

First, please refer toFIGS. 12A and 12B. The operation of adjusting the helical pitch d5of the flow regulator5is described below with these figures.

FIGS. 12A and 12Bare schematic diagrams showing how to adjust the helical pitch d5of the flow regulator5by moving the adjusting element57, in accordance with the fifth exemplary embodiment. Since one end of the helical coil55is connected to the fore end531of the rod53, and the other end of the helical coil55is connected to the adjusting element57, the helical pitch d5of the flow regulator5may be altered by the movement of the adjusting element57.

InFIGS. 12A and 12B, the helical pitch d5of the helical coil55is respectively defined as d51and d52. Compared with the condition shown inFIG. 12A, the adjusting element57inFIG. 12Bis moved more into the channel51(in other words, the adjusting element57is moved toward the fore end531of the rod53and away from the rear end533of the rod53). Therefore, the helical pitch d52inFIG. 12Bwould be smaller than the helical pitch d51inFIG. 12A. As the working principle set out before, the smaller the helical pitch d5is, the bigger the flow resistance R will be. Therefore, the flow resistance R inFIG. 12Bis bigger than that inFIG. 12A. One the other hand, when a smaller flow resistance R in required, the adjusting element57may be moved more out of the channel51(in other words, the adjusting element57is moved away from the fore end531and toward the rear end533of the rod53) than the adjusting element57inFIG. 12Adoes. In such circumstance, the helical pitch d5of the flow regulator5will be larger, and the smaller flow resistance R is achieved as a result.

Now, please refer toFIGS. 13A and 13B. The operation demonstrating how the automatic compensation function of the flow regulator5works is described below with these figures.

InFIGS. 13A and 13B, the force F5provided by the helical coil55is respectively defined as F53and F54, the helical pitch d5of the helical coil55is respectively defined as d53and d54, the inlet pressure measured at the fluid inlet511of the channel51is respectively defined as P53and P54, and the outlet pressure measured at the fluid outlet513of the channel51is respectively defined as P53′and P54′.

FIGS. 13A and 13Bare a series of schematic diagrams showing how the helical pitch d5of the helical coil55of the flow regulator5varies automatically along with the pressure change of the inlet pressure P5measured at the fluid inlet511of the channel51, in accordance with the fifth exemplary embodiment of the present disclosure. Since the forces applied to the fore end531of the rod53are balanced and the operation of the flow regulator5follows previously mentioned formula (5): (P5×A5=F5), the rod53may move toward or away from the fluid inlet511as either of these forces changes.

FIGS. 13A and 13Bshows how the rod53moves when the inlet pressure P53changes to P54. To be more specific, when the pressure setting of the fluid source (not shown) connected to the flow regulator5through the fluid inlet511is decreased, the inlet pressure P53inFIG. 13Awill decrease to P54inFIG. 12B(i.e. P53>P54). Since the inlet pressure P53decreases to P54, the force F54inFIG. 13Bbecomes smaller than F53inFIG. 13A, according to formula (5). As a result, the rod53will be forced to move toward the fluid inlet511, and the helical pitch d54of the helical coil55thus becomes larger (i.e. d54>d53), compared with the condition inFIG. 13A.

As the working principle set out before, the larger the helical pitch d5is, the smaller the flow resistance R will be. Therefore, the flow resistance R inFIG. 13Bis smaller than inFIG. 13A. When the flow resistance R gets smaller, the flow rate Q and the overall pressure in the flow regulator5will become larger in an automatically compensating manner. Similarly, when the inlet pressure P5of the flow regulator5increases, the force F5provided by the helical coil55will becomes bigger and the helical pitch d5will get smaller; thus increasing the flow resistances R.

From the above description, it is clear that the flow resistance R of the flow regulator5can be varied automatically along with the change of the pressure setting of the fluid source (not shown) connected to the channel51through the fluid inlet511of the flow regulator5, which in turn causes the flow rate Q and overall pressure of the flow regulator5to be changed in an automatically compensating manner.

Next, please refer toFIGS. 14A and 14B. The operation of adjusting the helical pitch d6of the flow regulator6is described below with these figures.

FIGS. 14A and 14Bare schematic diagrams showing how to adjust the helical pitch d6of the flow regulator6by moving the adjusting element67, in accordance with the sixth exemplary embodiment. Since one end of the helical coil65is connected to the fore end631of the rod63, and the other end of the helical coil65is connected to the adjusting element67, the helical pitch d6of the flow regulator6may be altered by the movement of the adjusting element67.

InFIGS. 14A and 14B, the helical pitch d6of the helical coil65is respectively defined as d61and d62. Compared with the condition shown inFIG. 14A, the adjusting element67inFIG. 14Bis moved more into the channel61(in other words, the adjusting element67is moved toward the rod63). Therefore, the helical pitch d62inFIG. 14Bwould be smaller than the helical pitch d61inFIG. 14A. As the working principle set out before, the smaller the helical pitch d6is, the bigger the flow resistance R will be. Therefore, the flow resistance R inFIG. 14Bis bigger than that inFIG. 14A. One the other hand, when a smaller flow resistance R in required, the adjusting element67may be moved more out of the channel61(in other words, the adjusting element67is moved away from the rod63) than the adjusting element67inFIG. 14Adoes. In such circumstance, the helical pitch d6of the flow regulator6will be larger, and the smaller flow resistance R is achieved as a result.

Now, please refer toFIGS. 15A and 15B. The operation demonstrating how the automatic compensation function of the flow regulator6works is described below with these figures.

InFIGS. 15A and 15B, the force F6provided by the helical coil65is respectively defined as F63and F64, the helical pitch d6of the helical coil65is respectively defined as d63and d64, the inlet pressure P6measured at the fluid inlet611of the channel61is respectively defined as P63and P64, and the outlet pressure Pcmeasured at the fluid outlet613of the channel61is respectively defined as P63′and P64′.

FIGS. 15A and 15Bare a series of schematic diagrams showing how the helical pitch d6of the helical coil65of the flow regulator6varies automatically along with the pressure change of the outlet pressure Pcmeasured at the fluid outlet613of the channel61, in accordance with the sixth exemplary embodiment of the present disclosure. Since the forces applied to the rod63are balanced and the operation of the flow regulator6follows previously mentioned formula (6): (F6+P6′×A6′=P6×A6), the rod63may move toward or away from the fluid inlet611as any of these forces changes.

FIGS. 15A and 15Bshows how the rod63moves when the outlet pressure P63′changes to P64′. To be more specific, when the pressure of a subsequent chamber (not shown) connected to the flow regulator6through the fluid outlet613is increased, the outlet pressure P63′inFIG. 15Awill increase to P64′inFIG. 15B(i.e. P64′>P63′). In such circumstance, the rod63will be forced to move more toward the fluid inlet611, the helical pitch d64of the helical coil65thus becomes larger (i.e. d64>d63) and the force F64provided by the helical coil65will thus become smaller (i.e. F64<F63), compared with the condition inFIG. 15A.

As the working principle set out before, the larger the helical pitch d6is, the smaller the flow resistance R will be. Therefore, the flow resistance R inFIG. 15Bis smaller than inFIG. 15A. When the flow resistance R gets smaller, the flow rate Q and the overall pressure in the flow regulator6will become larger in an automatically compensating manner. Similarly, when the outlet pressure P6′of the flow regulator6decreases, the rod63will be forced to move more away from the fluid inlet611, and the helical pitch d6will get smaller (and the force F6provided by the helical coil65will become bigger); thus increasing the flow resistances R.

From the above description, it is clear that the flow resistance R of the flow regulator6can be varied automatically along with the pressure change in the subsequent chamber (not shown) connected to the channel61through the fluid outlet613of the flow regulator6, which in turn causes the flow rate Q and overall pressure of the flow regulator6to be changed in an automatically compensating manner.

Next, please refer toFIGS. 16A and 16B. The operation of adjusting the helical pitch d7of the flow regulator7is described below with these figures.

FIGS. 16A and 16Bare schematic diagrams showing how to adjust the helical pitch d7of the first helical coil75of the flow regulator7by moving the adjusting element77, in accordance with the seventh exemplary embodiment. Since the rod73may move along the axial direction of the channel71, the first helical coil75is connected to the inner wall of the channel71and the rear end733of the rod73, and the second helical coil76is connected to the rear end733of the rod73and the adjusting element77, the helical pitch d7of the flow regulator7may be altered by the movement of the adjusting element77.

InFIGS. 16A and 16B, the helical pitch d7of the first helical coil75is respectively defined as d71and d72. Compared with the condition shown inFIG. 16A, the adjusting element77inFIG. 16Bis moved more into the channel71(in other words, the adjusting element77is moved more toward the rod73). Therefore, the helical pitch d72inFIG. 16Bwould be smaller than the helical pitch d71inFIG. 16A. As the working principle set out before, the smaller the helical pitch d7is, the bigger the flow resistance R will be. Therefore, the flow resistance R inFIG. 16Bis bigger than that inFIG. 16A. One the other hand, when a smaller flow resistance R in required, the adjusting element77may be moved more out of the channel71(in other words, the adjusting element77is moved more away from the rod73) than the adjusting element77inFIG. 16Adoes. In such circumstance, the helical pitch d7of the flow regulator7will be larger, and the smaller flow resistance R is achieved as a result.

Now, please refer toFIGS. 17A and 17B. The operation demonstrating how the automatic compensation function of the flow regulator7works is described below with these figures.

InFIGS. 17A and 17B, the first force F7provided by the first helical coil75is respectively defined as F73and F74, the second force F7′provided by the second helical coil76is respectively defined as F73′and F74′, the helical pitch d7of the first helical coil75is respectively defined as d73and d74, the inlet pressure P7measured at the fluid inlet711of the channel71is respectively defined as P73and P74, and the outlet pressure P7′, measured at the fluid outlet713of the channel71is respectively defined as P73′and P74′.

FIGS. 17A and 17Bare a series of schematic diagrams showing how the helical pitch d7of the first helical coil75of the flow regulator7varies automatically along with the pressure change of the outlet pressure P7′measured at the fluid outlet713of the channel71, in accordance with the seventh exemplary embodiment of the present disclosure. Since the forces applied to the rod73are balanced and the operation of the flow regulator7follows previously mentioned formula (7): (P7×A7+P7′×A7′+F7=F7′), the rod73may move toward or away from the adjusting element77as any of these forces changes.

FIGS. 17A and 17Bshows how the rod73moves when the outlet pressure P73′changes to P74′. To be more specific, when the pressure of a subsequent chamber (not shown) connected to the flow regulator7through the fluid outlet713is increased, the outlet pressure P73′inFIG. 17Awill increase to P74′inFIG. 17B(i.e. P74′>P73′). In such circumstance, the rod73will be forced to move toward the adjusting element77, and the helical pitch d74of the first helical coil75thus becomes larger (i.e. d74>d73), compared with the condition inFIG. 17A. As a result, the first force F7provided by the first helical coil75decreases (i.e. F74<F73), the second force F7′provided by the second helical coil76increases (i.e. F74′>F73′), and the final position of the rod73is determined by the force difference between the first and the second force F7and F7′.

As the working principle set out before, the larger the helical pitch d7is, the smaller the flow resistance R will be. Therefore, the flow resistance R inFIG. 17Bis smaller than inFIG. 17A. When the flow resistance R gets smaller, the flow rate Q and the overall pressure in the flow regulator7will become larger in an automatically compensating manner. Similarly, when the outlet pressure P7′of the flow regulator7decreases, the helical pitch d7will get smaller, and the flow resistances R thus increases.

From the above description, it is clear that the flow resistance R of the flow regulator7can be varied automatically along with the pressure change in the subsequent chamber (not shown) connected to the channel71through the fluid outlet713of the flow regulator7, which in turn causes the flow rate Q and overall pressure of the flow regulator7to be changed in an automatically compensating manner.

It will be apparent to those skilled in the art that various modifications and variations can be made to the structure of the disclosed embodiments without departing from the scope or true spirit of the present disclosure. In view of the foregoing, it is intended that the present disclosure covers modifications and variations of this disclosure provided that they fall within the scope of the following claims and their equivalents.