JP2001510268A - Volume delivery device with molded piston and molded cylinder - Google Patents

Abstract

(57) Abstract: A slider (12) comprising a molded product, which is a volume delivery maximizing device and is capable of moving bidirectionally within an elongated cavity (14) formed in a molded body (16). Is provided. The body (16) also includes a port structure (18) comprising an outlet port (18a) and an inlet port (18b), each forming a channel for communication between the cavity (14) and an off-body location. ing. The power device (22) causes bi-directional movement of the slider (12) within the cavity (14). The clearance between slider (12) and cavity (14) is greater than zero but less than about 0.0003 inches. The device of the present invention can be in the form of a pump, valve or motor.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD OF THE INVENTION

 This application is based on US Preliminary Application No. 60 / 052,839, filed Jul. 17, 1997, entitled VOLUMETRIC-DISPLACEMENT DEVICE.

The present invention generally relates to the technical field of fluid mechanics. More particularly, it relates to a novel volume delivery maximization device (which may also be considered a hydromechanical device) and a method of making its components. In accordance with the present invention, relatively small devices can be formed that are operable in various conventional applications, such as, for example, fluid pumps, fluid motors, and fluid flow controls (valves).

[0003]

2. Description of the Related Art

1A to 1C show various pumps according to the prior art so as to clarify the later-described features of the present invention. FIG. 1A shows a conventional diaphragm pump 1.
Is shown. In this pump 1, a reciprocating member 2 (reciprocating movement is indicated by an arrow A) is attached to a flexible diaphragm 3,
The reciprocating member 2 pushes the diaphragm toward the housing portion HS or pulls the diaphragm away from the housing portion HS. As a result of such an operation, the fluid contained in the space formed by the diaphragm 3 and the housing portion HS flows out of the outlet port 5a as shown by the arrow, or flows in the inlet port 5b as shown by the arrow. (The illustration of a check valve for controlling the inflow and outflow of the fluid through these desired ports is omitted). FIG. 1B schematically illustrates the fluid volume delivered when the diaphragm pump 1 operates. The volume in this case has a length L, a height H, and a width (not shown). FIG. 1C shows an oscillating pump 6 according to the prior art. This pump 6
For fluid outflow (through outlet port 9a) or fluid inflow (through inlet port 9b) from within each space formed by each flexible bulb 8 and housing portion HS. , A spherical part compression member 7 for alternately compressing the spherical part 8. From a volume delivery point of view, the fluid volume delivered by an oscillating pump such as pump 6 is equal to 2 × (0.5 × bulb height (BH) × bulb diameter).

[0004]

[Means for Solving the Problems]

Unlike conventional hydromechanical devices such as, for example, fluid motors, fluid pumps and fluid control valves, the structure of the present invention is essentially characterized by comprising two important central components. Is what you do. That is, a body in which a chamber for receiving and handling a fluid is provided, and a movable member such as a slider or a rotating body disposed in the chamber, which move to cause the fluid to flow. Or a movable member that moves to control the flow of the fluid or that moves in response to an externally applied pressurized fluid. No separate seal structure is used between the cooperating close abutment surfaces of the two components. In this case, preferably, the chamber has a generally circular cross section (although other shapes such as an oval shape are possible), such as a slider or a valve spool which forms a movable member. Such a member is, for example, cylindrical and has an outer surface that fits very tightly to the inner surface of the chamber, so that it can fit tightly rather than firmly.

[0005] In the present invention, the clearance between the two surfaces is in the range of about 0.0001 inches to about 0.0003 inches at all opposing locations.
Surprisingly, these surfaces can be formed, as the inventor has done, by choosing a suitable moldable plastic material, for example a structural thermoplastic material. The inventor has noted that the molding process itself does not require further machining or other processing to ensure such intimate contact, for example, preferably at least for moving parts (sliders, valve spools, etc.). A surface property that allows the seal to be easily slidable or rotatable relative to each other while ensuring a substantially leak free seal for a substantially infinite amount of time to maintain a fluid pressure differential of one atmosphere. I found it to bring.

The present invention provides a central cooperative structure comprising two members as described above and a method for molding the same. For example, in any case where the “diameter” of the chamber or the movable member is about 1 inch. Triggers the development of extremely small devices that do not exceed the limit, and also enables applications to fluid motors and pumps that can handle large volumes of fluid in a relatively short time, for example. It is.

[0007] These various features and objects and advantages attained by the structure and method according to the invention (all described below) are read in the following description with reference to the accompanying drawings, which form a part hereof. Will be clearer.

[0008]

BEST MODE FOR CARRYING OUT THE INVENTION

FIG. 1A is a partial cross-sectional view showing a first example of a conventional pump. FIG. 1B is a diagram schematically showing a delivery amount obtained in the conventional pump configuration shown in FIG. 1A. FIG. 1C is a partial sectional view showing a second example of the conventional pump. FIG. 2A is a partial cross-sectional view showing an embodiment forming a pump in the present invention. FIG. 2B is a diagram schematically showing the delivery amount obtained in the pump shown in FIG. 2A. FIG. 3 is a partial sectional view showing a first embodiment of the structure of the present invention. FIG. 4 is a partial cross-sectional view illustrating a second embodiment of the structure of the present invention, illustrating certain types of relative movement, fluid sealing, and fluid delivery movement. FIG. 5 is a partial cross-sectional view illustrating a third embodiment of the structure of the present invention, illustrating other types of relative movement, fluid sealing, and fluid delivery movement. FIG. 6 is a diagram schematically showing a feature of the present invention, and this feature can be added to any embodiment of the present invention. FIG. 7 is a diagram schematically illustrating a further feature of the present invention.
It can be added to any of the embodiments of the present invention. FIG. 8 is a perspective view showing a fourth embodiment of the present invention. FIG. 9 is an exploded perspective view of the fourth embodiment shown in FIG. FIG. 10 is a plan view of the fourth embodiment shown in FIG. FIG. 11 is a side view of the fourth embodiment shown in FIG. FIG. 12 is a perspective view showing an example of the reciprocating member in the fourth embodiment shown in FIG. 13 to 16 are cross-sectional views taken along line 13-13 in FIG. 8, and show the relative arrangement between the crank / cam members over a 360 ° rotation. FIG. 17 is a sectional view taken along line 17-17 in FIG. FIGS. 18 and 19 are perspective views of the fourth embodiment shown in FIG. 8, in which the micropump is cut away to show how the piston moves in the cylinder and how the piston moves in the cylinder. Is shown. FIG. 20 is an exploded perspective view showing a second configuration example of the fourth embodiment in FIG. FIG. 21 is a cross-sectional view taken along line 21-21 of FIG. 20, showing a cam member. FIG. 22 is a cross-sectional view showing a modification of the cam member shown in FIG. 23 to 26 are sectional views taken along the line 23-23 in FIG. 8, and show the relative arrangement between the members over a 360 ° rotation of the crank / cam member. FIG. 27 is a perspective view showing a second configuration example of the reciprocating member in the fourth embodiment shown in FIG. FIG. 28 is a plan view showing a fifth embodiment of the present invention. FIG. 29 is a plan view showing a sixth embodiment of the present invention. FIG. 30 is a plan view showing a seventh embodiment of the present invention.

[0009] Following the description of the drawings, the background of the invention will be described with text and illustration, and then the present invention and a method of practicing the same will be described.

Prior to the description, some preliminary considerations should be understood. First, FIGS. 3-7 enable an understanding of the various embodiments of the present invention. As will be appreciated, the invention can take various forms, such as a pump, a valve, and a motor. 3 to 7 are diagrams for enabling understanding of each of these embodiments. Second, although the present invention uses the prefix "micro", it only defines the size and does not imply micromachining.

Third, as will be described later, an object to which the present invention is applied is a micropump for a vital sign monitor such as an oscillatory non-invasive blood pressure measurement (NIBP). . A commercially available example of this device is PROPAQ ENCORE manufactured by Protocol Systems Inc. of Beaverton, Oregon. No. 4,949,710 to Dorsett et al. And US Pat. No. 5,339,822 to Taylor et al. And Nelson. And co-pending U.S. patent applications Ser. Nos. 08 / 673,318, 08 / 883,754, 08/8 by NIBP MEASURING SYSTEM.
No. 84,359 is incorporated by reference.

FIGS. 1A to 1C show various pumps according to the prior art so as to clarify the features of the present invention described later. FIG. 1A shows a conventional diaphragm pump 1.
Is shown. In this pump 1, a reciprocating member 2 (reciprocating movement is indicated by an arrow A) is attached to a flexible diaphragm 3,
The reciprocating member 2 pushes the diaphragm toward the housing portion HS or pulls the diaphragm away from the housing portion HS. As a result of such an operation, the fluid contained in the space formed by the diaphragm 3 and the housing portion HS flows out of the outlet port 5a as shown by the arrow, or flows in the inlet port 5b as shown by the arrow. (The illustration of a check valve for controlling the inflow and outflow of the fluid through these desired ports is omitted).

FIG. 1B schematically shows the fluid volume delivered when the diaphragm pump 1 operates. The volume in this case has a length L, a height H, and a width (not shown).

FIG. 1C shows an oscillating pump 6 according to the prior art. This pump 6
For fluid outflow (through outlet port 9a) or fluid inflow (through inlet port 9b) from within each space formed by each flexible bulb 8 and housing portion HS. , A spherical part compression member 7 for alternately compressing the spherical part 8. From a volume delivery point of view, the fluid volume delivered by an oscillating pump such as pump 6 is equal to 2 × (0.5 × bulb height (BH) × bulb diameter).

FIG. 2A illustrates a volume delivery maximizing device 10 according to the present invention, which includes a molded slider 12 that is bi-directionally movable within an elongated cavity 14 formed within a molded body 16. It has. The body 16 also includes a port structure 18 having an outlet port 18a and an inlet port 18b. Each of the outlet port 18a and the inlet port 18b forms a channel for communication between the cavity and an off-body location. Power device (not shown)
The slider 12 is moved bidirectionally within the cavity 14. Slider 1
The clearance between 2 and cavity 14 is greater than 0, but about 0.0
Less than 003 inches (0.00762 mm).

FIG. 2B schematically illustrates the fluid volume that can be delivered when using the device 10. The volume in this case has a length L, a height H, and a width (not shown). Assuming the same width, how the present invention maximizes fluid delivery volume compared to prior art pumps as shown in FIGS. 1A and 1C is:
Easy to understand. Compared to other micropumps that can be used as vital signs monitors, the present invention is evaluated as having increased fluid delivery to 280%.

In the present invention, the book that achieves the large volume delivery of fluids as outlined is only by using molded parts that meet the above clearance requirements to provide a substantially leak-free interface seal. It is important to note the unique features of the invention. Device 10 does not use O-rings, sealants, or other sealing materials.

Preferably, slider 12 and body 16 are formed from an injection molded plastic material, such as is commercially available under the trademark ULTEM. This material is dimensionally stable, self-lubricating and has effective resistance to water absorption. As described below with reference to FIGS. 8-14, the device 10 can take the form of a molded micropump for vital signs monitoring. Also, as described below, the power device transmits power from the applied voltage. In this case, the slider 12 can be moved bidirectionally in the cavity 14 by changing the applied voltage. Preferably, the slider 12 has a curved outer surface, and the cavity 14 has a circular or elliptical cross-sectional shape.

Referring to FIGS. 3-7, various aspects of the invention will be described by way of illustrations shown in the drawings. Referring to FIG. 3, a first aspect of the present invention will be described. The fluid mechanical device 10 is selectively operable as a motor, a pump, or a valve with respect to control of fluid flow conditions and according to fluid flow conditions. . Device 10 has a body 16 that is not machined. The body 16 includes a long fluid chamber 14 having a longitudinal axis LA and a long inner wall surface 16a surrounding the axis LA. The long, unmachined movable slider 12 has spaced apart opposite ends 13a, 13b, and accommodates reversible sliding conditions with very little clearance in the chamber 14. It has an outer surface 12a. The slider 12 is in contact with a wall surface 16a surrounding the axis LA so as to be reversibly movable in the chamber along the axis LA. The wall surface 16a and the slider outer surface 12a are in contact with each other in a self-sealing state. This situation is caused by the separated ends 13a of the slider 12,
The fluid pressure difference on 13b can be maintained indefinitely with no leak. Such a pressure difference is about one atmosphere or more. Preferably, the material forming each of body 16 and slider 12 has substantially the same coefficient of thermal expansion. Also, the body and the slider are preferably formed from the same, moldable plastic material.

Referring again to FIG. 3, a second aspect of the present invention will be described. The fluid mechanical device 10 is selectively operable as a motor, pump, or valve with respect to controlling fluid flow conditions and according to fluid flow conditions. Device 10 includes a molded body 16 having an elongate fluid chamber 14 having a longitudinal axis LA. The chamber 14 is at least partially formed by an elongated cylindrical inner wall surface 16a. The inner wall surface 16a is in the axial LA around and has a first radius of curvature R _1.
The axis LA forms a cylindrical center line formed by the inner wall surface 16a.

Still referring to FIG. 3, an elongated molded movable cylindrical slider 12 is disposed in the chamber 14 in a state of being accommodated in a reversibly slidable manner with a very small clearance. The slider 12 is provided with a cylindrical outer wall 12a, the radius of curvature R ₂ of the outer wall 12a is a is slightly smaller than the radius of curvature R _1, the effective sealing abutment against the inner wall surface 16a It can be done. Slider 1
2 is also reversibly movable in the direction indicated by arrow A along the axis LA within the chamber. The wall surface 16a of the body and the wall surface 12a of the slider abut each other in a self-sealing state. This situation is due to the slider 12
The fluid pressure difference on both ends 13a, 13b can be maintained indefinitely with no leak. Such a pressure difference is about one atmosphere or more. Preferably, the difference between the radii of curvature R ₁ and R ₂ is no more than about 0.0003 inches, and more preferably, no more than about 0.0001 inches to about 0.0003 inches. Things. In FIG. 3, the difference between the lengths of R ₁ and R ₂ indicated by arrows R ₁ and R ₂ in the extension of the left side of FIG. 3 is illustrated with a slight difference. It should be understood that this has been exaggerated for illustration. In essence, the image of the slider 12 located in the chamber 14 consists of an outer concentric circle (chamber 14) and an inner concentric circle (slider 12) having a radius of curvature slightly smaller than its radius of curvature. Approximated by two concentric circles.

Next, a third aspect of the present invention will be described. The fluid mechanical device 10 is selectively operable as a motor, pump, or valve with respect to controlling fluid flow conditions and according to fluid flow conditions. The device 10 has an elongated molded body 16. Inside the body 16 are two elongated, generally cylindrical chamber structures 14a,
14b is provided, each of these chambers structures 14a, 14b has a corresponding interior wall surface 14a _1, 14b _1, the longitudinal axis LA, a. The chamber structures 14a, 14b are spaced apart from each other and are arranged in a relative relationship that is generally aligned in the axial direction, and are arranged adjacent to both ends 17a, 17b of the body 16.

For each of the chamber structures 14a, 14b, each of the chamber structures 14a, 1
Long molded movable sliders 13a and 13b are arranged so as to be slidable within 4b. Each slider has an outer wall surface 13a ₁ , 13b ₁ which is in direct and fluid-tight contact with the respective inner wall surface 14a ₁ , 14b ₁ of the associated chamber structure 14a, 14b. The chamber structures associated with each slider abut each other via their respective wall-to-wall abutments which form a self-sealing situation with each other. In this situation, the fluid pressure difference on both ends 13a, 13b of the slider 12 can be maintained indefinitely with no leak. Such a pressure difference is about one atmosphere or more.

Continuing further with the description of the third aspect of the present invention, as schematically indicated by the dashed line in FIG. (Shown) is provided in the central portion of the body 16. The power transmission means 19 is movable as an articulated member to each of the sliders 13a and 13b, and is connected to each of the sliders so as to transmit power. The power transmission means 19 is connected to each slider so that the slider can be reciprocated reciprocally in the direction of arrow A as an essentially integral member. By this reciprocating movement,
Fluid flow is provided to each chamber structure 14a, 14b.

Referring to FIG. 3, a fourth aspect of the present invention will be described.
It includes an elongated molded body 16 in which two elongated, generally cylindrical chamber structures 14a, 14b are spaced apart from each other and generally axially. Aligned and positioned. Each end 17a, 17 of the body 16
b, each chamber structure has a generally cylindrical inner wall surface 1.
4a ₁ and 14b ₁ are provided. The molded piston 12 includes a plurality of chamber structures 14a, 14
b, sub-pistons 13a slidably arranged and spaced apart from each other
, 13b. The piston 12 has a generally cylindrical outer wall surface 12a.
(More precisely, the surfaces 13a ₁ , 13b ₁ of the sub-piston 13), the outer wall surfaces 12a of which correspond to the corresponding inner wall surfaces 14a ₁ , 14a ₁ , 14b of the associated chamber structure 14a, 14b.
14b ₁ slidably abuts directly and in a fluid-tight manner. Such a seal abutment creates a seal situation in which the fluid pressure differential across each sub-piston, which exceeds about one atmosphere, can be maintained indefinitely in a leak-free state. The pump 10 also includes an elongated driver 20 schematically illustrated by a thick dashed line. The elongated driver 20 extends to an intermediate portion within the body 16 and integrates the sub-pistons 13a, 13b as an integral member so as to deliver a fluid (not shown) contained within the chamber structures 14a, 14b. The sub-pistons 13a and 13b are drivably connected so as to be able to reciprocate in the direction of arrow A. An appropriate power motor 22 (which is drivingly connected to the driver 20 via the power transmission means 19)
(Shown schematically) to provide a reciprocating drive of the driver 20 and, via the driver 20, the sub-piston 13a
, 13b.

A fifth aspect of the present invention will be described with reference to FIG.
0 comprises a molded valve body 16 in which a fluid flow control chamber structure 14 is formed. Referring to FIG. 2A, the fluid passage structure 18
Has a pair of ports 18a, 18b in communication with the chamber structure 14 and open to the chamber structure. Disposed within the chamber structure 14 is an adjustable movable movable valve spool 12. The valve spool 12 is connected to the passage structure 18 and the chamber structure 14 through at least one of the ports 18a and 18b.
It is selectively movable by an applied driving force so that the degree of fluid communication allowed between the two can be changed. The valve spool 12 and the chamber structure 14, except in the region where the ports 18a, 18b are present, are in a sealing situation such that a fluid pressure differential of at least greater than about 1 atmosphere can be maintained indefinitely in a leak-free state. Thus, they are in direct seal contact with each other.

Referring to FIG. 3, a sixth aspect of the present invention will be described. The fluid motor 10 includes a molded motor body 16 in which a fluid delivery chamber structure 14 is formed. I have. In the chamber structure 14, the moving delivery structure 12, which is a molded product, is disposed. The moving delivery structure 12 can be moved periodically in the direction of arrow A by selective and periodic application of a pressurized fluid (not shown) in the chamber structure. The chamber structure 14 and the mobile delivery structure 12 have at least about 1
In a continuous sealing situation in which a fluid pressure difference exceeding the atmospheric pressure can be maintained indefinitely in a leak-free state, it operates by relative movement in a state where the fluid seals are in direct contact with each other. The motor 10 also includes a power output drive coupler 20.
It has. The coupler 20 is drivably connected to the moving delivery structure 12 and transmits drive output power to a selected external device via a power transmission means such as that indicated by reference numeral 19. So that it can work.

Referring to FIG. 3, a seventh aspect of the present invention will be described.
0 is selectively operable as a motor, pump or valve, especially for controlling the fluid flow conditions and according to the fluid flow conditions. Device 10 includes a molded body 16, which includes an elongated fluid chamber 14. The chamber 14 has a longitudinal axis LA, and has a long inner wall surface 16a extending around the axis LA. The long molded movable slider 12 can be reversibly slid with very little clearance in the chamber 14, and the outer wall directly abuts the inner wall 16a extending around the axis LA. 1
2a. The slider is reversibly movable along the axis LA within the chamber. The chamber 14 and the slider 12 are configured to be able to operate in an operation situation in which a pressure difference is applied between both ends of the slider 12 (the slider 12).
Are shown as sub-sliders 13a and 13b). Chamber 1
If there is no external force acting on the fluid inside 4 that causes compression or suction, the axis LA
By moving the slider 12 over a distance L in the direction, A is the effective operating surface area of the slider with respect to the delivered fluid of the slider, and L is the travel distance of the slider with respect to the chamber 14 during delivery, resulting in a volume ( A.times.L) of fluid, either positive or negative.

Referring to FIG. 3, an eighth aspect of the present invention illustrates a fluid mechanical device 10 for providing various fluid flow conditions in motors, pumps, valves, and the like. Device 10 includes a body 16 formed of a suitable moldable material.
The body 16 has a long fluid chamber 14 having a longitudinal axis LA and a long inner wall surface 16a. The inner wall surface 16a is formed by the axis LA and the inner wall surface 1.
6a, when viewed from a direction perpendicular to a plane intersecting both of them. The intersection with respect to the axis LA is substantially an orthogonal intersection, and the inner wall surface 16a is in a mutually cooperative face-to-face local direct contact with another surface having similar surface characteristics. The surface quality of the molding such that it has a selected predetermined local flatness to provide the desired desired fluid sealing performance.

Continuing with the description of the eighth aspect, device 10 also includes an elongated slider 12 formed from the same moldable material as body 16. The slider 12 has a longitudinal axis LA and a long outer wall surface 12a. Similarly, the outer wall surface 12a is characterized by a curve around the axis LA when viewed from a direction perpendicular to a plane intersecting both the longitudinal axis LA of the slider and the outer wall surface 12a. . The intersection in this case with respect to the longitudinal axis LA of the slider is likewise substantially an orthogonal intersection, the outer wall surface 12a being substantially different from the surface properties of the inner wall surface 16a of the chamber. It has the surface quality as a suitable molded product. The slider 12 is also slidably disposed within the chamber 14. In this case, the inner surface 16a and the outer surface 12a consequently are in mutually cooperative, face-to-face local direct contact with each other to achieve the desired desired fluid sealing performance. This fluid sealing performance is sufficient to prevent the occurrence of fluid leak between both wall surfaces even in a situation where a fluid pressure difference of up to about 1 atm appears between both ends of the slider 12 in the chamber 14. It is something. Both ends of the slider 12 are shown as sub-sliders 13a, 13b spaced apart from each other.

Referring to FIG. 3, with reference to a ninth aspect of the present invention, the hydromechanical device 10 is operable with respect to controlling specific fluid flow conditions in various selected fluid delivery applications, and And / or operable in response to such specific fluid flow conditions. Device 10 includes a body 1 formed of a suitable moldable material.
6 and the body 16 includes a fluid chamber 14. The fluid chamber 14 is at least partially formed by a fluid impermeable surface structure 14a. Device 10 also includes a relative displacement member 12 formed from the same moldable material as body 16. The relative movement member 12 has a fluid impermeable surface structure 12a, and can relatively move in a fluid-tight manner so as to be able to deliver fluid while being adjacent to the surface structure 14a of the chamber. Such a fluid delivery movement is characterized by a movement line in which a fluid seal-like surface opposition between the two surface structures is made. This line forms a fluid seal moving boundary for the fluid present in the chamber. Fluid movement at such a boundary results in positive or negative fluid inflow and outflow in chamber 14 depending on the direction of movement. Such a sealing situation along the line is capable of maintaining an infinite leak-free characteristic with respect to a fluid pressure difference exceeding about 1 atm across the line. In FIG. 3, an example of such a movement line made by the fluid seal-like surface opposition is between any two points along the boundary between any of the sub-members 13a, 13b of the relative movement member 12 and the wall surface 16a. The interval.

The tenth aspect of the present invention will be described with reference to the ninth aspect and FIG. FIG. 4 shows relevant parts of the hydromechanical device 110, and the device 11
0 comprises an annular relative movement member 112. The annular relative movement member 112 rotates within a generally spherical chamber 114. For this reason, the movement line which makes the fluid seal-like surface contact is endless. FIG. 4 shows this embodiment and FIG.
Except for the specific differences described below that exist between the
The same as the section taken along line -4. In the description of FIG. 3, it will be appreciated that there is a slight difference between the radius of the member 112 and the radius of the chamber 114. In this case, as in the seventh aspect, arrow A indicates the effective operating surface area of the slider with respect to the fluid to be delivered. A channel 112b is formed in the member 112, the channel 112b being capable of communicating with a port 118, which allows fluid to be delivered from the chamber 114.
Other parts of the device 110 are the same as those of the device 10 described in the ninth aspect.
Is the same as

The eleventh aspect of the present invention will be described with reference to the ninth and tenth aspects and FIG. FIG. 5 illustrates relevant portions of a hydromechanical device 210, which includes a relative displacement member 212. The relative movement member 212 is capable of rolling and translation within the chamber 214 to provide a desired fluid delivery. In this case, the other parts of the device 210 are the same as those of the device 10 described in the ninth aspect.

Returning to FIG. 3, a twelfth aspect of the present invention will be described.
Is a molded body 1 forming a cavity 14 for containing a fluid (not shown).
6 is provided. The molded body includes an outlet port 18a to allow communication between the cavity 14 and a desired external location. The device 10 also includes a molded fluid seal / fluid delivery structure 12 movably disposed within the cavity 14. Structure 12 may include substructures 13a, 13b. When the body 16 and the fluid seal / fluid delivery structure 12 move relative to each other, the device 10 is selectively operable to prevent fluid flow out of the cavity through the outlet port 18a (in solid lines). (See location of substructure 13a shown). The device 10 is connected to the exit port 1
It is optionally possible to operate to allow fluid outflow from the cavity through 8a (see the position of substructure 13a shown in dashed lines).
The device 10 further comprises a drive structure such as, for example, a driver 20, a power transmission means 19 and a motor 22 to cause relative movement between the structure 12 and the body 16.

Referring again to FIG. 3, a thirteenth aspect of the present invention, the fluid delivery device 10 includes a molded body 16 forming a cavity 14 for containing a fluid (not shown). . The body also includes an outlet port 18a to allow communication between the cavity 14 and a desired external location. Device 10 is
It also has a fluid seal / fluid delivery structure 12 consisting of a molded article with sub-structures 13a, 13b. Structure 12 has a first position (substructure 13a shown in solid lines).
) And a second position (see the position of the substructure 13a indicated by a dashed line) in the cavity 14 so as to be movable. Structure 12 is also optionally operable to prevent fluid outflow from cavity 14 through outlet port 18a in a first position and through outlet port 18a in a second position. The cavity 14
It is optionally possible to operate to allow for fluid outflow from the device.

With reference to FIGS. 6 and 7, additional features in various aspects will be described. These additional features illustrate how the slider member (or piston member) moves. In FIG. 6, a single motor 22 drives the drivers 26a and 26b via cranks, and ultimately, the sub-sliders 13a and 13a.
3b is driven in a desired direction. In FIG. 7, two motors 22a and 22b are
Finally, the sub-sliders 13a and 13b are driven in desired directions. These feature points will be further described later.

Referring now to FIG. 8, an example of the present invention, illustrated as a micropump suitable for application to vital signs monitors, such as the PROPAQ ENCORE monitor by Protocol Systems described above, for example, explain. In FIGS. 8-11, a fourth embodiment of the present invention is illustrated by reference numeral 310 in the form of a micropump for vital signs monitoring. The pump 310 has a molded body 316. The body 316 includes a central region 316a and the outlet port 31.
8a. The body 316 includes a chamber 314 having a cylinder 315.
Is formed. Within the cylinder 315, a slider structure 312 (the slider structure 312 includes sub-sliders or pistons 313a, 313b).
Can be moved in both directions. The pistons 313a and 313b are
20, the driver 320 is connected via the slider reciprocating member 330 and the cam / crank 332 so as to be driven by the crankshaft 328 a of the motor 328.

Furthermore, as shown in FIG. 9, the rounded ends of the driver 320 are arranged in a socket such as the socket 313 a ₁ so that each piston 31
Appropriately attached to 3a, 313b. The valve plate 334 and the manifold 336 located at both ends seal the outer ends of the sub-sliders 313a, 313b with respect to the central region 316a, for example, by ultrasonic welding or other suitable connection direction. Properly connected. A suitable check valve 337 controls fluid flow and the motor mounting plate 338 is properly coupled to the central region 316a. For assembly purposes, each check valve has a sharp end that projects beyond the ridge (FIG. 9). These sharp ends are cut by a suitable cutting device after assembly so that they do not protrude into the cavity formed by the cylinder 315 (FIGS. 13-16).

The resulting micropump 310 is therefore a molded article, preferably a plastic device formed from a plastic material sold under the trademark ULTEM. 10 and 11 show a plan view and a side view of the pump 310, respectively.

Returning to FIG. 9, another feature of the present invention will be described. Micro pump 310
Has a crank structure for driving the slider 312 bidirectionally. This crank structure includes a motor shaft 328a, a reciprocating member 330, and a crank / cam 332. The rotation of the crankshaft 328a about an axis corresponding to the longitudinal axis of the shaft 328a causes the cam 332 and the reciprocating member 330 to rotate.
Bidirectional movement of the slider 312 via the drive connection of members such as the driver and the driver 320 is caused. Cylindrical end 3 connected by long driver 320
Based on the configuration of the slider 312 having 13a, 313b, a barbell configuration in which both ends (pistons) are interconnected by a central bar (driver 320) is obtained.

FIG. 12 is a diagram showing a side surface of the slider reciprocating member 330 located on the motor 328 side. This figure illustrates the presence of a recess that can receive the cam / crank 332. The pin 332 a is eccentric from the rotation axis of the motor shaft 328 a and the cam / crank 332 and has a slot 333 formed in the member 330.
Project from As described below, based on this eccentric arrangement, translation of the piston within the cylinder 315 is provided by the pin 332a.

FIGS. 13-16 show how rotational movement of the motor shaft 328 a and cam / crank 332 causes bidirectional translation of pistons 313 a, 313 b within cylinder 315. FIG. 13 shows a state that can be regarded as a starting state in which the crank of the cam / crank 332 presses the side surface of the member 330 located on the piston 313b side and moves to one end of the cylinder 315. . FIG. 14 shows the arrangement of the cranks when the motor shaft 328a and the cam / crank 332 are rotated 90 degrees counterclockwise. FIG.
The motor shaft 328a and the cam / crank 332 move 9 more times in the counterclockwise direction.
13 shows the arrangement of the crank when rotated by 0 °. In this case, the crank of the cam / crank 332 presses the side surface of the member 330 located on the piston 313a side, and FIG. Are moved to the opposite end.
FIG. 16 shows the arrangement of the cranks after the motor shaft 328a and cam / crank 332 have completed their fourth 90 ° counterclockwise rotation. Of course, the motor shaft 328a is typically continuously rotating, causing a continuous reciprocation of the piston within the cylinder. This reciprocation results in continuous air intake through the check valve and delivery through outlet port 318a. Further, the rotational movement may be clockwise or counterclockwise.

FIGS. 18 and 19 show the cylinder 3 in FIGS. 13 and 15, respectively.
It is a perspective view showing the arrangement situation of the piston in 15.

FIG. 20 is a view similar to FIG. 9, showing a second configuration of the cam / crank and the slider-like reciprocating member. In this embodiment, the swing degree of the slider reciprocating member with respect to the cam / crank is smaller. In FIG. 20, a cam member 332 'having a pin 332a' and a slider reciprocating member 3
30 'are shown. All other configurations are the same as those described with reference to FIG. FIG. 21 is a cross-sectional view showing the cam member 332 ′,
a 'is shown eccentric from the center of the elliptical cam 332'. FIG. 22 is a cross-sectional view showing another embodiment 332 "of the cam member, in which the pin 332a" is eccentric from the center of the circular cam 332 ". The components can operate within the micropump, depending on the holding, delivery, and timing variables as required in a given application.

Next, FIGS. 27 and 23 to 26 show how the rotational movement of the motor shaft 328 a and the cam 332 ′ causes the bidirectional translation of the pistons 313 a and 313 b in the cylinder 315. . FIG. 27 shows a side surface of the slider reciprocating member 330 ′ on the side close to the motor 328. This figure shows the presence of a recess that can receive the cam 332 '. Pin 332a '
Is eccentric from the rotation axis of the motor shaft 328a and the cam 332 ',
It protrudes from a slot 333 'formed in the member 330'. As described below, based on this eccentric arrangement, translation of the piston within cylinder 315 is provided by pin 332a '.

FIG. 23 shows a state that can be regarded as a departure state in which the cam 332 ′ presses the side surface of the member 330 ′ located on the piston 313 b side and moves to one end of the cylinder 315. I have. FIG. 24 shows the motor shaft 328a and the cam 33.
2 shows the arrangement of the crank when 2 ′ is rotated 90 ° counterclockwise. FIG. 25 shows the arrangement of the crank when the motor shaft 328a and the cam 332 ′ are further rotated 90 ° in the counterclockwise direction.
'Presses the side surface of the member 330' located on the piston 313a side to move it to the end of the cylinder 315 on the opposite side to that in FIG. FIG. 26 shows the arrangement of the cranks after the motor shaft 328a and cam 332 'have completed their fourth 90 ° counterclockwise rotation. Of course, the motor shaft 328a is typically continuously rotating, causing a continuous reciprocation of the piston within the cylinder. This reciprocation results in continuous air intake through the check valve and delivery through outlet port 318a. Further, the rotational movement may be clockwise or counterclockwise.

FIG. 28 shows a fifth embodiment of the present invention as a micropump 410. The micropump 410 includes pressure transducers 440a and 440b and two valves 442a and 442b, and can be used for measuring blood pressure in the vital sign monitor described above.

FIG. 29 shows a sixth embodiment of the present invention as a micropump 510. This micropump 510 includes two ports 518a, 518b and two motors 528b, 528c, and can be used for blood pressure measurement in the vital sign monitor described above.

FIG. 30 shows a seventh embodiment of the present invention as a micropump 610. The micro pump 610 includes two ports 618a and 618b, two pressure transducers 640a and 640b, two valves 642a and 642b, and two motors 628a and 628b. Can be used for blood pressure measurement on a monitor.

In the method of the present invention, it is important to consider the five basic steps of forming an injection molded part. The following is a list of these steps. 1. Member configuration 2. 2. Mold configuration 3. Mold assembly / manufacture Injection molding process5. Configuration for Assembly (DFA)

In each of the above steps, a plurality of guidelines as described below should be followed.
The guidelines described are the most important ones currently known. However, the following description does not exclude other implementations.

1. Component configuration For certain plastics, the functional requirements of each component and the knowledge of construction rules and guidelines must be followed. These requirements, rules and guidelines include:・ Uniform wall thickness ・ Material selection ・ Material restrictions ・ Functional requirements ・ Structural requirements ・ Thermal requirements ・ Composition standards for materials

[0053] 2. Mold structure The mold structure is such that the members are sufficiently heated and cooled, the function of the mold for preventing warpage is sufficiently exhibited, and the member having an allowable error is obtained. Must be able to guarantee that the functions of the above are fully exhibited. The important elements are:・ Tool material type ・ Tool cooling ・ Tool heating ・ Runner configuration ・ Formation of features (slider, cavity, core) ・ Lock between members ・ Guided injection ・ Sensors (temperature, pressure)

[0054] 3. Die assembly / manufacture Various types of material manufacture must be considered to meet the required tolerances. Tool hardness and temperature limitations are related to tool life. The important factors are:・ Cutting (milling) ・ Grinding (grinding) ・ Electrical discharge machining (EDM) ・ Custom shape or standard shape ・ Mold base (custom or standard)

[0055] 4. Injection molding process This is the process where the plastic comes into contact with the tool. In order to achieve the desired result, all the following parameters must be met. Cavity pressure is measured to check if the device is operating within certain tolerances and to check if the cavity is uniformly filled with fluid in a repeatable manner It is desirable. Statistical process controls are implemented to verify and track the molding process. The important factors are:・ Selection of injection molding equipment (volume, size) ・ Material drying ・ Pouring temperature ・ Pouring speed ・ Molding pressure ・ Mold pressure ・ Mold temperature ・ Holding time ・ Test (tolerance, shape) ・ Post-processing Heat treatment)

[0056] 5. Configuration for assembly A test procedure for the assembly process is performed to check whether functional requirements are met and to provide a means for statistical process control. The important factors are:・ Minimum parts ・ Low assembly cost ・ Minimum handling ・ Process flow ・ Fixation of assembly ・ Functional test ・ Packaging / packing of parts

Although the invention has been illustrated and described with reference to preferred embodiments, it will be obvious to those skilled in the art that changes may be made in form and detail without departing from the spirit and scope of the invention. .

The invention is further described in the following sections.

[0059] 1. A micropump made of a molded product for maximizing volume delivery for a vital sign monitor, having an outlet port and a long cavity formed therein,
A molded micro-body having a channel structure for providing communication between the cavity and the outlet port; and a molded body movable bidirectionally within the cavity. A power device connected to the slider so that the slider can move bidirectionally within the cavity, wherein a clearance between the slider and the cavity is less than zero. A micropump characterized by being large, but smaller than about 0.0003 inches.

[0060] 2. 2. The micropump according to claim 1, wherein the power device transmits power resulting from an applied voltage, and changes the applied voltage to cause the slider to move bidirectionally in the cavity. Micro pump.

[0061] 3. The micropump according to claim 1, wherein the slider has a curved outer surface.

[0062] 4. The micropump according to claim 3, wherein the cavity is formed to have a circular or elliptical cross-sectional shape.

[0063] 5. 2. The micropump according to claim 1, wherein the microbody and the slider are formed of a material having dimensional stability, self-lubricating property, and effective resistance to water absorption. And a micropump.

[0064] 6. The micropump according to claim 5, wherein the material is plastic.

[0065] 7. The micropump according to claim 6, wherein the material is injection-molded.

8. 2. The micropump according to claim 1, further comprising a crank structure for causing the slider to move bidirectionally, wherein the power device includes a motor coupled to the crank structure so as to drive the crank structure. Wherein the crank structure is connected to the slider so as to drive the slider, and wherein axial movement of the crank structure with respect to a crankshaft (or rotational movement of the crank structure around a crankshaft) is provided, A micropump characterized by causing a bidirectional movement of a slider.

9. The micropump of claim 8, wherein the crank structure comprises a crankshaft having an outer surface and a central region, the micropump further positioning the crankshaft of the crankshaft to a position adjacent to the outer surface. A micropump characterized by comprising a capacity delivery maximizing structure capable of engaging with the crankshaft so as to be moved away from the central region.

10. The micropump according to claim 9, wherein the slider is formed in a barbell configuration in which two pistons arranged at both ends are connected by a center bar.

11. The micropump according to claim 1, wherein the power device includes a first motor and a second motor each of which is operably connected to a corresponding first crank structure and a second crank structure, wherein each crank structure is A micropump characterized in that the slider is drivably connected to the slider.

12. The micropump of claim 1, wherein a pneumatic capacitor is disposed within the channel structure.

13. A meterable self-sealing push-pull micropump having an outlet port and having a substantially cylindrical cavity formed therein communicating with the outlet port. A pump housing made of injection-molded and made of high-density plastic, which is stable, has low water absorption, is self-lubricating, and is made of high-density plastic; A pair of spaced apart and interconnected pistons having outer surfaces; and a power device connected to the pistons so that the pistons can move bidirectionally within the cavity. Wherein the clearance of the outer surface of the piston with respect to the cavity is greater than zero but about 0.000 Micropump, wherein less than an inch.

14. A method for optimal volume delivery in a micropump, wherein the piston structure is selected in terms of both accommodation in the cylinder structure and use in the micropump; The clearance between them is at most about 0.
Controlling the clearance between the piston structure and the cylinder structure to be 0003 inches.

15. The method according to claim 14, further comprising selecting a crank structure that is movable about a crank axis so as to drive the piston structure within the cylinder structure; a crankshaft having an outer surface and a central region. Selecting a crank structure comprising: moving the crankshaft to a position adjacent the outer surface and away from the central region.

16. A volume delivery maximizing device, comprising a molded body having an inner surface defining a long fluid containing cavity; and an outer surface disposed adjacent to the inner surface of the body; A slider made of a molded product, which is movable in both directions in the cavity; and a boundary surface seal is provided between the body and the slider. The clearance between the inner surface of the body and the outer surface includes a first clearance threshold having a first driving force, and a second clearance threshold having a second driving force. A device for causing relative movement under a set of operating conditions, wherein the second clearance threshold is smaller than the first clearance threshold.

17. A volume delivery maximizing device, comprising: a molded body in which an elongated fluid containing cavity is formed; and a molded slider movably bidirectional within the cavity. An axis alignment exists between the slider and the cavity, and the axis alignment determines a clearance between the slider and the cavity with a first threshold having a first driving force. A device having a second threshold value and a clearance having a second driving force less than the first driving force.

18. A method for optimizing fluid delivery in a molded fluid delivery device configured to deliver fluid by movement of a slider within a fluid containing cavity, selecting a molding material to form the fluid delivery device; Molding a fluid delivery device comprising a slider and a fluid containing cavity; axially aligning the slider within the cavity; wherein in the axial alignment, a first driving force is applied to a clearance between the slider and the cavity. Having a first threshold value for the clearance,
Setting a clearance second threshold value having a second driving force smaller than the driving force.

19. A method for optimizing fluid delivery in a molded fluid delivery device configured to deliver fluid by movement of a slider within a fluid containing cavity, selecting a molding material to form the fluid delivery device; Molding a fluid delivery device comprising an elongate slider and an elongate fluid containing cavity that is substantially leak free for substantially infinite time with respect to fluid pressure conditions within the cavity. And how.

20. 20. The method according to claim 19, wherein in the molding step, molding is performed such that the fluid pressure condition of 15 psig is substantially leak-free for substantially infinite time. Method.

21. 20. The method of claim 19, wherein the molding step is substantially leak free for substantially infinite time for a fluid pressure condition of 125 psig,
A method characterized by performing molding.

22. 22. The method of claim 20 or 21, wherein the molding step comprises molding a cylindrical cavity having a diameter of at most about 1 inch.

23. A method for optimizing fluid delivery in a molded fluid delivery device configured to deliver fluid by movement of a slider within a fluid containing cavity, selecting a molding material to form the fluid delivery device; Molding a fluid delivery device comprising an elongated slider and an elongated fluid containing cavity; a clearance between the slider and the cavity, a first threshold having a first driving force; The clearance between the cavity and the slider only by performing an alignment between the cavity and the slider as characterized by a clearance second threshold having a second driving force less than one driving force. Forming a seal therebetween.

24. A method for optimizing fluid delivery in a molded fluid delivery device configured to deliver fluid by movement of a slider within a fluid containing cavity, selecting a molding material for forming the fluid delivery device; Molding a fluid delivery device comprising a long slider and a long fluid containing cavity; a clearance between the slider and the cavity, a first clearance threshold having a first driving force; Forming a seal as characterized by a clearance second threshold value having a second driving force less than one driving force by only molding the cavity and the slider; how to.

25. A fluid mechanical device selectively operable as a motor, pump, or valve for controlling fluid flow conditions and in response to fluid flow conditions, the fluid mechanical device being formed about a longitudinal axis and about the longitudinal axis. A non-machined body having an elongate fluid chamber having an inner wall surface with an inner surface; A long, non-machined, movable slider abutting against the inner wall surface so as to be reversibly movable along a longitudinal axis; The outer surface of the slider has a self-sealing condition capable of maintaining an infinitely leak-free state with respect to a fluid pressure difference greater than about 1 atm at both ends of the slider separated from each other. A device characterized by being in contact with each other.

26. 26. The device according to claim 25, wherein the material forming the body and the material forming the slider have substantially the same coefficient of thermal expansion.

27. 27. The device according to claim 26, wherein said body and said slider are formed from the same material.

28. 28. The device according to claim 27, wherein said material is a moldable plastic material.

29. A fluid mechanical device that can be selectively operated as a motor, a pump, or a valve for controlling a fluid flow condition and according to a fluid flow condition, having a longitudinal axis, and A molded body, at least partially formed by an elongated cylindrical wall having a first radius of curvature formed about the longitudinal axis as a center line; and a very small body in the chamber. A cylindrical outer wall having a radius of curvature slightly smaller than the first radius of curvature, and a seal contact effective against the wall of the body. A movable cylindrical slider made of an elongated molded product, wherein the movable cylindrical slider is configured to be in contact with and reversibly move in the chamber along the axis of the chamber. The wall surface of the body and the wall surface of the slider maintain an infinite leak-free state with respect to a fluid pressure difference greater than about 1 atm applied to both ends of the slider separated from each other. Devices that are in contact with each other with self-sealing conditions that can be achieved.

30. 30. The device of claim 29, wherein the difference between the two radii of curvature is no more than about 0.0003 inches.

31. 30. The device of claim 29, wherein the difference between the two radii of curvature is in a range from about 0.0001 inches to about 0.0003 inches.

32. A fluid mechanical device that is selectively operable as a motor, pump or valve for controlling fluid flow conditions and in accordance with fluid flow conditions; and a body formed of a long molded product; , Each having an inner wall surface and a longitudinal axis and being spaced apart from each other in an axially aligned state, and being disposed near both ends of the body, generally Two cylindrical chambers having a cylindrical shape; slidably disposed in each of the chamber structures with respect to the respective chamber structures, and slidably contacting the inner wall surface of each of the associated chamber structures in a fluid-tight manner. A movable molded slider having a generally cylindrical outer wall surface, the movable slider comprising an elongated molded article, wherein each slider and its associated chamber structure are spaced apart from each other. In a self-sealing condition capable of maintaining an infinitely no leak state with respect to a fluid pressure difference greater than about 1 atm applied to both ends, the respective wall surfaces are in contact with each other. A slider; articulated to the slider such that the slider is located at an intermediate portion of the body and is reciprocable substantially as an integral member with the slider so as to provide fluid flow in each of the chamber structures. A long power transmission means connected to the sliders so as to be movable as the associated moving member and capable of transmitting power to the sliders. Device.

33. A fluid pump, comprising a body formed of an elongated molded product; disposed inside the body, each having a generally cylindrical inner wall surface and being axially aligned and spaced from one another. Two elongated, generally cylindrical chamber structures disposed near both ends of the body; and slidably disposed within each of the chamber structures relative to each of the chamber structures; A piston made of a molded product having an overall cylindrical outer wall capable of sliding contact with the inner wall surface of each of the chamber structures to be fluid-sealable. A piston for forming a sealing condition capable of maintaining an infinitely no leak state with respect to a fluid pressure difference greater than about 1 atm applied to both ends of the piston; The pistons are drivable with respect to the pistons so as to be reciprocally movable as an integral member together with the pistons so as to be able to deliver fluid in the chamber structures and to be able to deliver fluid in the chamber structures. An elongate driver coupled to the driver; and a power transmission operably coupled to the driver for driving the driver so as to cause reciprocal movement of the driver and thereby reciprocal movement of the piston at the same time. A fluid pump, comprising:

34. A fluid flow control valve, comprising: a valve body made of a molded product; a fluid flow control chamber structure formed inside the body; and communicating with the chamber structure; A fluid passage structure comprising a pair of ports, wherein: A valve spool made of an adjustably movable molded part which is selectively movable under the influence of an applied driving force so as to be variable in degree. The chamber structure is such that in a region excluding the port, a leak-free state with respect to a fluid pressure difference larger than about 1 atmosphere can be maintained indefinitely. With in matter, a fluid flow control valve, characterized in that it directly sealing contact with each other.

35. A fluid motor, comprising a molded motor body; a fluid delivery chamber structure formed within the body; a selected periodic effect of an applied fluid pressure substantially disposed within the chamber structure. A movable delivery structure made of a molded product, which is periodically movable in the chamber structure under the condition that the chamber structure and the movable delivery structure are
Movement that is relatively movable while in direct fluid seal contact with each other under continuous sealing conditions such that a leak-free state for a fluid pressure difference greater than about 1 atmosphere can be maintained indefinitely; A fluid motor, comprising: a delivery structure; and a power output drive coupler coupled to the mobile delivery structure so that drive output power can be transmitted to a selected external device.

36. A fluid mechanical device that is selectively operable as a motor, pump, or valve for controlling fluid flow conditions and in response to fluid flow conditions, particularly a longitudinal axis and extending about the longitudinal axis. A body comprising a molded article having a long fluid chamber having a long inner wall surface existing therein; and having an outer wall surface arranged in a reversibly movable state with very little clearance in the chamber. And a movable slider made of a long molded product, which is in contact with the inner wall surface around the axis so as to be reversibly movable along the axial direction in the chamber. The chamber and the slider are operable under an operating environment in which a fluid pressure difference within a predetermined range exists between both ends of the slider. Where there is no external force to pressurize or depressurize the fluid in the chamber, let A be the effective operating surface area of the slider with respect to the delivery fluid of the slider. Assuming that L is the moving distance of the slider with respect to the chamber at the time of delivery, substantial positive or negative fluid inflow and outflow of the volume (A × L) is performed. A device, characterized in that:

37. A fluid mechanical device for providing various fluid flow conditions in a motor, a pump, a valve, or the like, which is formed from a selected moldable material and has a longitudinal axis and an inner wall surface. Wherein the inner wall surface has a curve around the axis when viewed from a direction perpendicular to a plane intersecting both the axis and the inner wall surface. Wherein the intersection with respect to the axis is substantially orthogonal, and the inner wall surfaces cooperate with other surfaces having similar surface characteristics. Active face-to-face local direct contact, such that it has a surface quality as a molded article with a selected predetermined local flatness to provide a selected desired fluid sealing performance. With body; same as above body A long slider formed from a moldable material, comprising a longitudinal axis and a long outer wall surface, wherein the outer wall surface is provided on both the longitudinal axis of the slider and the outer wall surface. Characterized by curvilinearity about said axis when viewed from an orthogonal direction to the intersecting plane, wherein the intersection of said slider with said longitudinal axis is substantially Is a cross-over, wherein the outer wall has a surface quality as a molded article substantially adapted to the surface characteristics of the inner wall of the chamber; and a slider. The slider is slidably disposed within the chamber, wherein the inner surface and the outer surface consequently are mutually cooperative face-to-face local direct contact with each other; This allows the desired fluid seal to be selected The fluid seal performance is realized by a fluid leakage between both wall surfaces even under the condition that a fluid pressure difference of up to about 1 atm appears between both ends of the slider in the chamber. A device characterized in that it is sufficient to prevent occurrence.

38. A fluid mechanical device operable selectively for and / or in response to fluid flow conditions in a variety of selected fluid delivery applications, the fluid mechanical device comprising: A body comprising a fluid chamber formed and having a fluid impermeable surface structure and at least partially defined by the surface structure; and a chamber formed from the same moldable material as the body. A relative moving member having a fluid-impermeable surface structure that can move relative to the surface structure in a fluid-seal manner so as to be capable of delivering a fluid while adhering to the surface structure. The fluid delivery movement is characterized by a movement line in which a fluid seal-like surface opposition between the two surface structures is present, the line being present in the chamber. Form a fluid seal movement boundary for the fluid that
Providing a positive or negative fluid flow in or out of the chamber depending on the direction of movement;
A device characterized in that such a sealing situation along the line is capable of maintaining an infinite leak-free characteristic with respect to a fluid pressure difference exceeding about 1 atm across the line. .

39. 39. The device of claim 38, wherein said lines are endless.

40. 39. The device according to claim 38, wherein the movement is a translation movement.

41. 39. The device according to claim 38, wherein the movement is a slide movement.

42. 39. The device according to claim 38, wherein the movement is a rolling movement.

43. A fluid delivery device, comprising a molded body defining a cavity for containing a fluid and having an outlet port for allowing communication between the cavity and a desired external location; And a fluid seal / fluid delivery structure made of a molded product, which is provided so as to be relatively movable in the cavity.
The device is operable to prevent fluid outflow from the cavity through the outlet port and to operate to allow fluid outflow from the cavity through the outlet port. A device characterized in that it is enabled.

44. 44. The device of claim 43, further comprising a drive structure for causing said relative movement.

45. A fluid-delivery device, comprising a molded body defining a cavity for containing a fluid and having an outlet port for enabling communication between said cavity and a desired external location; A fluid seal / fluid delivery structure composed of a molded product movably housed in the cavity between the first position and the second position. An act of preventing fluid outflow from the cavity through the outlet port in a first position, and an act of fluid outflow from the cavity through the outlet port in the second position.
Wherein the device is selectively enabled.

[Brief description of the drawings]

FIG. 1A is a partial cross-sectional view showing a first example of a conventional pump, and FIG.
FIG. 1B is a diagram schematically showing a delivery amount obtained in the conventional pump configuration shown in FIG. 1A, and FIG. 1C is a partial cross-sectional view showing a second example of the conventional pump.

FIG. 2A is a partial cross-sectional view showing an embodiment of a pump according to the present invention, and FIG. 2B is a diagram schematically showing a delivery amount obtained in the pump shown in FIG. 2A.

FIG. 3 is a partial sectional view showing a first embodiment of the structure of the present invention.

FIG. 4 is a partial cross-sectional view of a second embodiment of the structure of the present invention, illustrating certain types of relative movement, fluid sealing, and fluid delivery movement.

FIG. 5 is a partial cross-sectional view of a third embodiment of the structure of the present invention, illustrating other types of relative movement, fluid sealing, and fluid delivery movement.

FIG. 6 is a diagram schematically showing a feature of the present invention, wherein the feature is
It can be added to any of the embodiments of the present invention.

FIG. 7 schematically illustrates further features of the present invention, which may be added to any embodiment of the present invention.

FIG. 8 is a perspective view showing a fourth embodiment of the present invention.

FIG. 9 is an exploded perspective view of the fourth embodiment shown in FIG.

FIG. 10 is a plan view of the fourth embodiment shown in FIG.

FIG. 11 is a side view of the fourth embodiment shown in FIG.

FIG. 12 is a perspective view showing an example of a reciprocating member according to the fourth embodiment shown in FIG.

FIG. 13 is a cross-sectional view taken along line 13-13 of FIG. 8 and shows the relative arrangement between the members at each time point over a 360 ° rotation of the crank / cam member.

FIG. 14 is a cross-sectional view taken along line 13-13 in FIG. 8, showing the relative arrangement between the members at each point in time over 360 ° rotation of the crank / cam member.

FIG. 15 is a cross-sectional view taken along line 13-13 in FIG. 8, showing the relative arrangement between the members at each point in time of 360 ° rotation of the crank / cam member.

FIG. 16 is a cross-sectional view taken along line 13-13 of FIG. 8, showing the relative arrangement between the members at each time point over a 360 ° rotation of the crank / cam member.

FIG. 17 is a sectional view taken along line 17-17 in FIG. 8;

FIG. 18 is a perspective view of the fourth embodiment shown in FIG. 8, with the micropump cut away and showing the movement of the piston in the cylinder and the displacement of the piston in the cylinder. .

FIG. 19 is a perspective view of the fourth embodiment shown in FIG. 8, in which the micropump is cut away, and shows how the piston moves in the cylinder and displacement of the piston in the cylinder. .

FIG. 20 is an exploded perspective view showing a second configuration example of the fourth embodiment in FIG.

21 is a cross-sectional view taken along line 21-21 in FIG. 20, showing a cam member.

FIG. 22 is a sectional view showing a modification of the cam member shown in FIG.

FIG. 23 is a cross-sectional view taken along line 23-23 of FIG. 8 and shows the relative arrangement between the members at each point in time of 360 ° rotation of the crank / cam member.

FIG. 24 is a cross-sectional view taken along line 23-23 in FIG. 8 and shows the relative arrangement between the members at each time point over a 360 ° rotation of the crank / cam member.

FIG. 25 is a cross-sectional view taken along line 23-23 in FIG. 8 and shows the relative arrangement between the members at each time point over a 360 ° rotation of the crank / cam member.

26 is a cross-sectional view taken along the line 23-23 in FIG. 8, showing the relative arrangement between the members at each time point over a 360 ° rotation of the crank / cam member.

FIG. 27 is a perspective view showing a second configuration example of the reciprocating member in the fourth embodiment shown in FIG.

FIG. 28 is a plan view showing a fifth embodiment of the present invention.

FIG. 29 is a plan view showing a sixth embodiment of the present invention.

FIG. 30 is a plan view showing a seventh embodiment of the present invention.

[Explanation of symbols]

10 Volume delivery maximizing device, fluid mechanical device, fluid pump, fluid flow control valve, fluid motor 12 Slider, piston, valve spool, moving delivery structure, fluid seal /
Fluid delivery structure, fluid delivery device 12a Outer wall surface 13a Slider, sub piston 13b Slider, sub piston 14 Cavity, fluid chamber, fluid delivery chamber structure 14a Chamber structure 14b Chamber structure 16 Body, valve body, motor body 16a Inner wall surface 18 Port structure Fluid passage structure 18a Outlet port 18b Inlet port 19 Power transmission means 20 Driver, drive coupler for power output 110 Fluid mechanical device 112 Relative moving member 114 Chamber 210 Fluid mechanical device 212 Relative moving member 214 Chamber 310 Micro pump 312 Slider structure 314 Chamber 315 Cylinder 316 Body 320 Driver 410 Micropump 510 Micropump 610 Micropump

──────────────────────────────────────────────────続 き Continuation of front page (81) Designated country EP (AT, BE, CH, CY, DE, DK, ES, FI, FR, GB, GR, IE, IT, LU, MC, NL, PT, SE ), OA (BF, BJ, CF, CG, CI, CM, GA, GN, GW, ML, MR, NE, SN, TD, TG), AP (GH, GM, KE, LS, MW, SD, SZ, UG, ZW), EA (AM, AZ, BY, KG, KZ, MD, RU, TJ, TM), AL, AM, AT, AU, AZ, BA, BB, BG, BR, BY, CA, CH, CN, CU, CZ, DE, DK, EE, ES, FI, GB, GE, GH, GM, HR, HU, ID, IL, IS, JP, KE, KG, KP , KR, KZ, LC, LK, LR, LS, LT, LU, LV, MD, MG, MK, MN, MW, MX, NO, NZ, PL, PT, RO, RU, SD, SE, SG, SI, SK, SL, TJ, TM, TR, TT, UA, UG, UZ, VN, YU, ZW

Claims (17)

[Claims] 1. A volume delivery maximizing device, comprising a molded body having an interior surface defining an elongated fluid containing cavity; and an exterior surface disposed adjacent the interior body surface. And a slider made of a molded product, which can be moved bidirectionally in the cavity; and a boundary surface seal exists between the body and the slider. The face seal has a clearance first threshold having a first driving force and a clearance second threshold having a second driving force with respect to a clearance between the inner surface of the body and the outer surface. Each driving force causes relative movement under a set of operating conditions, and the clearance second threshold value is smaller than the clearance first threshold value. Device. 2. A volume delivery maximizing device, comprising a molded body having an elongated fluid-containing cavity formed therein; and a molded body movable bidirectionally within said cavity. And a slider, wherein an alignment exists between the slider and the cavity, and the alignment has a first driving force with respect to a clearance between the slider and the cavity. A device characterized by having a first clearance threshold and a second clearance threshold having a second drive force less than the first drive force. 3. A method for optimizing fluid delivery in a molded fluid delivery device configured to deliver fluid by movement of a slider within a fluid containing cavity, the method comprising forming a fluid delivery device. Selecting a material; molding a fluid delivery device comprising a slider and a fluid containing cavity; axially aligning the slider within the cavity; A method characterized by a clearance first threshold value having one driving force and a clearance second threshold value having a second driving force smaller than the first driving force. . 4. A method for optimizing fluid delivery in a molded fluid delivery device configured to deliver fluid by movement of a slider within a fluid receiving cavity, the method comprising forming a fluid delivery device. Selecting a material; molding a fluid delivery device comprising an elongate slider and an elongate fluid containing cavity that is substantially leak free for substantially infinite time with respect to fluid pressure conditions within the cavity. A method characterized by: 5. The method of claim 4, wherein the molding step is performed such that the fluid pressure condition of 15 psig is substantially leak-free for substantially infinite time. A method comprising: 6. The method of claim 4, wherein the molding step is substantially leak free for substantially infinite time for a fluid pressure condition of 125 psig,
A method characterized by performing molding. 7. The method of claim 5, wherein said molding step comprises molding a cylindrical cavity having a diameter of at most about 1 inch. 8. The method of claim 6, wherein said molding step comprises molding a cylindrical cavity having a diameter of at most about 1 inch. 9. A method for optimizing fluid delivery in a molded fluid delivery device configured to deliver fluid by movement of a slider within a fluid containing cavity, the method comprising forming a fluid delivery device. Selecting a material; molding a fluid delivery device having an elongated slider and an elongated fluid containing cavity; a first threshold having a first driving force with respect to a clearance between the slider and the cavity. Only by performing an alignment between the cavity and the slider as characterized by a clearance and a second threshold clearance having a second driving force less than the first driving force. Forming a seal between the slider and the cavity. 10. A method for optimizing fluid delivery in a molded fluid delivery device configured to deliver fluid by movement of a slider within a fluid containing cavity, the method comprising forming a fluid delivery device. Selecting a material; molding a fluid delivery device having an elongated slider and an elongated fluid containing cavity; a first threshold having a first driving force with respect to a clearance between the slider and the cavity. Forming a seal as characterized by a value and a second clearance threshold having a second driving force less than the first driving force by only molding the cavity and the slider. A method characterized by: 11. For controlling fluid flow conditions and according to fluid flow conditions,
A fluid mechanical device selectively operable as a motor, pump, or valve, comprising a long fluid chamber having a longitudinal axis and an inner wall surface formed about the longitudinal axis. A machined body having an outer surface disposed in a reversible manner within the chamber with negligible clearance, and reversibly movable along the longitudinal axis within the chamber. A long, non-machined, movable slider that is in contact with an inner wall surface; and wherein the inner wall surface and the slider outer surface are at opposite ends of the slider. Devices that are in contact with each other under self-sealing conditions such that a leak-free state for a fluid pressure difference greater than about one atmosphere can be maintained indefinitely. 12. The device according to claim 11, wherein the material forming the body and the material forming the slider have substantially the same coefficient of thermal expansion. 13. The device according to claim 12, wherein said body and said slider are formed of the same material. 14. The device according to claim 13, wherein said material is a moldable plastic material. 15. For control of fluid flow conditions and according to fluid flow conditions,
A hydromechanical device selectively operable as a motor, pump, or valve, having a longitudinal axis, and a first curvature formed about the longitudinal axis about the longitudinal axis. A molded body, formed at least in part by a long cylindrical wall having a radius; disposed in said chamber in a reversibly movable manner with negligible clearance; A cylindrical outer wall having a radius of curvature slightly smaller than the first radius of curvature, providing an effective seal abutment against the wall of the body, within the chamber along the axis of the chamber; A movable cylindrical slider made of a long molded product, which is reversibly movable; and a front surface of the wall surface of the body and the slider. The wall faces are in contact with each other under self-sealing conditions such that an infinitely leak-free state can be maintained for a fluid pressure difference greater than about 1 atm at both ends of the slider separated from each other. Device. 16. The device of claim 15, wherein the difference between the two radii of curvature is no more than about 0.0003 inches. 17. The device of claim 15, wherein the difference between the two radii of curvature is in a range from about 0.0001 inches to about 0.0003 inches.