JPS61290962A - Fail-safe type mechanical drive apparatus for syringe - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION This invention relates generally to mechanical drives, and more particularly to fail-safe mechanical drives particularly suited for driving syringes or other fluid injection St over long periods of time. The present invention relates to a spring drive device.

Known dispensers for injecting small doses of medicinal fluids over long periods of time are bulky and therefore not easily portable or are powered by electric motors. Motor-operated infusion devices require a power source such as f-line power and a battery; wire power restrains the patient during the procedure; Because of the limited shelf life of battery operated devices, it is necessary for the patient to maintain a relatively fresh supply of batteries. Another problem with generously actuated dispenser devices is that they require sophisticated and expensive insulation to prevent even minute amounts of electrical energy from entering the patient's vascular system. Today, one example is on the order of microamperes.

It is known that even small amounts of electrical energy can affect the heart of an unfortunate patient.

Thus, in addition to inadvertent operation even for short periods of time, battery-powered injection devices.

Particularly if the equipment becomes wet, it can be dangerous to the patient.

Some of the above problems associated with electrically actuated dispenser devices are overcome by using mechanical pumps. Generally, a mechanical drive, in combination with a syringe, provides an infusion pump driven by a clock mechanism. This clock a structure is essentially conventional in that the plate-to-plate transmission is torqued by a wound spring. The rotational speed of this device, and therefore the speed of fluid injection, is
It is controlled by a conventional flywheel and detent system.

In addition to overcoming the disadvantages of electrical devices, mechanical drives exhibit all the known economic advantages of timed-release injection devices. Like this, it takes mechanical? t2
At t, patient infusions can be performed continuously, thereby reducing the required labor of hospital staff f! The amount of A is reduced. In addition, automatic infusion devices substantially eliminate the possibility of human-induced accidents, such as those caused when a patient attendant ignores or otherwise fails to follow a prescribed infusion schedule. reduced. In addition, such mechanical devices allow iJ
! U-shaped injections, which are more closely matched to the characteristics of the fluid production system within the patient's body, have the advantages of medicine 1 of such injections.

For example, there is a distance of 1500 mm between the drive spring and the stopper:
It is characteristic of conventional mechanical clockwork syringe section th devices that a high gear train drive ratio, on the order of 1, is required. In terms of standards, injection! 1t22 is driven almost directly by the spring. To achieve the required high transmission ratio by plate-to-plate clockwork,
Generally, when used in a 9-clock watch that requires a four-stage spur gear system, the 4RI drives the 1:01 minute and second hands at an appropriate one-wheel ratio. However, 1
A problem with such conventional clock technology is that, when used as a clock, any failure of the wheel structure has relatively minor consequences. At worst, one clock will point to the wrong time. However, when a clock drive is used to pump fluid into a patient's veins, this is not the case; failure of the clock under these circumstances could be catastrophic and cause total damage. Injected with spring energy! j
t21. For example, by rapid release into a syringe.

This can result in the patient receiving a large and potentially fatal dose of infusion fluid.

In addition, traditional clock mechanisms require a substantially greater load or stress to drive the syringe than simply rotating the clock hands, so the injection! When used in Aat, it is much more prone to failure.

Generally mechanical and rock driven! ! In conventional plate-to-plate gear drives of the type installed in the Shear stress is applied. Therefore, each gear tooth is subjected to a substantial portion, and possibly the entirety, to a driving load, resulting in a relatively high risk of breakage, as mentioned earlier. In terms of equipment, Kakeru! ! Since the loads are larger, the risk of failure is greater, and failure of the gear train in a plate-to-plate gear transmission will almost always be catastrophic.For example, if the gear train If a failure occurs at some point intermediate to the output shaft, the mechanism shuts down and the patient is no longer given life-sustaining infusions. On the other hand, if the gear train is damaged, the output shaft and the escape stop! ! If this occurs at some point between the device and the device, then a catastrophically rapid injection can occur, resulting in a potentially fatal overload of injection fluid. Conventional clockwork devices therefore do not seem reliable enough when a person's life is at stake.

There are various causes of damage to clockwork gear drives. For example, in a clockwork 5 transmitted to the driven pinion.

However, such pinions are typically manufactured by known guicasting or injection molding techniques.

In such manufacturing systems, it is possible for defects to exist within the mold or die,2 and these defects can cause pinion-
This appears as a vulnerability. Of course, such weakness may be caused by the material or processing present on the only pinion; such weakness may be caused by contamination during casting or injection molding. Such defects and weaknesses are generally not visible to the naked eye and can only be detected with expensive quality control equipment such as x-ray imaging or ultrasound equipment.

It is therefore an object of the present invention to provide a pharmaceutical fluid injection device that is cheap and simple to manufacture.

Another object of the invention is to make it small, lightweight, and portable.
Another object of the present invention is to provide a drive device for a syringe that can be easily attached to a patient.

The object of the invention is also to. It is an object of the present invention to provide a fluid dispensing device that is reliable over long periods of operation.

Yet another object of [Book 511J] is to provide a fail-safe arrangement δ for a fluid injection device that prevents uncontrolled operation of the fluid dispensing function.

Yet another object of the present invention is to provide a drive system for a pharmaceutical fluid dispensing device that does not require an external power source.

Yet another object of the present invention is to provide a pharmaceutical fluid infusion device that does not require a battery to perform a corporal injection.

Yet another object of the present invention is to provide a mechanical drive device capable of providing driving force with controlled excursion speed.

Accordingly, it is an object of the present invention to provide a drive device for a syringe that utilizes only mechanically stored energy to perform the drive action.

Another object of the invention is to provide a speed governor with high reliability for a mechanical drive.

Still another object of the present invention is to provide an operational indication for a fluid injection device into a lumbar tube, and a still further object of the invention is to provide an operating indication for a fluid injection device into a lumbar tube. Practically i! The object of the present invention is to provide a continuous disturbance transmission system.

Another object of the invention is to provide a drive device with substantially increased torque transmission capability between the drive shaft and the output shaft.

wood:%! A further purpose of llJ'l is that it is provided between the output shaft and the speed regulator of the output shaft, so that when tooth slippage occurs in the 7A adjustment device, the 7A adjustment device is out of control. It is an object of the present invention to provide a fail-safe device that prevents rotation.

Yet another object of the present invention is to provide a fail-safe arrangement that prevents uncontrolled rotation of the detent gear wheel.

These and other objects are achieved by the present invention which provides a drive tJJ device particularly suited for driving a medicinal fluid injection device by providing rapid input & IW output excursions. Preferably, the drive device is provided with rotary drive means for imparting a drive torque to the first shaft; on the preferred χ flow side, the rotary drive means is provided with a winding for storing energy used to perform the drive action. Equipped with a spring member.

A plurality of drive gears are coaxially disposed on the first shaft: the drive gears have a fixed rotational relationship with respect to each other. The second shaft, the output shaft, is provided with first and second pinion members that mesh with the first and second drive gears, respectively. The first and second pinion members are connected to the first and second drive shafts. h* have a fixed rotational relationship with respect to each other corresponding to the rotational relationship between the cars.According to the invention, a speed control device is provided for controlling the operating speed of the drive. A control gear is fixed on the output shaft and in conjunction with the speed controller limits its excursion rate in response to the speed M controller.

In one uninvented embodiment, the first and second drive gears are coaxially fixed on the first shaft and are rotationally offset with respect to each other, thereby causing each of the drive gears to The weapons on the gears are axially misaligned.

Only two such coaxial driving gears are provided, and it is a two-wheel drive gear! In embodiments of the invention in which the gears (i) have an equal number of teeth, both drive gears are arranged so that the first gear has a rotational relationship between them that corresponds to the maximum axial misalignment between the gears. fixed on the shaft.

Therefore, in such embodiments, one drive tooth 1! T's teeth are the other's drive! It is substantially axially aligned with the gap between the southeast peaks of the 0 south car.

According to the invention, the speed control device is provided with first and second anti-release ratchet wheels that are coaxially fixed to the ratchet wheel axis.

And, like known aspiration locking devices, it rotates at a faster speed than the output shaft. A flywheel is axially fixed on the flywheel and is rotatably oscillated at a substantially constant, predetermined frequency. In addition, the first and second lever members with pins are connected to the lever shaft, E, such that the first and second lever members with the pins are articulated between the first and second detent ratchet wheels, respectively, and to the momentum shaft.
Each of the two lever members disposed in the lever member is of a generally known type having a lever portion extending orthogonally to the two lever members. However, this rotary coupling device rotationally couples the control gear to drive the ratchet wheel shaft.

In this way, the rotational speed of the output shaft is controlled in response to the vibration frequency of the flywheel. In some embodiments, several flywheels may be mounted coaxially on the flywheel; however, the flywheels are all fixed to the flywheel for rotation together. il and the second lever member are similarly fixed and rotate together with the lever shaft. For this reason, a multi-purpose locking device is provided, so that even if the - lever member is damaged due to the bottle coming off the lever part, the second lever member will not stop on the speed billing machine. can be fulfilled. In addition, the undamaged lever member drives the damaged lever member to prevent the damaged lever from collapsing against its associated detent ratchet wheel. Therefore, this combined device is designed to prevent the device from jamming or stalling if one bottle or lever is damaged or otherwise broken, while still allowing the A. It fulfills the safety function of -tun, which essentially eliminates the risk of running.

The speed control is equipped with a frequency control device that controls a predetermined vibration frequency of the Momoichi. In one embodiment, the vibration frequency is controlled in part by a helical spring fixed substantially coaxially with the flywheel;
A mechanism is further provided for adjusting the tension within the helical spring. This mechanism, and thus the tension in the helical spring, provides a
1 (the vibration frequency and, as a result, the excursion speed of the output shaft) can be adjusted. By using the aforementioned dual drive gearing in conjunction with the individual pinion members on the output shaft, the reliability of the entire device is increased. First of all, the effective surface width or gear thickness is: 51 and the second drive f.
The fact that it corresponds to the sum of the convergence of each side of the HFA vehicle improves the torque transmission capability of the vehicle. In addition, each such drive gear is associated with a respective one of the associated concentric pinions, and according to the invention both pinions are rotationally offset with respect to each other so that they are engaged at two times. The probability that the pinion teeth will become weak and break is substantially reduced. For cast or injection molded types of pinion members.

The problem is that inclusions or air bubbles may form during the casting process, or there may be defects in the mold that severely weaken the south of one or more of the pinions. Due to the rotational deviation of the first and second pinions with respect to each other, even if a casting defect loses its effect on each pinion, a casting defect will cause each pinion to fail simultaneously, resulting in loss of power to the output shaft. The probability that transmission is completely lost is minimized. The aforementioned rotational deviations of the pinion, which may also apply to the drive gear, are related to the rotational deviation with respect to the particular orientation in which the pinion or gear was manufactured. Thus, for example, a defect that is common to each pinion may be caused by a defect between the first and second pinions, although in a particular embodiment the pinion grooves of the first and second pinions may be axially aligned. They won't line up.

Said rotational deviations between the first and second drive gears and the first and second pinions, respectively, may result in catastrophic failure resulting from defects that may become commonplace for a group of such pinions. A bad outcome is avoided. However, according to the invention, other types of rotational deviations may be provided with respect to the axial alignment of the teeth of the teeth F or of the pinion teeth. Such axial misalignment of the flesh, as mentioned above, results in an increase in the effective number of teeth, so that the subject stacked transmission has an increased effective radius or In addition to increasing the effective 1M and N thickness, the number of surfaces also increases effectively. In short, the diameter pitch of the effective gear increases, resulting in an increase in torque transmission force.

;■1 The transmission device was proposed to improve the reliability of power transmission to the output shaft. However, the invention further provides an arrangement in which the possibility of uncontrolled rotation of the output shaft is essentially eliminated.According to this aspect of the invention, a gear and a pinion associated with this gear are are arranged so as to have a pitch relationship corresponding to an integer ratio.

In situations of the invention where the gear shaft drives the pinion shaft, the wheel on the gear shaft has at least one tooth that is accommodated by a recess in the wheel on the pinion shaft. The pinion wheel has a number of depressions corresponding to the lowest denominator after the integer ratio is mathematically reduced. It extends radially outward a distance that exceeds the gap between the gear and pinion wheels. For this reason.

If a deviation occurs due to breakage or loss within the stack or pinion that actually transmits torque, a one-turn deviation will occur, and the south of the gear wheel will be located within the pinion wheel. It becomes rotationally out of sync with the recess, which forces the teeth against the outer surface of the pinion wheel. Preferably, the pinion has a large number of depressions distributed around it, the number of which is not more than one third of the kl number of the driven pinion associated with the pinion. Therefore, if up to three pinions south are damaged in the driven pinion, the south of the l1ii car wheel will no longer drive the pinion wheel, due to the further shape of the 6MI wheel and the depression in the pinion wheel. The shape means that engagement is avoided due to an angular distance deviation corresponding to only one pinion tooth of the associated driven pinion;
Preferably, the shape is such that indentation occurs; however, in some embodiments, even if tk1vJ
The shape of the recess of the pinion is such that even if the teeth of the L wheel deviate angularly by an angular distance corresponding to the fI angle of the stacked drive gear, the recess of the pinion accommodates the south of the gear wheel. It may be desirable to specify

With this 4I construction, even if one and possibly two pinion or gear teeth break, the drive will continue to operate normally, but when three teeth break, it will not start. will be prevented.

The aforementioned structure also clogs a potentially catastrophic gear excursion on the W4 rectifier side of the IN1 wheel drive. There is also the advantage that the pinion wheel does not have the shape of a pinion in the conventional sense, so that the risks associated with pinion tooth defects are eliminated. This structure is suitable for each gear-pinion engagement and the regulator side of the mechanical drive. The present invention therefore contemplates, within the scope of the present invention, a fail-safe device that prevents uncontrolled rotation of a locking ratchet wheel that is not associated with a pinion. In a preferred embodiment, the safety wheel is fixed on the axis of the anti-release ratchet wheel and rotates simultaneously with the ratchet wheel. The safety wheel is equipped with a centrifugal ejection mechanism that extends in the radial direction of the safety wheel in response to uncontrolled rotation or acceleration of the locking ratchet wheel. At least one stationary member is provided for engaging the radially extending centrifugal launch mechanism. Such engagement prevents rotation of the safety wheel and thus the relief ratchet wheel.

In one embodiment of the invention, the centrifugal ejector mechanism may include a spring loaded ejector member J11 held in a radially inward position by an inwardly biased spring. However, the centrifugal force created by the uncontrolled rotation is sufficient to overcome the radially inwardly directed spring force, thus allowing the centrifugal ejector member to extend radially outwardly. The stationary member connected to the radially extending centrifugal force a bridge is.

It may be a strut or wedge-shaped brake fixed to the chassis or housing member of the wheel stop, so that the last link in the drive train, i.e. Protected from excessively rapid rotation.

In another embodiment, the locking device is constructed to emit a rather loud clicking sound as an indication of its operability. In addition, the flywheel is located near the opening or window of the unit's case, making it easy to operate the unit!
S can be visually inspected. The present invention can be easily understood from the following detailed description with reference to the accompanying drawings.

FIG. 1 is a simplified, partially diagrammatic representation of a mechanical drive type 1 with a drive stack 20 supplying the mechanical energy to perform the drive action, as will be explained below. The drive stack 20 is mechanically connected to the output stack 40, and the output shaft 42 that the output stack 40 has
is connected to a mechanism (not shown) to be driven.

In this embodiment of the invention, the output stack 40 is mechanically associated with a speed limit g4st 215, which acts to limit the rotational speed of the output shaft 42. In this particular illustrated embodiment, speed control! ItW 150 is formed from first and second deceleration-vehicle stacks 60 and 70, respectively. The second reduction gear stack 70 drives a ratchet wheel stack 100, which is coupled to the flywheel stack 120 via a lever stack 140. 2 is a side view of an embodiment of the invention corresponding to the embodiment shown in FIG. 1; FIG. FIG. 2 shows a pair of drive gears 23 and 2.
A drive stack 20 consisting of a drive shaft 21 having a drive shaft 21 coaxially fixed to the drive stack 20 is shown in a simplified manner. In addition, drive shaft 2
1, the main spring assembly 25 is connected to a ratchet device (
(not shown), and the main spring assembly is fixed coaxially through the winding key 2 by this ratchet device.
It can be tightened by rotating it in step 6. It is well known that the main spring assembly 25 may be coupled to a structural member (not shown) to allow energy to be stored in the main spring assembly as is known.

Drive gears 23 and 24 are secured to the drive shaft by a collar 27, which secures the drive gears by any number of known means. Such fixings may be force fit, talimp, groove and key, spot welding, vc
In the context of the present invention, where high reliability is required for an actuation that may be performed by rt or the like, it is important that the drive gear is securely fixed to the drive shaft.

Mechanical energy stored in main spring assembly 25 is transmitted to output shaft 42 by drive gears 23 and 24 meshingly engaging pinions 43 and 44, respectively, while pinions 43 and 44 are The output shaft 42 is fixed on the output shaft 42 by any means. In this particular embodiment illustrated, the output gear 45 is the utilization mechanism (
WA! ! It is fixed on the output shaft 42 so that it can be rotated. As mentioned above, such a utilization mechanism may include a syringe that is desired to be driven for an extended period of time. FIG. 3 is a fragmentary plan view of drive gears 23 and 24. As pointed out before,
The drive gears are arranged coaxially with respect to each other,
And in addition to this, the south of each float may be axially aligned; however, according to the present invention, precious stones 23 and 24 may be rotationally offset with respect to each other in several ways. First, if you apply a rough rotational deviation, the weak spots on the gear teeth that result from manufacturing defects will not be placed in alignment with each other, but will be in different locations during one rotation cycle. For example, it is often assumed that the drive gears 23 and 24 are identical to each other, and are actually manufactured by the same mold or die, but that the corresponding vehicle is fixed and Suppose that both gears are rotated such that their corresponding Wll teeth are offset from each other and away from each other, in FIG. 3, the drive gear 23 has a specially defined gear tooth 23°; The drive gear 24 then has a similar corresponding float @24'. During manufacturing, specific m23' and 24' correspond to the same die in the mold or die used in manufacturing. Move the drive fa car onto the drive shaft zl! In the present invention, both drive gears are offset so that the south 11tJii 23° and 24° are not aligned when loading A. Such mutually corresponding gear teeth are preferably offset by an arc corresponding to a distance of about three gear teeth in length; of course, gear teeth 23' and 2
It would be advantageous if 4' were approximately diametrically opposed to each other.

The second component of rotational excursion illustrated in FIG. 3 corresponds to the teeth of one drive gear being axially aligned with the tooth gaps of the other gear. As previously noted, such deviation manifests itself as a doubling of the effective number of gear teeth, resulting in an increase in the torque transmission peak force of the drive train. Thus, the combination of stacked drive gears substantially increases torque capability and, as a result, reliability.
This results in a net doubling of the face width of the gear and a second rotational excursion that doubles the effective number of teeth in the gear.

Referring to FIG. 2, drive gears 23 and 24 are in meshing engagement with respective pinions 43 and 44. In one particularly advantageous embodiment of the invention, pinions 43 and 44 are preferably With respect to the drive-wheel shown in FIG. 3, it is intended to be rotationally offset in both senses previously discussed. This causes pinions 43 and 44 to be roughly rotationally offset, with the result that -
are axially aligned with the spacing between the shafts of the other pinion, but the corresponding shafts are substantially axially misaligned. In this way, a meshing connection between the pinion and the drive gear is achieved reliably.

In addition to the pinions 43 and 44, the output caster 40 includes:
A pair of gear plates 46 and 47 are provided coaxially fixed to the output shaft 42. In one embodiment, gear plates 46 and 47 correspond to teeth +p similar to drive gears 23 and 24 described above. In such an embodiment, the gear plates would be provided with respective rotational excursions as described in connection with FIG.
It is associated with pinions 61 and 62 coaxially fixed on the shaft 63 of the float stack 60. Pinions 61 and 62 will be rotationally offset in the manner described above with respect to output stack pinions 43 and 44.

Another embodiment of the invention, which is illustrated in FIG. 4, has the vehicle plates 46 and 47 shown in a simplified, exploded view. *The wheel plate 46 meshes with the pinion 61 with the ratio of the gear teeth to the pinion being N:n. Fourth
In the particular embodiment shown, the vehicle plate 47 and the IA
J! ! The pinion 62 is the lai car pre-plate 4
The pinion 61 is coaxially overlapped with the pinion 61, and has the same pitch as the pitch ratio between the plate 46 and the pinion 61. In this particularly illustrated embodiment, the ratio of the number of gear teeth N to the number of pinion teeth N is 5:1. Therefore, gear plate 47 is provided with five relatively large @47a to 47e, while pinion 62 is provided with a single recess 62a. The south 47a...47e of the gear plate is the pinion recess 62.
Because of its shape, there is only minimal contact between the south outer side of the gear plate and the inner surface of the pinion recess. car plate 46
and 47. Since the pinions 61 and 62 are fixed on their respective shafts, the gear plate and the pinion rotate synchronously, so that the gear plate 47 cannot drive the pinion 62 during normal operation. There is no,
Instead, this plate and pinion are gear plate 4
6 and the pinion 61, the wheel plate 46 drives the pinion 61. The first advantage presented in the subject matter 4IJk is that there is no drive ff friction since the housing of the gear plate heir within the pinion recess 62a can be essentially uncoordinated. The gear plate 47 and pinion 62 are each e8
Rotate in the direction indicated by the consecutive arrows. In FIG. 4, the teeth 47d of the welding wheel plate are about to be seated within the pinion recesses as they continue to rotate in the direction shown.

If one or more of the teeth on either gear plate 46 or pinion 61 were to fail, the looseness of the teeth would cause the axles 42 and 63 (not shown in this figure) to A rotational deviation will occur in between. The result is such a rotational deviation between the full plate 46 and the pinion 61.

The rjI wheel plate 47 and pinion 62 will be displaced in the same way. However, 11 of the gear plate
i47a***47e will not be synchronized with the rotation of pinion 62 so that it is accommodated within pinion recess 62a. 147a to 47e due to such asynchrony.
One of the teeth will be pressed against the outer surface 62b of the pinion 62. Such pressing is applied to the annular end sewing surface 48 of the gear plate 47 and the outer surface 6 of the pinion.
2b arises from the fact that the gap C is smaller than the radial length T of the teeth of each gear plate. In this embodiment, five teeth are shown, 47a to 47e, but in an uninvented implementation there may be only one such tooth. In this particular embodiment of the invention, the first The reduction gear stack 60 has vIs associated with the pinions 71 and 72 of the second speed gear stack 70, respectively.
IItf plates 64 and 65 are sunk. In addition, a pair of fJi4 wheel plates 74 and 75 are coaxially arranged within the second straight gear stack 70.

A pair of associated pinions 101 and 10 coaxially aligned with the anti-relief ratchet wheel stack 100.
It is engaged with 2.

According to the invention, first and second reduction gear stacks 60 and 70, respectively, of speed controller 50 are drive gears similar to gear plates 46 and 47, respectively, previously discussed in connection with FIG. It may also include a stacked combination of safety gearing and safety gearing, so that one
The safety features inherent in the stacked combination of Km wheel plates 46 and 47 are also reflected in the gear stacks 60 and 70, so that the stacked gear plates 74 and 75 of the second reduction gear stack 7 and The ri train up to the linkage between the pinions 101 and 1.02 of the release ratchet wheel stack 100 is provided with protection from uncontrolled rotation.

In this embodiment of the invention, the ability of the detent ratchet wheel stack to rotate uncontrollably is limited to the first and second ratchet wheels 105 and 106.
are each reduced by a compound relief detent device coaxially disposed on the ratchet wheel axis 107. Ratchet wheels 105 and 10B are preferably secured on ratchet wheel shaft 107 such that their respective ratchet teeth are axially aligned.

The rotational speed of ratchet wheels 105 and 106 is controlled by a pair of levers 141 and 142 fixed on a lever shaft 144 to form a lever stack 140. These levers vibrate according to the vibration frequency of the flywheel stack 120. In this embodiment, the flywheel stack 120 is provided with first and second flywheels 122 and 123, each fixed on a flyaxle 124. Cam 12, as known to 1K
5 and 126, levers 141 and 142 are oscillated to allow ratchet wheels 105 and 10B to provide controlled rotational locking. The link between the ratchet wheel and the lever includes a pin 14 fixed to the lever and extending substantially orthogonally therefrom.
It is given by 6. In a single lever and ratchet wheel detent system, if one or both bins are lost from the lever, the detent device will either become stuck or rotate uncontrollably. It is known to stow away.

) According to the K invention, since a plurality of relief stop devices are combined, if the relief stops become solidified or DI'R
This is essentially prevented since some such bottles will inevitably break if rotated too much.

Apart from the above, the IJI 1 is equipped with a centrifugal device 150 that prevents uncontrolled rotation of the locking ratchet wheel stack. The centrifugal mechanism 150 is preferably disposed on the ratchet wheel axis 107 and may include a co-rotating base member 151 and a stationary stop 152.

5 and 6 illustrate an exemplary mechanism that operates centrifugally to prevent uncontrolled rotation of the detent ratchet wheel stack. Fifth
The figure shows an embodiment of this mechanism in which the base member 151 is shown in diagrammatic form, either rotationally stationary or moving at normal operating speed. FIG. 6 illustrates this mechanism after it has been subjected to a significant centrifugal acceleration such that the centrifugal member 155 is radially displaced relative to the base member 151 and comes into engagement with the stop 152. The centrifugal member does not extend radially outwardly enough to engage the stop 152 at normal or slow operating speeds, as shown in FIG. 5, of course. In implementation, some other optional device for creating a centrifugal braking device may be utilized and may include a 9g member, such as a wire spring 157.

Two levers 141 and 142 are shown, even if only one flywheel is provided.

It should be understood that the flywheel star and ri will normally a10 In this embodiment, two hairspring devices 12β and 129 are provided to control the vibration speed of the flywheel stack simultaneously. It works properly. However, in some embodiments of the invention, only one such hairspring device is required. In light of this teaching, one of ordinary skill in the art will know how to shape a flywheel stack to vibrate at the proper frequency while using only one flywheel or one hairspring device. You will be able to do it.

Although the invention has been described in terms of particular embodiments and applications, a worker skilled in the art, in light of this teaching, would be aware that the invention would not exceed the scope of the claimed invention or: s9. Other embodiments may be created without departing from the spirit of the invention. Accordingly, it should be understood that the drawings and descriptions in this disclosure are presented to facilitate understanding of the invention and are not to be construed as limiting the scope of the invention.

[Brief explanation of drawings]

FIG. 1 is a partially schematic and simplified representation of an embodiment of the invention having an aligned gear train; FIG. 2 shows the embodiment shown in FIG. 1; , @only a partially diagrammatic side view; FIG. 3 is a fragmentary view of a stacked drive gear arrangement that can be advantageously used to carry out the invention; FIG. , a simplified partially exploded representation of the 7-Ale-Safe device that prevents accidental rotation of the meat train caused by defective pinions or gear teeth; FIG. FIG. 6 is a very concise illustration of the embodiment of the centrifugal safety device during rapid or uncontrolled rotation; . lO Red... Mechanical drive! ! With J-suite. 201111 Fist Drive Stack. 21... Drive shaft, 23.24... Drive gear, 2
5-01 Main spring assembly. 26・-Φ winding key, 40---output stack. 42.-φ output shaft, 43.44...pinion. 45φ/output gear. 46.47--4r car plate. 50... Speed control device. 47a-47e Sanken/Gang, 4811... Annular edge surface,
60・φ・1st reduction gear stack, 63 Y・-shaft, 61.62・・・Pinion. 62altlII+dent, 62b--, outer surface,
64.65-・11vi1 car plate. 70...Second reduction gear stack, 71.72--Coupling pinion. 74.75...Gear plate. 100--Takagashij tome ratchet wheel stack. 101.102・Good pinion, 105,106ψ・e ratchet wheel, 107--
φ ratchet wheel axis. 140--Lever stack. 141.142 Fist: Lever, 144: Battle lever shaft. 14B--bin, 120-- flywheel stack. 122.123・φ・flywheel. ! 24・1111 flywheel, 125,126・l
·cam. 150---Centrifugal device, 151---Base member,
152--Bottle stop body, 155--Centrifugal member. Engraving of the drawings (no changes to the contents) Figure 1 Figure 2 Figure 3 Procedural n Engineering Manual (Method) % Formula % 2. Name of the invention: Fail-safe mechanical mechanical system for syringes 3. Amendment. Name of patent applicant: Daltex Medical Sciences Incorporated 4, Agent 5, Date of amendment order Sent date: September 24, 1985 6, Subject of amendment

Claims (1)

[Scope of Claims] 1) Rotary drive means for generating a drive torque with respect to a first shaft; disposed coaxially with respect to the first shaft, each having a fixed rotational relationship with respect to the other; having the first and second
a drive gear for providing an output excursion; a second shaft coaxially fixed with respect to the second shaft and respectively associated with the first and second drive gears; first and second pinion members that transmit torque to each other and have a fixed rotational relationship with respect to each other, the rotational relationship between the first and second pinion members being in a fixed rotational relationship with respect to each other; said first and second pinion members corresponding in part to said relationship between drive gears of said first and second pinion members; speed control means for determining a time rate; and coaxially fixed relative to said second shaft; A drive device for providing a speed controlled output excursion comprising control gear means coupling said second shaft to said speed control means. 2) The first and second drive gears are offset with respect to each other such that the gear teeth on each of the first and second drive gears are axially misaligned. The drive device according to scope 1. 3) The first and second drive gears have the same number of gear teeth, and the rotational relationship between the first and second drive gears and between the first and second pinion members is similar to that of each gear. 3. A drive device as claimed in claim 2, which accommodates maximum axial misalignment between teeth. 4) said speed control means: first and second ratchet wheels coaxially fixed on a common ratchet wheel axis; coaxially fixed on a flywheel axle and configured to operate at a predetermined frequency; a rotationally oscillating flywheel; and a flywheel coaxially disposed on a common lever shaft such that it rotates simultaneously with said common lever shaft and said flywheel in response to said predetermined vibration frequency of said flywheel; The drive device according to claim 1, comprising first and second lever members that control the rotational speeds of the first and second ratchet wheels. 5) The drive apparatus of claim 4, wherein said speed control means further comprises rotational coupling means for rotationally coupling said control gear means to said common ratchet wheel axis. 6) A drive device according to claim 5, wherein said rotational coupling means comprises gear reduction means, whereby said common ratchet wheel axis rotates at a faster speed than said control gear means. 7) The drive device according to claim 4, further comprising frequency control means for controlling the predetermined vibration frequency of the flywheel. 8) The frequency control means comprises: a helical spring means substantially coaxially fixed on the common flywheel; and means for adjusting the tension within the helical spring means. The drive device according to item 7. 9) The drive device according to claim 1, further comprising runaway safety means for preventing uncontrolled rotation of the second shaft. 10) The runaway safety means; a predetermined pitch diameter D and at least one toothed member extending radially outward from the predetermined pitch diameter by a predetermined distance t. and a safety pinion having a predetermined pitch diameter and at least one receiver recess extending radially inwardly for accommodating said tooth member of said safety wheel means. 9. The drive device according to claim 9, wherein the drive device comprises means, and a gap distance between the safety wheel means and the safety pinion means is smaller than the predetermined distance t. . 11) said first and second drive gears are identical with respect to each other and rotationally fixed with respect to each other;
2. Drive device according to claim 1, wherein corresponding gear teeth on both drive gears are rotationally offset by an angular distance corresponding to at least three consecutive gear teeth. 12) said first and second pinion members are identical with respect to each other and rotationally fixed with respect to each other, such that corresponding pinion teeth on both pinion members correspond to at least three consecutive pinion teeth; 2. A drive device as claimed in claim 1, wherein the drive device is rotationally offset by an angular distance. 13) The driving gear has a pitch diameter of ￥D￥ and ￥n￥ gear teeth are arranged on its outer periphery, and the driven gear has a pitch diameter of ￥d￥.
A fail-safe device that has ￥n￥ gear teeth on its outer periphery and prevents desynchronization between the driving gear shaft to which the driving gear is fixed and the driven gear shaft to which the driven gear is fixed. a safety drive gear means fixed to the drive gear shaft coaxially with the drive gear and having N' gear teeth smaller than N; and a driven gear coaxially with the driven gear. The fail-safe device further comprises a secured drive gear means fixed to the shaft and having a number n' gear teeth less than n. 14) The fail-safe device according to claim 13, wherein the ratio N/n of the number of teeth is reduced to an integer ¥ I ¥. 15) The ratio N/n of the number of teeth is the sum of the integer I and a fraction a/b that is mathematically reduced by using ¥a¥ and ¥b¥ as integers; 15. The fail-safe device according to claim 14, wherein has at least ￥b￥ teeth. 16) The safety drive gear means and the safety driven gear means have a predetermined gap between them, and the gear teeth of the safety drive gear means are arranged within the predetermined gap. 14. A fail-safe device as claimed in claim 13, in which the radially extending radially outwardly extend a greater distance. 17) A centrifugal safety means fixed to the driven gear shaft for preventing the driven gear shaft from rotating substantially above a predetermined rotational speed is further provided. Fail-safe device according to clause 13. 18) said centrifugal safety means: a rotatable base means disposed parallel and coaxially with the driven gear; disposed on said rotatable base means and adapted to prevent rotation of said rotatable base means; a centrifugal member moving radially outwardly from said rotatable base means in response to velocity; and a centrifugal member stationary disposed proximate said rotatable base means, said rotatable base means 18. The fail-safe device of claim 17, further comprising a stop member that engages said centrifugal member when rotating at a speed substantially greater than said predetermined rotational speed. 19) A fail-safe device according to claim 18, further comprising elastic means for urging the centrifugal member radially inwardly of the rotatable base member. 20) Output shaft means for rotating at a predetermined speed; Drive means having first and second gear transmissions arranged to operate simultaneously; and Control means for controlling the rotational speed of the output shaft means. A mechanical drive device comprising the control means, comprising fail-safe means for preventing the output shaft means from rotating uncontrollably.