Abstract:
This invention discloses a hose or cable reeler that can retract a hose or cable without the need for a retracting coil spring. The reeler generally comprises a reeling wheel assembly and a reeling wheel drive. The reeling wheel assembly is detachably coupled with the reeling wheel drive by means of a clutch. The reeling wheel drive mainly comprises a gear transmission chain, and is operated through a lever by manpower (e.g., treading of a foot). Since manpower is used to retract the hose or cable, this invention avoids the related problems that may occur when the retraction is achieved completely relying on the coil spring. For example, the disordered brandish, which may occur owing to an excessive retractive force, can be avoided during the retraction of the hose or cable, and a combined drive of manpower and retractive force of the coil spring is possible. Therefore, the hose (cable) reeler of this disclosure allows for an operation of the hose or cable in a relatively laborsaving, convenient and safe manner.

Description:
CROSS SECTION TO RELATED APPLICATION 
     This application claims priority under 35 U.S.C. §119 to Chinese Patent Application Ser. No. 2006.2011.2698.7, filed May 9, 2006, entitled, HOSE/CABLE REELER. 
     TECHNICAL FIELD 
     This invention relates to a hose (or cable) reeler used to store up hoses, cables or the like, and particularly to a treadle hose/cable reeler that achieves the retraction of hoses or cables using manpower, such as treading of a foot. 
     BACKGROUND ART 
     In the prior art hose/cable reelers used to store up hoses, cables or the like, the retraction of hoses or the like is achieved purely relying on a coil spring mounted inside the reeler. With the prior equipment, there are some problems as follows: the cost of the equipment is increased due to the need for a retracting coil spring; since the retraction is achieved by the coil spring, the retraction speed of the hose may be too fast and therefore during the retraction of the hose a brandish of the hose may occur, which may cause harms to people or damages to the hoses or cables; and once the coil spring fails, its maintenance or replacement is time-consuming and laborious. 
     SUMMARY OF THE INVENTION 
     It is an objective of this invention is to solve the above problems in the prior art. This invention aims to provide a hose/cable reeler which achieves the hose retraction without the need for a retracting coil spring, and therefore avoids the problems associated with the use of the retracting coil spring. In this invention, a coil spring is provided only as an auxiliary unit and has two functions: one is to increase the retractive force during the retraction of hoses or cables, and the other is to keep the continuity of the hoses or cables during extension or retraction and to solve the problems associated with the retraction purely relying on manpower. 
     In order to achieve the above objective, this invention provides a hose/cable reeler, comprising: a housing; a reeling wheel assembly, mounted in the housing, and including a reeling wheel axle supported by the housing and a reeling wheel mounted on the reeling wheel axle with the reeling wheel axle serving as a center, the reeling wheel being adapted to wind a hose, cable or the like thereon, and to rotate in a first direction to wind the hose and in a second direction opposite to the first direction to unwind the hose; and a reeling wheel drive mounted in the housing and detachably coupled with the reeling wheel through a clutch to drive the reeling wheel to rotate in the first direction, the reeling wheel being coupled with the reeling wheel drive when the clutch is operated into an engaged state, and the reeling wheel being uncoupled from the reeling wheel drive when the clutch is operated into a disengaged state. 
     The reeling wheel drive of the invention comprises: a lever, swingably supported by the housing, and having a stationary portion that is pivoted to the housing and a free end that is opposite to the stationary portion, the lever being adapted to swing manually within a predetermined range between a start position and an end position with the stationary portion as a fulcrum, and the lever being connected with a spring and biased by the spring towards the start position; a driven gear mounted coaxially and fixedly with respect to the reeling wheel; a driving gear mounted to engage the driven gear; a transmission gear mounted coaxially with respect to the driving gear; and a transmission member engaged with the transmission gear to drive the transmission gear, the transmission member having mesh teeth on a side facing the transmission gear to mesh with the driving gear, and the transmission member being connected with the lever to reciprocate as the lever swings. 
     In the above hose/cable reeler, the clutch may be an overrunning clutch, comprising a first clutch half and a second clutch half that are able to axially engage with and disengage from each other and a control mechanism that cooperates with the first clutch half to control the axial engagement and disengagement between the first clutch half and the second clutch half, the control mechanism including: a control member that is able to rotate on the reeling wheel axle and has a first cam portion; a first cam follower portion provided on the first clutch half and cooperated with the first cam portion of the control member; a second cam portion provided on the reeling wheel axle; a second cam follower portion provided on the first clutch half and cooperated with the second cam portion provided on the reeling wheel axle; a compression spring provided between the first clutch half and the second clutch half for biasing the halves in a direction of disengagement thereof, and a rotation damping means to damp down the rotation of the control member, wherein the control member is disposed to be axially stationary relative to the reeling wheel axle, the first clutch half is disposed relative to the reeling wheel axle so as to be movable axially within a determined lengthwise range and be rotatable within a determined angular range, the second clutch half is fixed to the reeling wheel, the first cam portion of the control member and the first cam follower portion of the first clutch half are configured such that when the first clutch half rotates, along with the second clutch half and the reeling wheel, in the second direction relative to the control member or when the reeling wheel rotates in the first direction relative to the reeling wheel axle, the first clutch half moves axially in a direction away from the second clutch half under the bias of the compression spring, whereby the clutch is operated into the disengaged state, and the second cam portion of the reeling wheel axle and the second cam follower portion of the first clutch half are configured such that when the reeling wheel axle rotates in the first direction relative to the first clutch half and the reeling wheel within the determined angular, the first clutch half moves axially towards the second clutch half against the bias of the compression spring, whereby the clutch is operated into the engaged state. The first cam portion may comprise at least one recess having a slope fixedly disposed on the control member and the first cam follower portion comprises at least one cog fixedly disposed on the first clutch half, the cog fitting in the recess and being able to slide along the slope of the recess. The cog may have a slope that is complementary to and mates with the slope of the recess. The second cam portion may comprise at least one key fixedly disposed on a circumferential surface of the reeling wheel axle and the second cam follower portion comprises at least one shaped groove having a slope fixedly disposed on the first clutch half, the key fitting in the shaped groove and being able to slide along the slope of the shaped groove. The key may have a slope that is complementary to and mates with the slope of the shaped groove. Both the first clutch half and the second clutch half may be formed with teeth on opposing end surfaces thereof, the first clutch half and the second clutch half being engaged with each other by means of the teeth. Both the first clutch half and the second clutch half may be formed with a counterbore on opposing end surfaces thereof, the compression spring being disposed between the first clutch half and the second clutch half with its opposite ends seated in the two counterbores respectively. The control member may be formed as a wave wheel with waved teeth on its circumference, the wave wheel being rotatably mounted on the reeling wheel axle, the waved teeth of the wave wheel being engaged with a detent that is mounted to the housing by means of a spring, and the detent engaging the waved teeth of the wave wheel under the bias of the spring, whereby the waved teeth, the detent and the spring constitute the rotation damping means for damping down the rotation of the wave wheel on the reeling wheel axle. The control member may be formed as a belt pulley with a belt winding portion on its circumference, the belt pulley being rotatably mounted on the reeling wheel axle, and a belt being wound on the belt winding portion of the belt pulley with opposite ends of the belt fixed to a stationary portion of the housing under a determined tension, whereby the belt and the belt winding portion constitute the rotation damping means for damping down the rotation of the belt pulley on the reeling wheel axle. The rotation damping means may further comprise a tension spring connected between one end of the belt and the stationary portion of the housing. 
     In the above hose/cable reeler, the clutch may comprise a first clutch half and a second clutch half that are able to axially engage with and disengage from each other and a control mechanism that cooperates with the first clutch half to control the axial engagement and disengagement between the first clutch half and the second clutch half, both the first clutch half and second clutch half being formed with one-way teeth that are able to engage with each other in a one-way manner, the first clutch half being fixed to the driven gear, and the second clutch half being fixed to the reeling wheel, wherein the control mechanism comprises: an external thread formed on a portion of a circumferential surface of the reeling wheel axle; an internal thread formed in a central bore of the first clutch half and engaging the external thread, the first clutch half being movable axially relative to the reeling wheel axle within a predetermined range by means of a screwing action between the internal thread and the external thread; a compression spring disposed between the first clutch half and second clutch half for biasing the first clutch half and second clutch half in a direction to separate them from each other; and a rotation damping means adapted to damp down the rotation of the reeling wheel axle, wherein the internal thread and the external are configured such that when rotating in the first direction the first clutch half moves axially towards the second clutch half against the bias of the compression spring until it is engaged with the second clutch half. The rotation damping means may comprise a wave wheel that is fixed to the reeling wheel axle and has waved teeth on its circumference, and a detent that is mounted to the housing through a spring and engages the waved teeth of the wave wheel, the detent engaging the waved teeth of the wave wheel under the bias of the spring to damp down the rotation of the wave wheel. The rotation damping means may comprise a belt pulley that is fixed to the reeling wheel axle and has a belt winding portion on its circumference, and a belt that is wound on the belt winding portion of the belt pulley, with opposite ends of the belt being fixed to a stationary portion of the housing under a determined tension, for damping down the rotation of the belt pulley. The rotation damping means may further comprise a tension spring that is connected between one end of the belt and the stationary portion of the housing. Both the first clutch half and the second clutch half may be formed with a counterbore on opposing end surfaces thereof, the compression spring being disposed between the first clutch half and the second clutch half with its opposite ends seated in the two counterbores respectively. The mating internal thread and external thread may be multi start thread. 
     In the above hose/cable reeler, the reeling wheel axle may comprise a principal reeling wheel axle that is fixed to the housing and a semi reeling wheel axle that is coaxial with the principal reeling wheel axle and is rotatably supported by the housing, and the reeling wheel assembly further comprises a coil spring mounted between the principal reeling wheel axle and the reeling wheel, with one end of the coil spring fixed to the principal reeling wheel axle and other end fixed to the reeling wheel. 
     In the above hose/cable reeler, the clutch is a manually operated clutch. The manually operated clutch may comprise a first clutch half and a second clutch half that are able to be axially engaged with and disengaged from each other, and a manually operated mechanism that is connected with at least one of the two clutch halves to control the axial engagement and disengagement between the first clutch half and the second clutch half. 
     In the above hose/cable reeler, a treadle may be mounted on the free end of the lever for treading. 
     In the above hose/cable reeler, the transmission member in the reeling wheel drive may be a sector gear that is fixed to the lever and swings reciprocally about the stationary portion along with the lever. The sector gear may be an internal gear. 
     In the above hose/cable reeler, the transmission member in the reeling wheel drive may be a gear rack, one end of which is connected to the lever so as to reciprocate linearly as the lever swings. 
     Since manpower (e.g., treading of a foot) is used as a moving force to retract a hose or cable, this invention avoids the related problems which may occur when the retraction is achieved completely relying on a retracting coil spring. For example, the brandish, which may occur owing to an excessive retractive force, can be avoided during the retraction of the hose or cable, and a combined drive of manpower and the retractive force of a coil spring is possible. Therefore, the hose/cable reeler of this invention allows for an operation of the hose or cable in a relatively labour-saving, convenient and safe manner. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is an exploded view of a treadle hose reeler according to a first embodiment of the invention; 
         FIG. 2  is an exploded view of a hose distribution mechanism shown in  FIG. 1 ; 
         FIG. 3  is a front view of a first clutch half of an overrunning clutch used in the invention; 
         FIG. 4  is a sectional view along the A-A line in  FIG. 3 ; 
         FIG. 5  is a sectional view of a second clutch half of the overrunning clutch; 
         FIG. 6  is a front view of a semi reeling wheel axle; 
         FIG. 7  is a sectional view along the B-B line in  FIG. 6 ; 
         FIG. 8  is a perspective view of a control member of the overrunning clutch; 
         FIG. 9  is a sectional view of a principal reeling wheel axle; 
         FIG. 10  is an assembly diagram of the overrunning clutch; 
         FIG. 11  is a schematic diagram showing the engagement between the first clutch half and the control member; 
         FIG. 12  is a schematic diagram showing the movement of various parts of a reeling wheel drive when a treadle is trod down; 
         FIG. 13  is a schematic diagram showing the movement of the various parts of the reeling wheel drive when the treadle is released; 
         FIG. 14  is an exploded view of a treadle hose reeler according to a second embodiment of the invention; 
         FIG. 15  is a front view of a semi reeling wheel axle used in the second embodiment; 
         FIG. 16  is a sectional view along the B-B line in  FIG. 15 ; 
         FIG. 17  is a perspective view of a transmission member used in the second embodiment; 
         FIG. 18  is a perspective view of a driven gear used in the second embodiment; 
         FIG. 19  is a schematic assembly diagram of a driven gear, a semi reeling wheel axle, a compression spring and a transmission member that constitute a clutch in the second embodiment; 
         FIG. 20  is a schematic diagram showing the movements of various parts of a reeling wheel drive when a treadle is trod down in the second embodiment; 
         FIG. 21  is a schematic diagram showing the movements of the various parts of the reeling wheel drive when the treadle is released; 
         FIG. 22  is an exploded view of a reeling wheel drive in a hose reeler according to a third embodiment of the invention; 
         FIG. 23  is a schematic diagram showing the movements of various parts of the reeling wheel drive when a treadle is trod down in the third embodiment; 
         FIG. 24  is a schematic diagram showing the movements of the various parts of the reeling wheel drive when the treadle is released in the third embodiment; 
         FIG. 25  is an exploded view of a treadle hose reeler according to a fourth embodiment of the invention; 
         FIG. 26  is a schematic diagram showing the movement of various parts of a reeling wheel drive when a treadle is trod down in the fourth embodiment; 
         FIG. 27  is a schematic diagram showing the movement of the various parts of the reeling wheel drive when the treadle is released in the fourth embodiment; 
         FIG. 28  is an exploded view of a treadle hose reeler according to a fifth embodiment of the invention; 
         FIG. 29  is a schematic diagram which shows the movements of various parts of the reeling wheel drive when a treadle is trod down in the fifth embodiment; 
         FIG. 30  is a schematic diagram showing the movements of the various parts of the reeling wheel drive when the treadle is released in the fifth embodiment; 
         FIG. 31  shows a modification of main parts (an internal sector gear and a lever) in the reeling wheel drive of the invention shown in  FIG. 1 ; and 
         FIG. 32  shows a modification of the control member in the overrunning clutch of the invention shown in  FIG. 8 , wherein (a) is a perspective view and (b) is a schematic assembly diagram of the control member. 
     
    
    
     DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS 
     Several preferred embodiment of the invention will be described with reference to the accompanying drawings. For the purpose of simplicity and clarity, only the mechanisms and components which are related to the invention will be described in the embodiments in detail, and other mechanisms in the hose reeler such as hose distribution mechanism, water (air) inlet and outlet mechanism and the like which are not related to the invention will be described schematically and briefly. 
     First Embodiment 
     See  FIGS. 1-13 , which show a hose reeler according to the first embodiment of the invention. The hose reeler is a treadle hose reeler and is use to store up a hose  10 . In order to prevent the hose  10  from being completely wound into the housing, a stopper  9  is fixed at the end of the hose  10 . The hose reeler mainly comprises a housing, a reeling wheel assembly  46 , a clutch  47 , a reeling wheel drive  45 , a hose distribution mechanism and a water (air) inlet and outlet mechanism. The housing is composed of a right housing  3  and a left housing  24 . There is a side cover  36  on the left housing  24 . A partition  37  is provided in the left housing  24  which substantially separates the left housing  24  into two, left and right, chambers. The left chamber is sealed by the side cover  36  and is used to hold a reeling wheel drive  45 . The right chamber is sealed by the right housing  3  and is used to hold a reeling wheel assembly  46  and a clutch  47 . 
     The reeling wheel assembly  46  comprises a principal reeling wheel axle  15  fixed to the left housing  24  and the right housing  3 , a semi reeling wheel axle  16  rotatably mounted on the principal reeling wheel axle  15 , a coil spring  14 , and a reeling wheel that is mounted on and can rotate about the principal reeling wheel axle  15 . The reeling wheel consists of a left reeling wheel disk  17  and a right reeling wheel disk  13  which are connected together. A central through hole  38  in the left reeling wheel disk  17  is fit with a circumferential surface  48  of the semi reeling wheel axle  16 . A left end of the right reeling wheel disk  13  is fixed to the left reeling wheel disk  17 , and a right end thereof is rotatably supported on a circumferential surface  41  of a stationary axle  4  which is fixed to the right housing  3 . A shaped key  40  on the right end of the principal reeling wheel axle  15  cooperates with a shaped hole  42  in the stationary axle  4  which is fixed to the right housing  3 . In this way, the principal reeling wheel axle  15  is fixed to the right housing  3  through the stationary axle  4 . The left end of the principal reeling wheel axle  15  is movably connected with the semi reeling wheel axle  16  through an axial part  39  provided on the axle  15  and a hole  50  in the axle  16 . On the right end of the principal reeling wheel axle  15  there is a slit  49 . One end of the coil spring  14  is fixed to the right reeling wheel disk  13  and the other end is fixed to the principal reeling wheel axle  15  through the slit  49 . 
     The clutch  47  is an overrunning clutch which consists of a first clutch half  20  and a second clutch half  18  with teeth on their one end face respectively and a control mechanism which is fit with the first clutch half  20  (the left one in  FIG. 1 ). The teeth  51  on the right end face of the first clutch half  20  can be engaged with and disengaged from the teeth  52  on the left end face of the second clutch half  18 , therefore an axial engagement and disengagement between the two clutch halves can be obtained. The control mechanism consists of a control member  21 , a detent  22 , a spring  23  and the semi reeling wheel axle  16 . The second clutch half  18  is fixed to the left reeling wheel disk  17 . On the left side of the second clutch half  18  there is a counterbore  53 . On the right side of the first clutch half  20  there is a counterbore  54  and on the left side of the first clutch half  20  there are one-way cogs  55 . Along the axial direction of the first clutch half  20  there are four shaped grooves  56  each with a shape of            .
     A compression spring  19  is fit around a circumferential surface of the semi reeling wheel axle  16 , with its one end seated in the counterbore  53  of the second clutch half  18  and the other end seated in the counterbore  54  of the first clutch half  20 . There are four shaped keys  57  having a shape of            , which fit with the respective shaped grooves  56  on the first clutch half  20 . The control member  21  is formed as a wave wheel with waved teeth around its circumference. On the right side there are recesses  58  which can be engaged with the one-way cogs  55  on the first clutch half  20 . The control member  21  is rotatably situated around a cylindrical portion of the semi reeling wheel axle  16 , with no axial movement allowed relative to the semi reeling wheel axle  16 . The detent  22  is fixed to a stationary portion of the left housing  24 . One end of the spring  23  is fixed to a stationary portion of the left housing  24  and the other end thereof is connected to the detent  22 . The detent  22  is used to damp down the rotation of the control member  21  in any direction.
     The hose distribution mechanism is mounted on the housing and consists of a synchronizing gear  6 , a synchronizing gear cover  5 , a guide column d, a pinion gear a, a two-way trapezoid screw b, a commutator c, a mounting frame e, two small pulleys f, two iron bars g, and a timing toothed belt  7 . The synchronizing gear  6  is coaxially fixed to the right side of the right reeling wheel disk  13 . The synchronizing gear cover  5  is connected to the synchronizing gear  6  which is connected to the hose distribution mechanism through the timing toothed belt  7 . The pinion gear a is situated on one side of the two-way trapezoid screw b to correspond to the synchronizing gear  6 . The mounting frame e is situated on the two-way trapezoid screw b. The commutator c is situated on the mounting frame e. The guide column d is situated on the left housing  24  and the right housing  3 . A round hole  66  in the mounting frame e is fit with the guide column d. The small pulleys are movably connected to the mounting frame e through the two iron bars g. The function of the hose distribution mechanism is to distribute the hose (or cable) in order during winding. When a hose or cable is being wound up, the right reeling wheel disk  13  drives the synchronizing gear  6  to rotate, and the synchronizing gear  6  in turn drives the pinion gear a through the timing toothed belt  7 , therefore the two-way trapezoid screw b is rotated. In this way, the distribution of the hose can be achieved. Once a layer of the hose is full up, the mounting frame will automatically switch over to the next layer by means of the commutator c. 
     The water (air) inlet and outlet mechanism mainly consists of a water (air) tie-in  2 , a stationary axle  4  and a water (air) inlet connector  11 . One end of the stationary axle  4  is fixed to the principal reeling wheel axle  15 , and the other end  43  thereof is specially shaped and is fit to a shaped hole  44  in the right housing  3  to fix the stationary axle  4 . There is an axial water (air) inlet in the stationary axle  4  with the tie-in  2  fixed to it. The water (air) inlet connector  11  is fit around the stationary axle  4 . On a side of the water (air) inlet connector  11  there is a water (air) outlet. The water (air) outlet of the stationary axle  4  corresponds to the water (air) outlet of the water (air) inlet connector  11 . A water (air) outlet hose  10  wound on the reeling wheel is connected to side water (air) outlet of the water (air) inlet connector  11 . At the joint between the stationary axle  4  and the water (air) inlet connector  11  there is a ring groove in which a sealing ring is fit. On one side of the ring groove of the stationary axle  4  there is a spring washer  12  which allows the stationary axle  4  and the water (air) inlet connector  11  to rotate freely with no leakage of water (air). A water (air) inlet pipe  1  is fixed to the water (air) tie-in  2 . 
     In this embodiment, the reeling wheel drive  45  consists of a tension spring  31 , a transmission gear  29 , an internal sector gear  30 , a driving gear  27 , a driven gear  28 , secondary axles  25  and  26 , a lever  34 , a treadle  35  and an optional bracket. The bracket consists of two horizontal columns  32  and two vertical cylindrical columns  33 , and is used to limit the movement of the lever  34 . The two columns  32  are fixed to a stationary portion of the left housing  24 . The two ends of the two cylindrical columns  33  are connected to the two columns  32 . The bracket is helpful to define the movement range of lever  34  in a firmer manner. However, in many cases, the bracket is not necessary and can be replaced by equivalent means. The lever  34  is pivotally mounted to the side cover  36  through the secondary axle  26  and can pivot about an axis of the secondary axle  26 . On a free end of the lever  34  there is a treadle  35  which can be trod by a user&#39;s foot to apply a force to the lever. An internal sector gear  30  is fixed to a side of the lever  34  opposite to the treadle  35 . The internal sector gear  30  is used as a transmission member which can engage the transmission gear  29  and therefore drive it. The internal sector gear  30  is fixed to the lever  34  in such a way that it can rotate about the secondary axle  26  as the lever  34  swings. The transmission gear  29  is engaged internally with the internal sector gear  30 . The transmission gear  29  and the driving gear  27  are coaxially fixed to the secondary axle  25  which is fixed to a stationary portion of the left housing  24 . The secondary axle  25  can rotate about its axis. The driving gear  27  engages the driven gear  28  externally. The driven gear  28  is coaxially fixed to the semi reeling wheel axle  16 . One end of the tension spring  31  is fixed to a stationary portion of the housing, and the other end thereof is fixed to the lever proximate to the treadle. 
     When the hose is pulled out, the lever  34  is at the start position with the clutch  47  in the disengaged state. At this time, both the principal reeling wheel axle  15  and the semi reeling wheel axle  16  remain stationary, and the reeling wheel rotates counterclockwise about the principal reeling wheel axle  15 . During the rotation of the reeling wheel, the coil spring  14  is tensioned, and the energy is accumulated. 
     When the treadle  35  is being pressed down, the lever  34  drives the internal sector gear  30  to rotate counterclockwise. Under the action of the internal sector gear  30 , the transmission gear  29  rotates counterclockwise. Since the driving gear  27  and the transmission gear  29  are fixed coaxially, the driving gear  27  rotates counterclockwise under the driving of the transmission gear  29 . Acted by the driving gear  27 , the driven gear  28  rotates clockwise. Since the driven gear  28  is fixed to the semi reeling wheel axle  16 , the semi reeling wheel axle  16  rotates clockwise under the action of the driven gear  28 . The rotation of the semi reeling wheel axle  16  causes the first clutch half  20  to rotate clockwise. Since at this time the one-way cogs  55  of the first clutch half  20  are engaged with the recesses  58  of the control member  21  and the detent  22  damps down the rotation of the control member  21 , the movement of the first clutch half  20  lags behind the movement of the semi reeling wheel axle  16 . Under the camming actions between the slopes of the shaped keys  57  of the semi reeling wheel axle  16  and the slopes of the shaped grooves  56  of the first clutch half  20 , the one-way cogs  55  of the first clutch half  20  slide out of the recesses  58  of the control member  21 , and the first clutch half moves toward the second clutch half  18  against the action of the compression spring  19 , resulting in the engagement of the teeth  51  of the first clutch half  20  with the teeth  52  of the second clutch half  18 . Therefore, the first clutch half and the second clutch half are engaged with each other axially. Then the first clutch half  20  drives the second clutch half  18  to rotate clockwise, and in turn, drives the reeling wheel to rotate clockwise. Thus, the retraction of the hose is achieved. At this time, the tension spring  31  is in tension. 
     During the retraction of the hose, energy is released from the coil spring  14 . The coil spring  14  has two functions, one is to increase the retractive force and the other is to keep the continuity of the hose retraction. Of course, the elasticity of the coil spring  14  is lower than that of the coil spring used in a conventional hose reeler in which the hose retraction purely relies on the retracting coil spring. Once the clockwise rotation speed of the reeling wheel is higher than that of the semi reeling wheel axle  16  under the action of the coil spring  14  and the inertia, there will be a relative rotation between the reeling wheel and the semi reeling wheel axle  16 . Meanwhile, the first clutch half  20  rotates clockwise with the reeling wheel. That means there is a relative rotation between the semi reeling wheel axle  16  and first clutch half  20 . When the shaped key  57  of the semi reeling wheel axle  16  slides along the slope of the shaped groove  56  to the opening  59 , i.e., the portion having no slope, of the shaped groove  56  following the rotation of the semi reeling wheel axle  16 , the first clutch half  20  moves axially away from the second clutch half  18  under the action of the compression spring  19  and therefore the clutch is in the disengaged state. In this way, the reeling wheel is allowed to rotate in a speed higher than that of the semi reeling wheel axle  16 . 
     When the treadle  35  is released, the lever  34  drives the internal sector gear  30  to rotate clockwise under the action of the tension spring  31 , and the transmission gear  29  rotates clockwise under the action of the internal sector gear. Since the driving gear  27  is coaxially fixed to the transmission gear  29 , the driving gear  27  rotates clockwise under the driving of the transmission gear  29 , and the driven gear  28  rotates counterclockwise under the action of the driving gear  27 . Since the driven gear  28  is fixed to the semi reeling wheel axle  16 , under the action of the driven gear  28 , the semi reeling wheel axle  16  rotates counterclockwise. During the counterclockwise rotation of the semi reeling wheel axle  16 , due to the axial bias of the compression spring  19  to the first clutch half  20  and the camming action of the recesses  58  of the control member  21  on the one-way cogs  55  of the first clutch half  20 , the first clutch half  20  moves axially away from the second clutch half  18  until the one-way cogs  56  of the first clutch half  20  entirely fall into the recesses  58  of the control member  21 , and therefore the clutch  47  is in the disengaged state. 
     Second Embodiment 
     See  FIG. 14-21  which show a hose reeler according to the second embodiment of the invention. In order to be simple, the mechanisms such as the hose distribution mechanism and the water (air) inlet and outlet mechanism which are the same as in the first embodiment will not be described. 
     In this embodiment, except the clutch  47 B and the semi reeling wheel axle  16 B, the structures are basically the same as in the first embodiment. In this embodiment, the semi reeling wheel axle  16 B is a substantially smooth axle, and its circumferential surface  48  is movably fit to a central through hole  38  of the left disk  17 . The left end of the principal reeling wheel axle  15  is movably coupled to the semi reeling wheel axle  16 B through an axial part  39  provided on the left end of the axle  15  and a hole  50  in the axle  16 . There is a length of external thread  65  proximate the middle portion of the semi reeling wheel axle  16 B. 
     The reeling wheel drive  45  consists of a tension spring  31 , a transmission gear  29 , an internal sector gear  30 , a driving gear  27 , a driven gear  28 , secondary axles  25  and  26 , a lever  34 , a treadle  35  and an optional bracket. The lever  34  is pivotally mounted to the side cover  36  through the secondary axle  26  and can pivot about an axis of the secondary axle  26 . On a free end of the lever  34  there is a treadle  35  which can be trod by a user&#39;s foot to apply a force to the lever. An internal sector gear  30  is fixed to a side of the lever  34  opposite to the treadle  35 . The internal sector gear  30  is used as a transmission member which can engage the transmission gear  29  and therefore drive it. The internal sector gear  30  is fixed to the lever  34  in such a way that it can rotate about the secondary axle  26  as the lever  34  swings. The transmission gear  29  is engaged internally with the internal sector gear  30 . The transmission gear  29  and the driving gear  27  are coaxially fixed to the secondary axle  25  which is fixed to a stationary portion of the left housing  24 . The secondary axle  25  can rotate about its axis. The driving gear  27  engages the driven gear  28  externally. One end of the tension spring  31  is fixed to a stationary portion of the housing, and the other end thereof is fixed to the lever  34  proximate to the treadle. 
     In this embodiment, the clutch  47 B consists of a driven gear  28 B, a transmission connector  18 B, a semi reeling wheel axle  16 B, and a rotation damping means that damps down the rotation of the semi reeling wheel axle. On a side of the driven gear  28 B facing the reeling wheel there are one-way teeth  63  that are distributed regularly, which corresponds to a first clutch half. There is a counterbore  62  in the driven gear  28 B axially, and in an axial hole of the driven gear there is provided an internal thread  64 . The transmission connector  18 B is coaxially fixed to the reeling wheel. On a side of the transmission connector  18 B facing the driven gear  28 B there are one-way teeth  61  that can mesh with the one-way teeth in a one-way manner, which corresponds to a second clutch half. There is an axial counterbore  60  on the transmission connector  18 B, an axial hole  66  of which is movably fit with a circumferential surface  48  of the semi reeling wheel axle  16 B. The structure of the one-way teeth  61  and  63  which mesh with each other in the one-way manner is well known in art, for example, including the incline teeth arranged circumferentially. The driven gear  28 B and the semi reeling wheel axle  16 B are cooperatively coupled with each other through the internal thread  64  and the external thread  65 , and the driven gear  28 B is allowed to move axially on the semi reeling wheel axle  16 B within a predetermined range via the screwing action of these threads. Preferably, the internal and external threads  64 ,  65  are multi start threads. A compression spring  19 B is fit around the circumferential surface of the semi reeling wheel axle  16 B, with one end seated in the counterbore  62  of the driven gear  28 B and the other seated in the counterbore  60  of the transmission connector  18 B. The compression spring  19 B is used to bias the driven gear  28 B in a direction away from the transmission connector  18 B. The rotation damp mechanism consists of a wave wheel  21 B that is fixed to the semi reeling wheel axle  16 B and has waved teeth on its circumference, and a detent  22  that is engaged with the waved teeth of the wave wheel  21 B and is fixed to the left housing  24  through a spring  23 . One end of the spring  23  is fixed to a stationary portion of the left housing  24  and the other end thereof is connected to the detent  22 . The detent  22  is used to damp down the rotation in any direction of the wave wheel  21 B, and in turn, the semi reeling wheel axle  16 B. 
     When the hose is pulled out, the lever  34  is in the start position and the one-way teeth  63  on the driven gear  28 B and the one-way teeth  61  on the transmission connector  18 B are in the disengaged state. At this time, both the principal reeling wheel axle  15  and the semi reeling wheel axle  16 B remain stationary, and the reeling wheel rotates counterclockwise about the principal reeling wheel axle  15 . During the movement of the reeling wheel, the coil spring  14  is tensioned, which means the energy is accumulated. 
     When the treadle  35  is being pressed down, the lever  34  drives the internal sector gear  30  to rotate counterclockwise, and the transmission gear  29  rotates counterclockwise under the action of the internal sector gear  30 . Since the driving gear  27  and the transmission gear  29  are fixed coaxially, the driving gear  27  rotates counterclockwise under the driving of the transmission gear  29 . Acted by the driving gear  27 , the driven gear  28 B rotates clockwise. Since the driven gear  28 B is cooperatively coupled with the semi reeling wheel axle  16 B by means of threads, the clockwise rotation of the driven gear  28 B causes the semi reeling wheel axle  16 B to rotate clockwise therewith. However, due to the damping action of the detent  22  on the rotation of the rotation damper  21 B, the rotation of the semi reeling wheel axle  16 B lags behind the rotation of the driven gear  28 B. In this case, the driven gear  28 B moves on the semi reeling wheel axle  16 B toward the transmission connector  18 B via screwing action, until the one-way teeth  63  on the driven gear  28 B mesh with the one-way teeth  61  on the transmission connector  18 B, which operates the clutch  47 B into the engaged state. Then, under the action of the driven gear  28 B, the transmission connector  18 B rotates clockwise, which drives the reeling wheel fixed thereto to rotate clockwise. Therefore the hose is retracted. At this time, the tension spring  31  is in tension. 
     During the retraction of the hose, energy is released from the coil spring  14 . The coil spring  14  has two functions, one is to increase the retractive force and the other is to keep the continuity of the hose retraction. Of course, the elasticity of the coil spring  14  is lower than that of the coil spring used in a conventional hose reeler in which the hose retraction purely relies on the coil spring. Once the clockwise rotation speed of the reeling wheel is higher than that of the semi reeling wheel axle  16  under the action of the coil spring  14  and the inertia (i.e., there is a relative rotation between the transmission connector  18 B and the driven gear  28 B, and the movement of the driven gear  28 B lags behind the movement of the transmission connector  18 B), due to the damping action of the detent  22  on the wave wheel  21 B, the semi reeling wheel axle  16 B remains stationary relative to the driven gear  28 B, and the one-way teeth  63  of the driven gear  28 B escape from the one-way teeth  61  of the transmission connector  18 B under the actions of the one-way teeth  61  of the transmission connector  18 B and the compression spring  19 B. Then, the transmission gear  28 B moves away from the transmission connector  18 B, until the one-way teeth  63  of the driven gear  28 B is disengaged from the one-way teeth  61  of the transmission connector  18 B. In this way, the reeling wheel is allowed to rotate in a speed higher than that of the semi reeling wheel axle  16 B. 
     When the treadle  35  is released, under the action of the tension spring  31 , the lever  34  drives the internal sector gear  30  to rotate clockwise, and under the action of the internal sector gear, the transmission gear  29  rotates clockwise. Since the driving gear  27  is coaxially fixed to the transmission gear  29 , driven by the transmission gear  29 , the driving gear  27  rotates clockwise, and the driven gear  28 B rotates counterclockwise under the action of the driving gear  27 . Due to the damping action of the detent  22  on the rotation damper  21 B, the semi reeling wheel axle  16 B remains stationary relative to the driven gear  28 B. In this case, the driven gear  28 B moves away from the transmission connector  18 B via the action of screwing. Then the one-way teeth  63  of the driven gear  28 B are disengaged from the one-way teeth  61  of the transmission connector  18 B. Therefore, the driven gear  28 B is in idle running about the axis of the semi reeling wheel axle  16 B. 
     Third Embodiment 
     See  FIGS. 22-24  which show a reeling wheel drive of a hose reeler according to the third embodiment of the invention. In the embodiment, except the reeling wheel drive, the components may be substantially the same as those in the first embodiment. Therefore, only the hose reeler drive is described and shown. As for the other parts, reference can be made to the first embodiment. 
     In this embodiment, the reeling wheel drive  45 B consists of a transmission gear  29 B, a gear rack  30 B, a driving gear  28 C, wire ropes  69  and  70 , pulleys  67  and  68 , a secondary axle  25 B, a tension spring  31 B, a lever  34 , a treadle  35  and an optional bracket. The lever  34  has a stationary portion pivotally mounted to the housing and an opposite free end. On the free end of the lever  34  there is a treadle  35  which can be trod by a user&#39;s foot to apply a force to the lever. The stationary portion of the lever  34  is pivotally fixed to the left housing  24  through a pivot  26 B. One end of the wire rope  69  is connected to an approximately middle portion of the lever  34  and the other is connected to the end of the gear rack  30 B proximate to the treadle  35 . One end of the wire rope  70  is connected to the end of the gear rack  30 B away from the treadle  35  and the other end thereof is connected to the tension spring  31 B, with the middle portion tensioned by the pulley  68 , One end of the tension spring  31 B is connected to the wire rope  70  and the other to a stationary portion of the left housing  24 . The pulleys  67 ,  68  are fixed to a stationary portion of the left housing  24  respectively. The gear rack  29 B is disposed such that when the treadle  35  is in the start position and end position the transmission gear  29 B always meshes with the gear rack  30 B. The transmission gear  29 B and the driving gear  27 B are coaxially fixed to the secondary axle  25 B which is fixed to a stationary portion of the left housing  24 . The secondary axle  25 B is rotatable about its axis. The driving gear  27 B is externally meshed with the driven gear  28 C. The driven gear  28 C and the semi reeling wheel axle  16  are coaxially fixed with each other. 
     When the hose is pulled out, the lever  34  is in the start position and the clutch  47  is in the disengaged state. At this time, both the principal reeling wheel axle  15  and the semi reeling wheel axle  16  remain stationary, and the reeling wheel rotates counterclockwise about the principal reeling wheel axle  15 . During the rotation of the reeling wheel, the coil spring  14  is tensioned, which means energy is accumulated. 
     When the treadle  35  is being pressed down, the lever  34  drives the wire rope  69  to move in a direction in which the hose is retracted, and therefore the gear rack  30 B is driven to move in the direction in which the hose is retracted. Under the action of the gear rack  30 B, the transmission gear  29 B rotates counterclockwise. Since the transmission gear  29 B is coaxially fixed to the driving gear  27 B, the transmission gear  29 B drives the driving gear  27 B to rotate counterclockwise, and under the action of the driving gear  27 B, the driven gear  28 C rotates clockwise. As the driven gear  28 C is fixed to the semi reeling wheel axle  16 , under the action of the driven gear  28 C, the semi reeling wheel axle  16  rotates clockwise. At this time, the clutch is in the engaged state (the principle is the same as in the first embodiment), and the reeling wheel rotates clockwise, whereby the hose is retracted. At this time, the tension spring  31 B is in tension. 
     During the retraction of the hose, energy is released from the coil spring  14 . Once the clockwise rotation speed of the reeling wheel is higher than that of the semi reeling wheel axle  16  under the action of the coil spring  14  and the inertia, there will be a relative rotation between the reeling wheel and the semi reeling wheel axle. Since the first clutch half  20  rotates clockwise following the reeling wheel, that means there is a relative rotation between the semi reeling wheel axle  16  and the first clutch half  20 . When the shaped key  57  on the semi reeling wheel axle  16  slides along the slope of the shaped groove  56  to the opening  59  of the shaped groove  56  as the semi reeling wheel axle  16  rotates, the first clutch half  20  moves axially away from the second clutch half  18  under the action of the compression spring  19 , and therefore the clutch is in the disengaged state. In this way, the reeling wheel is allowed to rotate in a speed higher than that of the semi reeling wheel axle  16 . 
     When the treadle  35  is released, under the action of the tension spring  31 B, the wire rope  70  moves in the direction in which the hose is pulled out, and therefore, the gear rack  30 B is driven. And under the action of the gear rack  30 B, the transmission gear  29 B rotates clockwise. Since the driving gear  27 B is coaxially fixed to the transmission gear  29 B, the driving gear  27 B rotates clockwise under the driving of the transmission gear  29 B, and the driven gear  28 C rotates counterclockwise under the driving of the driving gear  27 B. Since the driven gear  28 C is fixed to the semi reeling wheel axle  16 , under the action of the driven gear  28 C, the semi reeling wheel axle  16  rotates counterclockwise. During the counterclockwise rotation of the semi reeling wheel axle  16 , due to the axial bias of the compression spring  19  to the first clutch half  20  and the camming actions of the recesses  58  of the control member  21  on the one-way cogs  55  of the first clutch half  20 , the first clutch half  20  moves axially away from the second clutch half  18  until the one-way cogs  55  of the first clutch half  20  entirely falls into the recesses  58  of the control member  21 , whereby the clutch  47  is in the disengaged state. 
     Fourth Embodiment 
     See  FIGS. 25-27  which show a hose reeler according to the forth embodiment of the invention. This embodiment is substantially the same as the first embodiment of the invention with the difference lying in that a coil spring as in the first embodiment is not used and a single axle is employed here as a reeling wheel axle to replace the combination of the principal reeling wheel axle and the semi reeling wheel axle in the first embodiment. Therefore, only the portion different from the first embodiment will be described, and the remainders can refer to the first embodiment. 
     In this embodiment, since no coil spring is used in the reeling wheel assembly  46 C, the reeling wheel axle  15 B can be a single axle. An axial hole  42 B is provided at one end of a stationary axle  4  proximate to the reeling wheel axle  15 B, and movably fits with a circumferential surface  40 B of the reeling wheel axle  15 B. A circumferential surface  48 B of the reeling wheel axle  15 B is fit to a central through hole  38  of the left disk  17 . There are four shaped keys  57  in a shape of            on the circumferential surface  48 B of the reeling wheel axle  15 B that can fit with the shaped grooves  56  of the first clutch half  20 .
     When the hose is pulled out, the lever  34  is in the start position and the clutch  47  is in the disengaged state. At this time the reeling wheel axle  15 B remains stationary and the reeling wheel rotates counterclockwise about the reeling wheel axle  15 B. 
     When the treadle  35  is being pressed down, the lever  34  drives the internal sector gear  30  to rotate counterclockwise. Under the action of the internal sector gear  30 , the transmission gear  29  rotates counterclockwise. Since the driving gear  27  and the transmission gear  29  are fixed coaxially, the driving gear  27  rotates counterclockwise under the driving of the transmission gear  29 . Acted by the driving gear  27 , the driven gear  28  rotates clockwise. Since the driven gear  28  is fixed to the reeling wheel axle  15 B, the reeling wheel axle  15 B rotates clockwise under the action of the driven gear  28 . The rotation of the reeling wheel axle  15 B causes the first clutch half  20  to rotate clockwise. Since at this time the one-way cogs  55  of the first clutch half  20  are engaged with the recesses  58  of the control member  21  and the detent  22  damps down the rotation of the control member  21 , the movement of the first clutch half  20  lags behind the movement of the semi reeling wheel axle  16 . Under the camming actions between the slopes of the shaped keys  57  of the reeling wheel axle  15 B and the slopes of the shaped grooves  56  of the first clutch half  20 , the one-way cogs  55  of the first clutch half  20  slide out of the recesses  58  of the control member  21 , and the first clutch half moves toward the second clutch half  18 , resulting in the engagement of the teeth  51  of the first clutch half  20  with the teeth  52  of the second clutch half  18 . Therefore, the first clutch half and the second clutch half are engaged with each other axially. Then the first clutch half  20  drives the second clutch half  18  to rotate clockwise, and in turn, drives the reeling wheel to rotate clockwise. Thus, the retraction of the hose is achieved. At this time, the tension spring  31  is in tension. 
     Once the clockwise rotation speed of the reeling wheel is higher than that of the reeling wheel axle  15 B due to the action of the inertia during the retraction of the hose, there will be a relative rotation between the reeling wheel and the reeling wheel axle  15 B. Since the first clutch half  20  rotates clockwise as the reeling wheel rotates, that means there is a relative rotation between the reeling wheel axle  15  B and first clutch half  20 . When the shaped key  57  of the reeling wheel axle  15 B slides along the slope of the shaped groove  56  to the opening  59  of the shaped groove  60  (i.e., a portion without slope) as the reeling wheel axle  15 B rotates, the first clutch half  20  moves axially away from the second clutch half  18  under the action of the compression spring  19 , and therefore the clutch is in the disengaged state. In this way, the reeling wheel is allowed to rotate in a speed higher than that of the reeling wheel axle  15 B. 
     When the treadle  35  is released, the lever  34  drives the internal sector gear  30  to rotate clockwise under the action of the tension spring  31 , and the transmission gear  29  rotates clockwise under the action of the internal sector gear. Since the driving gear  27  is coaxially fixed to the transmission gear  29 , the driving gear  27  rotates clockwise under the driving of the transmission gear  29 , and the driven gear  28  rotates counterclockwise under the action of the driving gear  27 . Since the driven gear  28  is fixed to the reeling wheel axle  15 B, under the action of the driven gear  28 , the reeling wheel axle  15 B rotates counterclockwise. During the counterclockwise rotation of the reeling wheel axle  15 B, due to the axial bias of the compression spring  19  to the first clutch half  20  and the camming action of the recesses  58  of the control member  21  on the one-way cogs  55  of the first clutch half  20 , the first clutch half  20  moves axially away from the second clutch half  18  until the one-way cogs  56  of the first clutch half  20  entirely fall into the recesses  58  of the control member  21 , and therefore the clutch  47  is in the disengaged state. 
     Fifth Embodiment 
     See  FIGS. 28-30  which show a hose reeler according to the fifth embodiment of the invention. This embodiment is substantially the same as the second embodiment of the invention with the difference only lying in that the coil spring in the second embodiment is not used and a single axle is employed here as a reeling wheel axle to replace the combination of the principal reeling wheel axle and the semi reeling wheel axle in the second embodiment. Therefore, only the portion different from the first embodiment will be described, and the remainder can refer to the second embodiment. 
     In this embodiment, since no coil spring is used in the reeling wheel assembly  46 C, the reeling wheel axle  15 C can be a single axle. There is an axial hole  42 B at one end of a stationary axle  4  proximate to the reeling wheel axle  15 C. The axial hole  42 B can movably fit with a circumferential surface  40 C of the reeling wheel axle  15 C which in turn is fit to a central through hole  38  in the left disk  17  of the reeling wheel. There is a length of external thread  65  on a side of reeling wheel axle  15 C proximate to the left disk  17 . 
     When the hose is pulled out, the lever  34  is in the start position and the one-way teeth  63  on the driven gear  28 B and the one-way teeth  61  on the transmission connector  18 B are disengaged, and the clutch  47 B is in the disengaged state. At this time, the reeling wheel axle  15 C remains stationary, and the reeling wheel rotates counterclockwise about the reeling wheel axle  15 C. 
     When the treadle  35  is being pressed down, the lever  34  drives the internal sector gear  30  to rotate counterclockwise, and the transmission gear  29  rotates counterclockwise under the driving of the internal sector gear  30 . Since the driving gear  27  and the transmission gear  29  are fixed coaxially, the driving gear  27  rotates counterclockwise under the driving of the transmission gear  29 . Acted by the driving gear  27 , the driven gear  28 B rotates clockwise. Since the driven gear  28 B is fit with the reeling wheel axle  15 C by means of threads, the clockwise rotation of the driven gear  28 B causes the reeling wheel axle  15 C to rotate clockwise therewith. However, due to the damping action of the detent  22  on the wave wheel  21 B, the rotation of the reeling wheel axle  15 C lags behind the rotation of the driven gear  28 B. In this case, the driven gear  28 B moves toward the transmission connector  18 B via screwing action, until the one-way teeth  63  on the driven gear  28 B mesh with the one-way teeth  61  on the transmission connector  18 B, and the transmission connector  18 B rotates clockwise under the action of driven gear  28 B thereby to drive the reeling wheel, which is fixed to the transmission connector, to rotate clockwise. Therefore the hose is retracted. At this time, the tension spring  31  is in tension. 
     During the retraction of the hose, once the clockwise rotation speed of the reeling wheel is higher than that of the reeling wheel axle  15 C due to the action of inertia (i.e., there is a relative rotation between the transmission connector  18 B and the driven gear  28 B, and the movement of the driven gear  28 B lags behind that of the transmission connector  18 B), the reeling wheel axle  15 C remains stationary relative to the driven gear  28 B due to the damping action of the detent  22  on the wave wheel  21 B. The one-way teeth  63  of the driven gear  28 B escape from the one-way teeth  61  of the transmission connector  18 B under the action of the one-way teeth  61  of the transmission connector  18 B and the compression spring  19 B, and the transmission gear  28 B moves away from the transmission connector  18 B until the one-way teeth  63  of the driven gear  28 B is disengaged from the one-way teeth  61  of the transmission connector  18 B. In this way, the reeling wheel is allowed to rotate in a speed higher than that of the reeling wheel axle  15 C. 
     When the treadle  35  is released, the lever  34  drives the internal sector gear  30  to rotate clockwise under the action of the tension spring  31 , and the transmission gear  29  rotates clockwise under the action of the internal sector gear  30 . Since the driving gear  27  is coaxially fixed to the transmission gear  29 , the driving gear  27  rotates clockwise under the driving of the transmission gear  29 , and the driven gear  28 B rotates counterclockwise under the action of the driving gear  27 . Due to the damping action of the detent  22  on the wave wheel  21 B, the reeling wheel axle  15 C remains stationary relative to the driven gear  28 B. Then the one-way teeth  63  of the driven gear  28 B escape from the one-way teeth  61  of transmission connector  18 B and the driven gear  28 B move away from transmission connector  18 B. Therefore, the driven gear  28 B is in idle running about the axis of the reeling wheel axle  15 C. 
       FIG. 31  shows an optional modification of the internal sector gear and the lever of the reeling wheel drive shown in  FIG. 1  in accordance with the present invention. In this modification, the internal sector gear  30 ′ and the lever  34 ′ are at the same side of the pivot P (corresponding to the axis of the secondary axle  26  in  FIG. 1 ). Swinging about the pivot P, the lever  34 ′ drives the internal sector gear  30 ′ to swing, and therefore the transmission gear  29  which internally meshes with the internal sector gear  30 ′ is driven. This modification is helpful in reducing the size of the lever-internal sector gear assembly. 
       FIG. 32  shows a modification of the control mechanism of the overrunning clutch shown in  FIG. 1  and  FIG. 8  in accordance with the present invention.  FIG. 32(   a ) is a perspective view of a control member of the mechanism and  FIG. 32(   b ) is a schematic diagram which shows the assembly of the control member. In the modification, the control member is a belt pulley  21 ′ having a belt winding portion  211 ′ on its circumference and a belt  22 ′ winding around the belt winding portion  211 ′. Opposite ends of the belt  22 ′ are fixed to a stationary portion (for example, the left housing  24 ) with one end tensioned by a spring  23 ′ at a predetermined tension force. That is to say, the control member  21 , the detent  22  and the spring  23  constituting the control mechanism of the first embodiment of the invention are replaced by a control member in the form of a belt pulley  21 ′, a belt  22 ′ and a spring  23 ′, with the semi reeling wheel axle  16  unchanged. Except the belt winding portion  211 ′, the structures of the control member  21 ′ are substantially the same as the control member  21  in the first embodiment. When the belt pulley  21 ′ rotates in one direction (the counterclockwise direction in  FIG. 32(   b )), the spring  23 ′ is tensioned, and therefore the damping force applied by belt  22 ′ to the belt pulley  21 ′ is increased and the rotation of the belt pulley is damped down. This shows that the function of the above pulley-belt arrangement is substantially the same as that of the wave wheel-detent arrangement in the first embodiment of the invention, i.e., both to damp down the rotation of the control member. 
     A detailed description has been given to the various embodiments of the invention in the above. It is understood that the invention is not limited to these exemplary embodiments. Those skilled in the art can make varieties of equivalent modifications and changes to the above embodiments within the present inventive concept. For example, although in the embodiments described herein the lever in the reeling wheel drive is a foot-treading type, a hand pulling or other appropriate types can be adopted. Although in the described embodiments an automatic overrunning clutch is used, a manually operated or other appropriate clutches can be used, e.g., a manually operated clutch (such a manual-type clutch is well known) comprising first and second clutch halves that can be engaged with or disengaged from each other axially and a manually operated mechanism that is connected with one of the first and second clutch halves and extends out of a housing of a hose/cable reeler for manipulation by an operator to control the engagement and disengagement between the halves. Although in the described embodiments the transmission member in the reeling wheel drive is a gear rack or an internal sector gear, an external gear or other appropriate forms can be employed. Although in the described embodiments the rotation damping mechanism comprises a wave wheel-detent or a pulley-belt arrangement, any other known appropriate structures which can damp down the rotation can be used. Therefore, the scope of the invention should not limited to the described embodiments and is intended to be defined by the appended claims.