JP2021095083A - Bicycle parking machine - Google Patents

Abstract

To provide a bicycle parking machine which can achieve an increase in durability of an actual vehicle lifting and lowering driving gas spring, and consequently the entire bicycle parking machine without impairing a cost reduction effect accompanying introduction of the gas spring that is an actual vehicle lifting and lowering driving actuator and an effect of improving safety accompanying support post internal arrangement of the gas spring as an actual vehicle lifting and lowering driving part and a winding transmission mechanism.SOLUTION: One end of a wire rope 25 is connected to a base end part side of a cylinder 21S of a lifting and lowering gas spring 21 relative to a moving pulley group 23 comprising one or more moving pulleys 23B, 23D and a fixed pulley group 24 comprising two or more fixed pulleys 24A, 24C, is wound around the moving pulley 23D with a minimum diameter, the fixed pulley 24C, and the moving pulley 23B in this order so that a pulley diameter becomes larger in a winding order, and is finally wound around the fixed pulley 24A with a maximum diameter. In this case, the hanging number of the wire ropes 25 relative to the moving pulley group 23 is three or more, and an actual vehicle driving stroke SM is lower than 1/2 of rack stroke SR.SELECTED DRAWING: Figure 4

Description

The present invention relates to a bicycle parking machine.

In a bicycle parking machine having a vertical vertical lift type rack, a bicycle is carried into the rack at the lower position of the support column, and the rack in the actual vehicle state is stored and managed at the upper position. In Patent Document 1, the actual vehicle elevating drive unit for elevating and lowering the rack in the actual vehicle state includes a double-acting air cylinder as an actuator for elevating and lowering the actual vehicle, an air supply device including a switching valve, a pressure accumulator tank, and a pressure booster. It has a wrapping transmission mechanism including a pulley, a fixed pulley and a lifting rope, and at least an air cylinder and a wrapping transmission mechanism are arranged outside the column. Specifically, a moving pulley is connected to the tip of the piston rod of the air cylinder, one end of the elevating rope is fixed to a support, the middle part is wound around the moving pulley and the fixed pulley, and then the other end. Is fixed to the lift that supports the rack. As a result, the piston stroke (for example, 0.6 m) of the air cylinder on the driving side is shortened to 1/2 of the rack stroke (for example, 1.2 m) on the operating side.

On the other hand, in Patent Documents 2 and 3, as an actuator for raising and lowering an actual vehicle instead of a double-acting air cylinder, the push output of the piston when the gas sealed in the cylinder passes through the piston and moves from the rod side to the head side. A protruding gas spring is used as a drive source, and the cost is reduced by greatly simplifying the peripheral configuration. Further, the safety of the operator and the actual vehicle elevating drive unit is improved by arranging the entire actual vehicle elevating drive unit (that is, the gas spring and the winding transmission mechanism) inside the column.

By the way, in general, the main use of a gas spring is to support a light load (for example, to support the opening and closing of a hatchback door of an automobile), and it is used with a relatively short piston stroke (for example, within 0.3 m). On the other hand, as in Patent Documents 2 and 3, the gas spring acts as an actuator for driving the actual vehicle up and down of the bicycle parking machine, and is relatively long under the heavy load (for example, 20 to 40 kg) of the rack in the actual vehicle state. When used frequently and for a long period of time with a piston stroke (for example, 0.6 m or more), an O-ring is used to further improve durability, especially to maintain high airtightness and oiltightness of the piston. It is required to extend the life of sealing members such as oil seals.

At that time, by using a plurality of high-quality sealing members (multiple structure), it is possible to contribute to extending the life of the sealing member and improving the durability of the gas spring, but the effect of introducing the gas spring instead of the air cylinder (cost reduction) is lost. There is a risk of being damaged (offset). In addition, the durability of the gas spring can be improved by changing the design of the gas spring (for example, increasing the diameter and length of the cylinder), but safety is achieved because all or part of the actual vehicle elevating drive unit cannot be arranged inside the column. May be hindered.

JP-A-2007-138680 Japanese Unexamined Patent Publication No. 2018-039493 Japanese Patent No. 6598340

An object of the present invention is to impair the cost reduction effect associated with the introduction of the gas spring, which is an actuator for raising and lowering the actual vehicle, and the safety improving effect associated with the arrangement of the gas spring as the actual vehicle raising and lowering drive unit and the internal support of the winding transmission mechanism. The purpose is to provide a bicycle parking machine that can improve the durability of the entire bicycle parking machine by using a gas spring for driving the actual vehicle up and down.

Means for Solving Problems and Effects of Invention

In order to solve the above problems, the bicycle parking machine of the present invention
A first drive unit (for example, an empty vehicle elevating drive unit) for raising and lowering an empty rack without a bicycle in a horizontal posture along a column erected in a tubular shape in the vertical direction, and an actual vehicle equipped with a bicycle. A bicycle parking machine including a second drive unit (for example, an actual vehicle elevating drive unit) for raising and lowering the rack in a state in a horizontal posture along the support column.
The second drive unit is connected to the tip end portion of a piston rod that projects downward from the cylinder of the actual vehicle lifting / lowering drive gas spring to which the base end portion is attached inside above the column and exerts a traction force, and one or more movements. A group of moving pulleys composed of pulleys, a group of fixed pulleys composed of two or more fixed pulleys fixed inside the support column at a position higher than the cylinder, the moving pulley group and all the pulleys constituting the fixed pulley group. Has a winding transmission mechanism that includes a single wire rope that is wound once in a row.
One end of the wire rope is connected to the tip end side of the piston rod or the base end side of the cylinder, and the minimum diameter fixed pulley or the tip of the piston rod attached to the base end side of the cylinder. Starting from the minimum diameter moving pulley attached to the part side, the moving pulley arranged on the tip side of the piston rod so that the pulley diameter increases in the winding order and the fixed pulley arranged on the base end side of the cylinder. It continues in the form of being wound alternately with and, and finally passes through the hanging part leading to the fixed pulley with the maximum diameter attached to the base end side of the cylinder, and the other end (for example, the actual vehicle elevating trolley). Connected to the rack (via)
By winding the wire rope so that the number of suspended wire ropes with respect to the moving pulley group is 3 or more, the movement range of the connection point between the piston rod and the moving pulley group is shown as the movement range of the connection point between the piston rod and the moving pulley group according to the advancement and retreat of the piston rod. The actual vehicle drive stroke (equal to the piston stroke) is less than 1/2 of the rack stroke represented as the movement range of the lower end of the rack elevating and lowering operation unit including the rack in the actual vehicle state.

Further, in order to solve the above problems, the bicycle parking machine of the present invention is used.
A first drive unit (for example, an empty vehicle) for swinging an empty rack without a bicycle between a horizontal posture at the lower part of a support column erected in a tubular shape in the vertical direction and an inverted posture along the support column. A bicycle parking machine including a rocking drive unit) and a second drive unit (for example, an actual vehicle elevating drive unit) for raising and lowering a rack in an actual vehicle state on which a bicycle is mounted in a horizontal posture along the support column.
The second drive unit is connected to the tip end portion of a piston rod that projects downward from the cylinder of the actual vehicle lifting / lowering drive gas spring to which the base end portion is attached inside above the column and exerts a traction force, and one or more movements. A group of moving pulleys composed of pulleys, a group of fixed pulleys composed of two or more fixed pulleys fixed inside the support column at a position higher than the cylinder, the moving pulley group and all the pulleys constituting the fixed pulley group. Has a winding transmission mechanism that includes a single wire rope that is wound once in a row.
One end of the wire rope is connected to the tip end side of the piston rod or the base end side of the cylinder, and the minimum diameter fixed pulley or the tip of the piston rod attached to the base end side of the cylinder. Starting from the minimum diameter moving pulley attached to the part side, the moving pulley arranged on the tip side of the piston rod so that the pulley diameter increases in the winding order and the fixed pulley arranged on the base end side of the cylinder. It continues in the form of being wound alternately with and, and finally passes through the hanging part leading to the fixed pulley with the maximum diameter attached to the base end side of the cylinder, and the other end (for example, via an elevating trolley). ) Connected to the rack
By winding the wire rope so that the number of suspended wire ropes with respect to the moving pulley group is 3 or more, the movement range of the connection point between the piston rod and the moving pulley group is shown as the movement range of the connection point between the piston rod and the moving pulley group according to the advancement and retreat of the piston rod. The actual vehicle drive stroke (equal to the piston stroke) is less than 1/2 of the rack stroke represented as the movement range of the lower end of the rack elevating and lowering operation unit including the rack in the actual vehicle state.

In this way, regardless of whether the rack is stored horizontally or inverted, the wires are attached to the moving pulley group and the fixed pulley group arranged so that the pulley diameter increases in the winding order. By winding the rope, the actual vehicle drive stroke (piston stroke) becomes less than half of the rack stroke. That is, the moving distance of the sealing member (for example, the O-ring) in the cylinder is shorter than that of the case where the moving pulley and the fixed pulley are each one (corresponding to 1/2 of the rack stroke at this time). Minutes are accumulated by repeated reciprocating movements, and the life of the sealing member is extended, and the durability of the gas spring for raising and lowering the actual vehicle and the bicycle parking machine is improved.

Moreover, at this time, since it is not necessary to replace the sealing member with a high-quality one or to use a plurality of sealing members, the cost reduction effect due to the introduction of the gas spring is not hindered. In addition, since it is not necessary to replace the gas spring for raising and lowering the actual vehicle with a large product or changing the arrangement position, the effect of improving safety by arranging the gas spring for raising and lowering the actual vehicle and the support of the winding transmission mechanism inside the column is hindered. There is no such thing.

As described above, the "actual vehicle drive stroke" is equal to the "piston stroke of the actual vehicle elevating drive gas spring" and is also synonymous with the "moving distance of the sealing member (for example, O-ring) in the cylinder". In addition, regarding "moving pulleys and fixed pulleys that are alternately wound so that the pulley diameter increases in the winding order", the same diameter is used for any two (one set) pulleys in which the winding order is continuous. Shall include.

As a specific example, for a moving pulley group consisting of two moving pulleys and a fixed pulley group consisting of two fixed pulleys, one end of a wire rope is connected to the base end side of the cylinder and a piston rod. Starting from the minimum diameter moving pulley attached to the tip side of the pulley, the fixed pulley arranged on the base end side of the cylinder and the moving pulley arranged on the tip side of the piston rod so that the pulley diameter increases in the winding order. When the pulleys are wound alternately with the pulleys and finally reach the fixed pulley with the maximum diameter attached to the base end side of the cylinder, the number of wire ropes suspended from the moving pulleys is 4, and the actual vehicle The drive stroke (ie, piston stroke) is less than 1/2 of the rack stroke (eg, about 1/3).

As another example, for a moving pulley group consisting of one moving pulley and a fixed pulley group consisting of two fixed pulleys, one end of the wire rope is connected to the tip end side of the piston rod and the base of the cylinder. Starting from the smallest fixed pulley attached to the end side, the moving pulley arranged on the tip side of the piston rod so that the pulley diameter increases in the winding order and the fixed pulley arranged on the base end side of the cylinder. If the last wound fixed pulley corresponds to the maximum diameter fixed pulley attached to the base end side of the cylinder, the wire rope for the moving pulley group. The number of suspensions is 3, and the actual vehicle drive stroke (that is, the piston stroke) is less than 1/2 of the rack stroke (for example, about 1 / 2.5).

As yet another example, for a group of moving pulleys consisting of two moving pulleys and a group of fixed pulleys consisting of three fixed pulleys, one end of the wire rope is connected to the tip end side of the piston rod, and the cylinder Starting from the smallest fixed pulley attached to the base end side, the moving pulley placed on the tip side of the piston rod and the fixed pulley placed on the base end side of the cylinder so that the pulley diameter increases in the winding order. Wires to the moving pulley group if they continue to be wound alternately with the pulleys and as a result the last wound pulley corresponds to the largest diameter pulley mounted on the proximal end side of the cylinder. The number of suspended ropes is 5, and the actual vehicle drive stroke (that is, the piston stroke) is less than 1/2 of the rack stroke (for example, about 1 / 3.5).

By the way, in a bicycle parking machine having a vertical vertical lift type rack, in the type in which the rack in an empty vehicle state is horizontally stored, the first drive unit functions as an empty vehicle lift drive unit, and a constant load spring for lift drive as an actuator for lift and lower drive of an empty vehicle. A gas spring or the like for driving an empty vehicle up and down is used. On the other hand, in the type in which the rack in the empty vehicle state is stored upside down, the first drive unit functions as an empty vehicle rocking drive unit, and a constant load spring for rocking drive, a gas spring for rocking vehicle rocking, etc. are used as actuators for rocking the empty vehicle. Used.

When an empty vehicle elevating drive gas spring or an empty vehicle rocking drive gas spring is used in the first drive unit, the rack in the empty vehicle state has a light load (for example, 5 to 7 kg weight). The degree of demand for improved durability (that is, longer life of the sealing member) is much lower than that of the gas spring for raising and lowering the actual vehicle.

Next, each pulley constituting the moving pulley group and the fixed pulley group (for example, when viewed from the width direction of the rack) was arranged horizontally in a state parallel to each other along the advancing / retreating direction of the piston rod. It is held individually for multiple central axes.

As a result, the second drive unit (gas spring for raising and lowering the actual vehicle and the winding transmission mechanism) can be housed in a small and compact space in the limited space inside the support of the bicycle parking machine, so that the safety of the operator and the second drive unit can be accommodated. The second drive unit operates smoothly, and vibration and noise are less likely to occur.

Further, the cylinder outer diameter of the gas spring for raising and lowering the actual vehicle is smaller than the pulley diameters of all the pulleys constituting the moving pulley group and the fixed pulley group, and the maximum diameter fixed pulley is the minimum diameter fixed pulley or the minimum diameter moving pulley. It has a pulley diameter 1.5 to 2.0 times that of a pulley.

As a result, it is possible to prevent damage or performance deterioration of the wire ropes due to contact between the wire ropes or between the wire ropes and the gas spring for driving the actual vehicle up / down in a narrow vertically long space inside the support column. In the case of a sheave in which the pulley has a groove for holding the wire rope, the "pulley diameter" corresponds to both the nominal diameter and the effective diameter.

Here, it is desirable that the pulley diameter of the fixed pulley having the minimum diameter or the moving pulley having the minimum diameter exceeds 10 times the diameter of the wire rope. As a result, the kink phenomenon is less likely to occur in the wire rope, the operation of the second drive unit becomes smoother, and it is less likely to be a source of vibration / noise.

When the total height of the columns is equally divided into three areas, upper, middle and lower, the rack stroke is located across both the middle and lower areas, and the actual vehicle drive stroke is located only in the middle area. be able to.

As a result, the cylinder of the gas spring for lifting and lowering the actual vehicle is firmly placed in the upper area inside the column because the actual vehicle drive stroke is within the middle stage area while sufficiently securing the upper storage space for the bicycle and the space for raising and lowering the stored bicycle. It is fixed and the piston rod and the moving pulley group can move back and forth stably around the middle area. The rack stroke may partially extend to the upper area.

Alternatively, when the rack stroke is bisected into an upper area and a lower area, the actual vehicle drive stroke is located only in the upper area.

As a result, the actual vehicle drive stroke is less than half of the rack stroke and is located in the upper half area of the rack stroke, so that the cylinder of the actual vehicle elevating drive gas spring is firmly fixed to the inner upper region of the column. Then, the piston rod and the moving pulley group can move back and forth stably around the upper half area of the rack stroke.

FIG. 5 is a side view simply showing a state in which an empty rack is in the upper position in the bicycle parking machine according to the first embodiment. FIG. 5 is a side view simply showing a state in which an empty rack is in the lower position in the bicycle parking machine of FIG. FIG. 5 is a side view simply showing a state in which the rack in the actual vehicle state is in the lower position in the bicycle parking machine of FIG. FIG. 5 is a side view simply showing a state in which the rack in the actual vehicle state is in the upper position in the bicycle parking machine of FIG. FIG. 5 is a side view showing a retracted state (a) and an extended state (b) of the piston rod of the gas spring in the winding transmission mechanism of the bicycle parking machine of FIG. FIG. 5 is a perspective view showing a state in which one of the facing plates is removed in the winding transmission mechanism of FIG. FIG. 5 is a cross-sectional view simply showing a horizontal cross section of a support column of the bicycle parking machine of FIG. The figure which showed the internal structure of a gas spring simply. The side view which showed the inverted storage state of the rack in an empty state simply in the bicycle parking machine which is 2nd Example. FIG. 9 is a side view simply showing a state in which an empty rack is in the lower position in the bicycle parking machine of FIG. FIG. 9 is a side view simply showing a state in which the rack in the actual vehicle state is in the lower position in the bicycle parking machine of FIG. FIG. 9 is a side view simply showing a state in which the rack in the actual vehicle state is in the upper position in the bicycle parking machine of FIG. The front view which showed the bicycle parking machine which is 3rd Example simply. The side view which showed the retracted state (a) and the extended state (b) of the piston rod of a gas spring in the winding transmission mechanism used for the bicycle parking machine which is a 1st modification. The side view which showed the retracted state (a) and the extended state (b) of the piston rod of a gas spring in the winding transmission mechanism used for the bicycle parking machine which is a 2nd modification.

Hereinafter, the first embodiment of the present invention will be described with reference to the drawings.

In the bicycle parking machine 100 shown in FIGS. 1 to 4, the left-right direction of each figure is the front-rear direction of the bicycle parking machine 100 (left is the front, the right is the back), and the depth direction of each figure is the width direction of the bicycle parking machine 100. The vertical direction of each figure shall be defined as the vertical direction of the bicycle parking machine 100.

As shown in FIGS. 1 to 4, the bicycle parking machine 100 of the first embodiment includes a vertically elevating rack 13 for mounting a bicycle BCL (see FIGS. 3 and 4). The rack 13 has a gutter-shaped elongated shape extending in a cantilever shape in the front-rear direction (front-back direction) when the bicycle BCL is mounted and disembarked, and the bicycle BCL is carried in and out at the tip (rear end: right end in the figure). An entrance / exit 15 for the bicycle is formed. A pair of braces 14 (side guards) for preventing the mounted bicycle BCL from rolling over are arranged on both sides of the rack 13 in the width direction. Further, the rack 13 is provided with a tire guard 16 on the front side for holding the preceding carry-in wheels (front wheels FW in FIGS. 3 and 4) of the mounted bicycle BCL.

Further, in the bicycle parking machine 100 of the first embodiment, as shown in FIGS. 1 to 4, an empty rack 13 on which the bicycle BCL (see FIGS. 3 and 4) is not mounted is erected in a tubular shape in the vertical direction. The first drive unit 10 (empty vehicle elevating drive unit) for ascending and descending in a horizontal posture along the support column 1 and the rack 13 in an actual vehicle state on which the bicycle BCL is mounted are used for ascending and descending in a horizontal position along the support column 1. A second drive unit 20 (actual vehicle elevating drive unit) is provided.

The first drive unit 10 raises and lowers the first elevating carriage 12 (also referred to as the first elevating unit: hereinafter abbreviated as the upper carriage 12) by the first urging member 11 forming the actuator for raising and lowering the empty vehicle. Here, the first drive unit 10 includes an upper carriage 12 on which the rack 13 on which the bicycle BCL can be mounted can be raised and lowered along the support column 1, and a rack 13 in an empty state (a rack accessory such as a brace 14) on which the bicycle BCL is not mounted. The first urging member 11 has a function of pulling the total load of (including), and the upper carriage 12 is urged by the first urging member 11 so as to be constantly pulled upward.

The rack 13 and the brace 14 are integrally assembled to the upper carriage 12, and the upper carriage 12 moves up and down along the guide rail 34 shown in FIG. 7. Here, the upper carriage 12 is assembled with a roller 4 that rolls on a guide rail 34 extending in the vertical direction provided on the rear side surface of the support column 1. The rollers 4 here form a pair on both outer sides in the width direction of the support column 1, and the pair of rollers 4 and 4 are rotatably assembled to the main body of the upper carriage 12 in a form in which two pairs of rollers 4 and 4 are arranged in the vertical direction. There is.

Here, the first urging member 11 employs a constant load spring for lifting and lowering an empty vehicle (hereinafter, abbreviated as the constant load spring 11). An opening is provided in the upper part of the support column 1, and a cover 101 is attached so as to cover the opening. The constant load spring 11 is fixed to the support column 1 in a form in which a drum is arranged inside the cover 101. ing.

The second drive unit 20 raises and lowers the second elevating carriage 22 (also referred to as the second elevating unit: hereinafter abbreviated as the lower carriage 22) by the second urging member 21 forming the actuator for driving the actual vehicle. The second drive unit 20 here has a function of towing the total load of the lower bogie 22 that can be integrally raised and lowered with the upper bogie 12 along the support column 1 and the bicycle BCL mounted on the rack 13 in the actual vehicle state. The lower carriage 22 is urged by the second urging member 21 so as to be constantly pulled upward.

The lower carriage 22 is arranged below the upper carriage 12, and like the upper carriage 12, moves up and down along the guide rail 34 shown in FIG. 7. The lower carriage 22 here is assembled with a roller 5 that rolls on the guide rail 34. The rollers 5 here form a pair on both outer sides in the width direction of the support column 1, and the pair of rollers 5 and 5 are rotatably assembled to the main body of the lower carriage 22 in a form in which two pairs of rollers 5 and 5 are arranged in the vertical direction. There is.

The second urging member 21 employs an actual vehicle elevating drive gas spring (hereinafter, abbreviated as elevating gas spring 21). The lower carriage 22 is in a predetermined lower position when the piston rod 21R is retracted (contracted) as shown in FIG. 5 (a) (see FIGS. 1 to 3), and the lower carriage 22 is located on the piston rod 21R as shown in FIG. 5 (b). It rises to a predetermined upper position due to protrusion (extension) (see FIG. 4).

The elevating gas spring 21 is arranged inside the support column 1, and as shown in FIG. 8, the piston rod 21R always has a push output F (also referred to as a gas reaction force) in the extension direction within a predetermined stroke range. The elevating gas spring 21 includes a cylinder 21S in which a working fluid (inert compressed gas: for example, nitrogen gas) is sealed, a piston 21P that is inserted into the cylinder 21S and divides the inside of the cylinder 21S into two chambers 201 and 202, and a rear. It has a piston rod 21R whose end is connected to the piston 21P and whose front end projects outward from the front end of the cylinder 21S. The piston 21P is provided with an orifice 21F for circulating a working fluid between the two chambers 201 and 202 inside the cylinder 21S as the piston rod 21R moves. Further, an O-ring 21Q1 is provided as a sealing member for sealing between the outer peripheral surface of the piston 21P and the inner wall surface 21s of the cylinder 21S, and further, the inner peripheral surface of the piston rod projecting opening 21H and the piston rod 21R An O-ring 21Q2 and an oil seal 21Q3 are provided as sealing members for sealing the space. As the piston rod 21R advances and retreats, the O-ring 21Q1 slides on the inner wall surface 21s of the cylinder 21S, and the O-ring 21Q2 and the oil seal 21Q3 slide on the outer peripheral surface of the piston rod 21R.

Next, the winding transmission mechanism 26 will be described.

The second drive unit 20 has a winding transmission mechanism 26. As shown in FIGS. 5 and 6, the winding transmission mechanism 26 has a moving pulley group 23, a fixed pulley group 24, and a wire rope 25 in order to apply the urging force of the elevating gas spring 21 to the lower carriage 22. And, including.

The moving pulley group 23 is composed of one or more moving pulleys 23B and 23D (here, 2), and projects downward from the cylinder 21S of the elevating gas spring 21 to which the base end is attached inside the support column 1 to exert a traction force. It is connected to the tip of the piston rod 21R that exerts. The moving pulley group 23 here has a moving pulley 23D attached to the tip end side of the piston rod 21R and a moving pulley 23B attached to the lower side thereof, and the moving pulleys 23B and 23D are in the vertical direction. It is fixed to the pulley fixing member 230 in a positional relationship separated by a certain distance.

The fixed pulley group 24 is composed of two or more fixed pulleys 24A and 24C (here, 2), and is fixed to the inside of the support column 1 at a position higher than the cylinder 21S. The fixed pulley group 24 here includes a fixed pulley 24A attached to the base end side of the cylinder 21S and a fixed pulley 24C attached to the lower side thereof, and the fixed pulleys 24A and 24C, respectively. Is fixed to the pulley fixing member 240 in a positional relationship separated by a certain distance in the vertical direction.

Each pulley 24A, 23B, 24C, 23D is an independent pulley. When viewed from the width direction of the rack 13, each pulley 24A, 23B, 24C, 23D corresponds to a plurality of central axes 231 and 241 arranged in the horizontal direction in a state parallel to each other along the advancing / retreating direction of the piston rod 21R. They are individually held and are rotatable around their respective central axes 231 and 241 (rotating axes P23 and P24).

In the case of a sheave in which the pulley has a groove for holding the wire rope, the "pulley diameter" corresponds to both the nominal diameter and the effective diameter. All the pulleys 24A, 23B, 24C and 23D constituting the moving pulley group 23 and the fixed pulley group 24 here are sheaves. Further, the pulley diameters a, b, c and d of the pulleys 24A, 23B, 24C and 23D exceed the outer diameter s of the cylinder 21S of the elevating gas spring 21, and the pulley 24A having the maximum diameter a has the minimum diameter d. It has a pulley diameter 1.5 to 2.0 times that of the pulley 23D. Further, the pulleys 23B and 24C are pulleys having the same shape, and their pulley diameters b and c are the same as each other, smaller than the fixed pulley 24A and larger than the moving pulley 23D. For the pulley with the minimum diameter d (here, the moving pulley 23D), the pulley diameter is more than 10 times the wire rope diameter, and the kink phenomenon is less likely to occur.

The pulley fixing members 230 and 240 penetrate the facing plates 232 and 242 and the facing plates 232 and 242, which are fixed to each other by fastening members such as bolts and nuts so as to face each other in the axial direction of the corresponding central shafts 231 and 241. It has central axes 231 and 241.

The pulleys 23B and 23D constituting the moving pulley group 23 are rotatably assembled with respect to the central shaft 231 so as to be sandwiched between the opposing plates 232. Further, a roller 3 that rolls on a guide rail 33 (see FIG. 7) extending in the vertical direction provided inside the support column 1 is assembled to the facing plate 232. Here, the rollers 3 form a pair on both outer sides of the facing plate 232, and the pair of rollers 3 and 3 are rotatably assembled as wheels of the facing plate 232 in a form in which two pairs of rollers 3 and 3 are arranged in the vertical direction. Here, the elevating portion 2 in the column, which has the moving pulley group 23, the pulley fixing member 230, and the roller 3, is guided by the guide rail 33 and moves up and down in the internal space 1S of the column 1 in a tubular shape. It is formed.

The pulleys 24A and 24C constituting the fixed pulley group 24 are rotatably assembled with respect to the central shaft 241 so as to be sandwiched between the opposing plates 242. The facing plate 242 is fixed to the inner wall surface of the support column 1 by a fastening member such as a bolt or a nut. The winding transmission mechanism 26 shown in FIG. 6 is inserted into the internal space 1S (see FIG. 7) from one end of the tubular form of the support column 1, and the facing plate 242 is fixed to the support column 1 to fix the support column 1. The internal space 1S of 1 is arranged so that the elevating portion 2 in the column can be elevated along the guide rail 33.

The pulley fixing members 230 and 240 have dropout prevention members 233 and 243 at positions facing the pulley grooves of the pulleys 24A, 23B, 24C and 23D to prevent the wound wire rope 25 from falling off. The dropout prevention members 233 and 243 here are bolts arranged so as to penetrate the facing plates 232 and 242, and are fixed to the facing plates 232 and 242 by being fastened with nuts. Further, the fall prevention member 243 corresponding to the fixed pulleys 24A and 24C is located above the corresponding pulleys 24A and 24C, and the fall prevention member 233 corresponding to the moving pulleys 23B and 23D is located below the pulleys 23B and 23D. It is positioned to prevent the wire rope 25 from falling off.

The wire rope 25 is a single wire rope, and as shown in FIGS. 5 and 6, the wire rope 25 is once for all the pulleys 24A, 23B, 24C, and 23D constituting the moving pulley group 23 and the fixed pulley group 24. It is wound. Specifically, in the wire rope 25, one end 25A is connected to the base end side of the cylinder 21S, and the wire rope 25 starts from the moving pulley 23D having the minimum diameter d on the tip end side of the piston rod 21R and starts from the base end of the cylinder 21S. It continues in a form of being wound around a fixed pulley 24C on the part side and a moving pulley 23B on the tip side of the piston rod 21R, and finally hangs around to a fixed pulley 24A having a maximum diameter a on the base end side of the cylinder 21S. The other end 25B is connected to the rack 13 via the portion 25C.

The other end 25B of the wire rope 25 is directly connected to the lower carriage 22 here, and is racked via the lower carriage 22 and the upper carriage 12 locked to the lower carriage 22. Can be connected to 13.

Further, one end 25A of the wire rope 25 is fixed here in a form of being hooked on the dropout prevention member 243 of the fixed pulley 24C. Therefore, the fall-off prevention member 243 has both functions of preventing the wire rope 25 from falling off and fixing the wire rope 25.

As shown in FIGS. 5 and 6, the winding transmission mechanism 26 configured in this way is wound so that the number of suspended wire ropes 25 with respect to the moving pulley group 23 is 3 or more (4 in this case). ing. As a result, as shown in FIG. 4, the actual vehicle drive stroke SM represented as the movement range (S1 to S2) of the connection point between the piston rod 21R and the moving pulley group 23 according to the advance / retreat of the piston rod 21R is in the actual vehicle state. Is less than 1/2 (here, about 1/3) with respect to the rack stroke SR represented as the movement range (S3 to S4) of the lower end (here, the lower end of the lower bogie 22) of the rack elevating operation portion including the rack 13. Will be. The actual vehicle drive stroke SM is the same as the moving distance SQ (see FIG. 8) of the O-ring 21Q1 which is a sealing member of the elevating gas spring 21 in the cylinder 21S and the moving distance (unsigned) of the O-ring 21Q2 with respect to the piston rod 21R. Therefore, the moving distance SQ is shorter than that of the case where the moving pulley and the fixed pulley are each one. As a result, the shortened amount is accumulated by repeated reciprocating movements, and the life of the O-rings 21Q1 and 21Q2, which are the sealing members, is extended.

The above-mentioned "rack elevating operation unit" is an elevating body that is integrally raised and lowered with the rack 13 by the second drive unit 20, and here includes an upper carriage 12 and a lower carriage 22.

Further, the above "actual vehicle drive stroke SM" is equal to the "piston stroke of the elevating gas spring 21", and the "moving distance SQ of the O-ring 21Q1 in the cylinder 21S (see FIG. 8)" and the "piston of the O-ring 21Q2". It is also synonymous with "moving distance with respect to rod 21R (unsigned)". The "actual vehicle drive stroke SM" is not limited to the vertical direction, and may not be parallel to the "rack stroke SR".

Further, the above-mentioned "the pulley diameter increases in the winding order" includes the case where any two (one set) pulleys having a continuous winding order have the same diameter. Here, in order to prevent the wire ropes 25 to be wound from coming into contact with each other, the maximum number of pulleys having the same diameter is two.

According to the winding transmission mechanism 26, as shown in FIG. 4, when the total height of the support column 1 is equally divided into three areas of the upper stage A, the middle stage B and the lower stage C, the rack stroke SR is the middle stage B and the lower stage C. It is located across both areas, and the actual vehicle drive stroke SM is located only in the area of the middle stage B. Furthermore, when the rack stroke SR is bisected into the upper and lower areas, the actual vehicle drive stroke SM is located only in the upper area.

As shown in FIG. 5, in the pulleys 24A and 24C constituting the fixed pulley group 24 here, the rotation axes P24 are arranged apart by a certain distance in the vertical direction (vertical direction), but in the front-rear direction. They are placed at the same position in the direction. Further, in the width direction of the support column 1, the positions of the rotation centers of the pulleys 24A and 24C are the same. On the other hand, the pulleys 23B and 23D constituting the moving pulley group 23 are arranged so that the rotation axes P23 are separated by a certain distance in the vertical direction (vertical direction), but are arranged at the same positions in the front-rear direction. .. Further, in the width direction of the support column 1, the positions of the rotation centers of the pulleys 23B and 23D are the same. However, the positions of the rotation centers of the pulleys 24A and 24C constituting the fixed pulley group 24 and the pulleys 23B and 23D constituting the moving pulley group 23 are such that the pulleys 24A and 24C constituting the fixed pulley group 24 are on the front side. It is located at a different position.

Further, the elevating gas spring 21 here is arranged in the column 1 so that the axis of the piston rod 21R extends in the vertical direction (vertical direction). As a result, the advance / retreat of the piston rod 21R and the ascending / descending of the moving pulley group 23 (the elevating portion 2 in the column) become smoother. However, since the guide rail 33 guides the roller 3 from both sides in the front-rear direction, there is no problem even if the axis of the piston rod 21R does not extend in the vertical direction (vertical direction) and is slightly inclined. Here, the axis of the piston rod 21R is in a positional relationship (here, an orthogonal positional relationship) with the rotating axes P23 of the pulleys 23B and 23D constituting the moving pulley group 23, and the fixed pulley group 24 is formed. The pulleys 24A and 24C are in a positional relationship parallel to the alignment direction (vertical direction) of the rotation axes P24.

Further, as shown in FIGS. 1 to 4, the bicycle parking machine 100 of the first embodiment includes a bogie lock mechanism 40 (lower stop mechanism) and a rack lock mechanism 50 (movement stop mechanism). As for the carriage lock mechanism 40 and the rack lock mechanism 50, since the same mechanism is described in Patent Document 2, detailed description thereof will be omitted.

As shown in FIG. 2, the trolley lock mechanism 40 disconnects the upper and lower trolleys 12 and 22 when the bicycle BCL is not carried into the rack 13 and is in a trolley lock operating state in which the lower trolley 22 cannot be raised and lowered. On the other hand, as shown in FIG. 3, when the bicycle BCL is carried into the rack 13, the upper and lower bogies 12 and 22 are connected, and the lower bogie 22 is unlocked so that the lower bogie 22 can be raised and lowered.

Specifically, the bogie lock mechanism 40 engages (locks here) the lower bogie 22 with the support column 1 when the lower bogie 22 is in a predetermined lower stage position and the rack 13 is in an empty state. Then, the lower bogie 22 is locked so as not to be able to move up and down (see FIG. 2). Then, when the upper bogie 12 descends with respect to the lower bogie 22 in this bogie lock operating state, it becomes a connectable state in which the upper bogie 12 is arranged close to each other in the vertical direction. In conjunction with the detection operation, the upper and lower bogies 12 and 22 are connected so as to be able to move up and down in an integrated state. Further, the bogie lock mechanism 40 disengages the lower bogie 22 with the support column 1 in conjunction with the connecting operation, and unlocks the lower bogie 22 so that the lower bogie 22 can be raised and lowered (see FIG. 3). In this way, the bogie lock mechanism 40 acts as a lower bogie lock mechanism (second lift bogie lock mechanism) and a bogie connecting mechanism.

The means for detecting the empty state and the actual vehicle state of the rack 13 is a wheel receiver 44 that can swing back and forth on the rack 13 and is urged in a backward tilted state by a wheel bearing member (not shown) such as a spring member. (First detection means). When the wheel receiver 44 is in the backward tilted state (actual vehicle non-detection state), it is detected as an empty vehicle state, and when it is in the forward tilted state (actual vehicle detection state) by receiving the preceding carry-in wheel (for example, front wheel FW) of the bicycle BCL, it is the actual vehicle. Detect as a state. In conjunction with the operation of the wheel receiver 44, the carriage lock mechanism 40 switches between the carriage lock operating state and the carriage lock release state.

The rack lock mechanism 50 is in a rack lock operating state in which the rack 13 cannot be raised or lowered with respect to the support column 1 when the rack 13 is in a predetermined lower position (see FIGS. 2 and 3) or a predetermined upper position (see FIGS. 1 and 4). On the other hand, the rack lock operating state is released based on the operation of the operating member 54 (second detecting means), and the predetermined lower position (see FIGS. 2 and 3) or the predetermined upper position (FIGS. 1 and 4). ) Allows the rack 13 to move up and down with respect to the column 1.

Specifically, the rack lock mechanism 50 is a support column when the rack 13 is in a predetermined lower position (see FIG. 2) or a predetermined upper position (see FIG. 3) and the operating member 54 is in an inactive state. The upper carriage 12 is engaged (locked here) with respect to 1, and the upper carriage 12 is locked so as not to be able to move up and down (see FIG. 2). Then, when the operating state of the operating member 54 is detected in this rack lock operating state, the rack lock mechanism 50 disengages the upper carriage 12 with the support column 1 in conjunction with the detection operation, and raises and lowers the upper carriage 12. Unlock so that is possible (rack unlocked state). In this way, the rack lock mechanism 50 acts as an upper carriage lock mechanism (first lift carriage lock mechanism).

The actuating member 54 is provided at the entrance / exit 15 of the carry-in bicycle BCL at the rear end of the rack 13, and is provided by an actuating member urging member (not shown) such as a spring member so that the tip end side (rear end side) is at an upper position. Be urged. When the tip side (rear end side) of the actuating member 54 is in the upper position, it is in the non-operation state (operation non-detection state), and the tip side (rear end side) is the wheel (front wheel FW or rear wheel RW) of the bicycle BCL. The operating state (operation detection state) is when the wheel is pushed down to the lower position by being placed on the wheel or by an artificial operation.

As described above, the bogie lock mechanism 40 is a mechanism that locks and holds the lower bogie 22 at a predetermined lower stage position to prohibit the rack 13 from ascending, and the wheel receiver 44 receives the wheels and the lower bogie 22 becomes the upper bogie 12. The lock can be released when connected. On the other hand, the rack lock mechanism 50 is a mechanism that locks and holds the upper carriage 12 at a predetermined lower position and upper position to prohibit the rack 13 from moving up and down, and the lock can be released by operating the operating member 54.

The operation of the bicycle parking machine 100 of the first embodiment described above will be described.

<Empty car standby state = empty car state rack is in the upper position: Fig. 1>
-The rack 13 and the upper trolley 12 are in the upper position.-The upper trolley 12 cannot be lowered by the rack lock mechanism 50 (the operating member 54 is not operated).
-The lower bogie 22 is in the lower position (the moving pulley group 23 is in the upper position, and the piston rod 21R is in and out).
-The lower bogie 22 cannot be raised by the bogie lock mechanism 40 (the wheel receiver 44 is in a backward tilted state).
-The upper and lower trolleys 12 and 22 are separated from each other in the upper and lower states (cannot be connected).

<Empty rack descent = Empty rack descends: Fig. 1 → Fig. 2>
In the state of FIG. 1, when the operating member 54 is brought into the operating state by an artificial operation, the rack lock mechanism 50 switches the upper carriage 12 so as to be able to descend. Then, the rack 13 and the upper carriage 12 are lowered to the position shown in FIG. 2 against the urging force of the constant load spring 11. Since the urging force of the constant load spring 11 is almost balanced with the total weight of the rack 13 and the upper carriage 12 (actually, it is set slightly larger than the total load), the rack 13 is pushed down with a slight force. Can be done.

<Bicycle-carryable state = empty rack is in the lower position: Fig. 2>
-The rack 13 and the upper trolley 12 are in the lower position.-The upper trolley 12 cannot be raised by the rack lock mechanism 50 (the operating member 54 is not operated).
-The lower bogie 22 is in the lower position (the moving pulley group 23 is in the upper position, and the piston rod 21R is in and out).
-The lower bogie 22 is kept unable to climb by the bogie lock mechanism 40 (the wheel receiver 44 remains tilted backward).
-The upper and lower trolleys 12 and 22 are in a connectable state close to the top and bottom (however, they are not connected).

<Bicycle carry-in = Bicycle is brought into an empty rack: Fig. 3>
-The rack 13 and the upper trolley 12 are in the lower position.-The upper trolley 12 cannot be raised by the rack lock mechanism 50 (the operating member 54 is not operated).
-The lower bogie 22 is in the lower position (the moving pulley group 23 is in the upper position, and the piston rod 21R is in and out).
-The lower bogie 22 can be raised by the bogie lock mechanism 40 (the wheel receiver 44 is switched to the forward tilted state).
・ Both upper and lower bogies 12 and 22 are now connected.

<Rise of actual vehicle rack = Rise of actual vehicle rack: Fig. 3 → Fig. 4>
In the state of FIG. 3, when the operating member 54 is brought into the operating state by an artificial operation (for example, stepping on the operating member 54), the rack lock mechanism 50 switches the upper carriage 12 so that it can be raised. Then, the rack 13 and the upper and lower carriages 12 and 22 are pulled up to the position shown in FIG. 4 by using the urging force of the constant load spring 11 and the elevating gas spring 21. At this time, the piston rod 21R of the elevating gas spring 21 protrudes, and the moving pulley group 23 changes its position from top to bottom. Since the urging force of the constant load spring 11 and the elevating gas spring 21 is almost balanced with the total weight of the bicycle BCL, the rack 13, and the upper and lower carriages 12 and 22 (actually, it is set slightly larger than the total load). The rack 13 can be pulled up with a slight force.

<Actual vehicle standby state = The rack in the actual vehicle state is in the upper position: Fig. 4>
-The rack 13 and the upper trolley 12 are in the upper position.-The upper trolley 12 cannot be lowered by the rack lock mechanism 50 (the operating member 54 is not operated).
-The lower bogie 22 is in the upper position (the moving pulley group 23 is in the lower position, and the piston rod 21R is protruding).
-The lower bogie 22 can be lowered by the bogie lock mechanism 40 (the wheel receiver 44 maintains the forward tilted state).
・ Both upper and lower bogies 12 and 22 remain connected.

<Actual vehicle rack descent = The actual vehicle rack descends: Fig. 4 → Fig. 3>
When the operating member 54 is brought into the operating state by an artificial operation in the state of FIG. 4, the rack lock mechanism 50 switches the upper carriage 12 so as to be able to descend. Then, the rack 13 and the upper and lower carriages 12 and 22 are lowered to the position shown in FIG. 3 against the urging force of the constant load spring 11 and the elevating gas spring 21. At this time, the piston rod 21R of the elevating gas spring 21 retracts, and the moving pulley group 23 changes its position from bottom to top. Since the urging force of the constant load spring 11 and the elevating gas spring 21 is almost balanced with the total weight of the bicycle BCL, the rack 13, and the upper and lower carriages 12 and 22 (actually, it is set slightly larger than the total load). The rack 13 can be pushed down with a slight force.

<Bicycle unloading = When the bicycle is unloaded from the rack, the empty rack automatically rises: Fig. 3 → Fig. 2 → Fig. 1>
When the bicycle BCL moves backward on the rack 13 in the state of FIG. 3, the front wheel FW (preceding carry-in wheel) separates from the wheel receiver 44 and returns to the forward leaning state. As a result, the lower bogie 22 is switched so as not to be able to rise by the bogie lock mechanism 40.
-Furthermore, when the bicycle BCL moves backward on the rack 13 and the front wheel FW (preceding carry-in wheel) is placed on the operating member 54, the operating member 54 is pushed down to enter the operating state. As a result, the upper carriage 12 is switched so as to be able to be raised by the rack lock mechanism 50. However, since the front wheel FW (preceding carry-in wheel) is mounted on the operating member 54, the upper bogie 12 cannot be raised due to its weight.
When the front wheel FW (preceding carry-in wheel) is separated from the operating member 54, the rack 13 and the upper bogie 12 are automatically raised by using the urging force of the constant load spring 11. Since the urging force of the constant load spring 11 is almost balanced with the total weight of the rack 13 and the upper carriage 12 (actually, it is set slightly larger than the total load), the rack 13 is shown in FIG. 1 with a slight force. Can be pushed up to the position of. The lower bogie 22 is left at the lower position.

<Empty rack rise = Empty rack rises: Fig. 2 → Fig. 1>
In the state of FIG. 2, the upper trolley 12 cannot be raised by the rack lock mechanism 50, but the rack lock mechanism 50 raises the upper trolley 12 when the operating member 54 is brought into the operating state by an artificial operation. Switch to possible. Then, while leaving the lower carriage 22 at the lower position, the rack 13 and the upper carriage 12 are raised to the position shown in FIG. 1 by using the urging force of the constant load spring 11. Since the urging force of the constant load spring 11 is almost balanced with the total weight of the rack 13 and the upper carriage 12 (actually, it is set slightly larger than the total load), the rack 13 is pushed up with a slight force. Can be done.

The first embodiment of the present invention has been described above, but this is merely an example, and the present invention is not limited thereto, and knowledge of those skilled in the art as long as it does not deviate from the scope of claims. Various changes such as addition and omission can be made based on the above.

Hereinafter, examples different from the above-described examples and modified examples of those examples will be described. The parts having the same functions as those in the above embodiment are designated by the same reference numerals, and detailed description thereof will be omitted. Further, the above embodiment and the following modified examples and other embodiments can be appropriately combined and carried out within a range that does not cause a technical contradiction.

A second embodiment of the present invention will be described with reference to the drawings.

In the bicycle parking machine 100 of the second embodiment shown in FIGS. 9 to 12, the left-right direction of each figure is the front-rear direction of the bicycle parking machine 100 (opposite to the first embodiment, the right is the front and the left is the back). , The depth direction of each figure is defined as the width direction of the bicycle parking machine 100, and the vertical direction of each figure is defined as the vertical direction of the bicycle parking machine 100 as it is.

The bicycle parking machine 100 of the second embodiment is a type in which the empty rack 62 is stored upside down, and as shown in FIGS. 9 to 12, the empty rack 62 on which the bicycle BCL is not mounted is vertically tubular. First drive unit 110 (empty vehicle swing drive unit) for swinging between the horizontal posture (see FIG. 10) at the lower part of the support column 1 erected in 1 and the inverted posture along the support column 1 (see FIG. 9). A second drive unit 120 (actual vehicle elevating drive unit) for raising and lowering the rack 62 in the actual vehicle state (see FIGS. 11 and 12) on which the bicycle BCL is mounted in a horizontal posture along the support column 1 is provided.

First, the second drive unit 120 will be described. The second drive unit 120 operates as a bogie lifting mechanism for raising and lowering the bogie 61 (lifting bogie) by the first urging member 11 and the second urging member 21 described in the first embodiment. The bogie 61 is urged so as to be constantly pulled upward by the first urging member 11 and the second urging member 21 forming an actuator for driving the actual vehicle up and down. The second drive unit 120 here acts to constantly pull up the trolley 61 with a traction force corresponding to the total load of the trolley 61, the rack 62 (including rack accessories such as the brace 63), and the rack-mounted bicycle BCL. .. In the second embodiment, the elevating body including the rack 62 and the bogie 61 is the rack elevating operation unit, and the actual vehicle drive stroke (piston stroke) is halved with respect to the rack stroke as in the first embodiment. It is below.

The first urging member 11 here uses the same constant load spring 11 (constant load spring for raising and lowering the actual vehicle) as in the first embodiment, and the second urging member 21 is the first. The same elevating gas spring 21 (actual vehicle elevating gas spring) as in the embodiment is adopted.

Further, the second drive unit 120 has a winding transmission mechanism 26 including a moving pulley group 23, a fixed pulley group 24, and a wire rope 25, as in the first embodiment. Since the configuration of the winding transmission mechanism 26 is the same as that of the first embodiment, the description thereof will be omitted. The winding transmission mechanism 26 of the second embodiment is different from the first embodiment in that the elevating gas spring 21 always urges the same bogie 61 upward together with the constant load spring 11. That is, the second drive unit 120 of the second embodiment includes a main drive unit having the elevating gas spring 21 and the winding transmission mechanism 26, and an auxiliary drive unit having the constant load spring 11. ing.

The dolly 61 is integrally assembled with the rack 62 so as to be able to move up and down, and a traction force is applied by the second drive unit 120 to provide a predetermined lower position (see FIGS. 10 and 11) and a predetermined upper position with respect to the support column 1. (See FIG. 12) is arranged so as to be able to move up and down by a roller 6. The carriage 61 here also moves up and down along a guide rail 34 provided on the rear side surface of the support column 1 as shown in FIG. 7, like the upper carriage 12 and the lower carriage 22 of the first embodiment. The bogie 61 is in the lower position (see FIG. 10) together with the rack 62 when the piston rod 21R of the elevating gas spring 21 moves in and out (contracts), and is brought into the actual vehicle state by carrying in the bicycle BCL (see FIG. 11), while the piston Due to the protrusion (extension) of the rod 21R, it rises to the upper position together with the rack 62 to store the bicycle BCL (see FIG. 12).

The first drive unit 110 has a basic configuration for realizing an inverted storage of the rack 62, that is, a function as an empty vehicle swing drive unit for storing the rack 62 in an empty vehicle state in which the bicycle BCL is not mounted in an inverted state (see FIG. 9). The rotary slider crank mechanism 60 and the rack rotation mechanism 70 (moment applying mechanism) are provided. The mechanism related to these is also described in Patent Document 3.

As shown in FIGS. 9 to 12, the rotary slider crank mechanism 60 includes a carriage 61 that functions as a fixed link, a rack 62 that functions as a rotary drive link, and a brace 63 (side guard) that functions as a rotary driven link. It is formed in the shape of a rigid body triangle. The carriage 61 functions as a fixed link in the rotary slider crank mechanism 60.

As shown in FIG. 10, the rack 62 is rotatably supported in the front-rear direction around a rotation shaft 620 (rotation axis C62) whose front end portion (base end portion) extends in the width direction with respect to the lower portion of the carriage 61. It has a gutter shape and extends in a cantilever shape, and a doorway 65 for carrying in and out the bicycle BCL is formed at the tip (rear end). The rack rotation mechanism 70 applies a moment centered on the rotation shaft 620 to the front end in the empty state, and is rotatably arranged from the horizontal state to the inverted state along the support column 1 with respect to the trolley 61 at the lower stage position ( (Details will be described later), the rotary slider crank mechanism 60 functions as a rotary drive link.

A pair of braces 63 are arranged on both sides of the rack 62 in the width direction, and one end portion (upper end portion in FIGS. 10 to 12) of the brace 63 is arranged with respect to the upper portion of the carriage 61 with respect to the swing shaft 630 in the width direction (swing axis C63). It is supported so that it can swing around. On the other hand, the other end of the pair of braces 63 (the lower end in FIGS. 10 to 12) is an elongated hole 621 (guide portion) formed in the middle of the rack 62 and closer to the rear end (tip). On the other hand, a slide pin 631 (slider) that is slidably supported in an empty state (see FIG. 10) at the lower stage is formed, and functions as a rotation driven link in the rotation slider crank mechanism 60.

As described above, the rotary slider crank mechanism 60 is configured such that the rack 62 and the brace 63 crank movement via the slide pin 631 (slider center C61). Specifically, the empty rack 62, the brace 63, and the carriage 61 shown in FIG. 10 are deployed in a right-angled triangular shape with the rack 62 substantially horizontal at the lower position of the support column 1, while the slide pins. As the 631 slides in the elongated hole 621 along the longitudinal direction of the rack, the rack 62 and the brace 63 rotate upward with respect to the carriage 61 and are stored in an inverted state along the support column 1. Then, in this inverted state, the rack 62 is housed so as to overlap with the carriage 61 and the brace 63 (see FIG. 9).

The brace 63 is provided with a tire guard 64 for holding the front wheel FW (preceding carry-in wheel) when the bicycle BCL is mounted on the rack 62 in the horizontal state at the lower position. In the process in which the empty rack 62 and the brace 63 rotate upward to reach the inverted state, the upper end of the tire guard 64 comes into contact with the support column 1 and resists the urging force of the standing urging spring (not shown). Gradually change the posture along the support column 1. Then, when the rack 62 is stored upside down, the tire guard 64 is stored so as to overlap the rack 62 and the support column 1 (see FIG. 9).

As shown in FIGS. 9 to 12, the rack rotation mechanism 70 is mainly composed of a rotating gas spring 71 (gas spring for driving an empty vehicle swing) forming an actuator for driving an empty vehicle swing, and its base end is a bogie. The tip of the piston rod 71R is attached to the front end of the rack 62 while it is attached to the upper end of the 61. The push output of the piston rod 71R generates a moment whose arm length is the horizontal separation distance between the tip mounting position of the piston rod 71R and the rotation axis C62. The rack 62 is maintained in a horizontal state when the piston rod 71R is retracted (retracted) (see FIGS. 10 to 12). On the other hand, when the piston rod 71R protrudes (extends), the rack 62 and the brace 63 rotate upward with respect to the carriage 61 and are stored in an inverted state along the support column 1 (see FIG. 9). The rotating gas spring 71 of the rack rotation mechanism 70 acts so as to always store the front end portion of the rack 62 in an inverted state with a moment corresponding to the total load of the rack 62 (including rack accessories such as the brace 63). ..

Further, the bicycle parking machine 100 of the second embodiment has a bogie lock mechanism 80, a slider lock mechanism 66, and a rack lock mechanism 90. Although these mechanisms will be described below, detailed description of these mechanisms will be omitted because similar mechanisms are described in Patent Document 3.

When the bogie 61 is in a predetermined lower position, the bogie lock mechanism 80 raises and lowers the bogie 61 based on the traction force of the elevating gas spring 21 for raising and lowering the actual vehicle and the constant load spring 11 with respect to the support column 1 when the rack 13 is empty. The lock is activated so that the vehicle cannot move up and down (see FIG. 10), and the lock is released so that the vehicle can move up and down in the actual vehicle state (see FIG. 11).

In the bogie lock mechanism 80 here, as shown in FIG. 10, the wheel receiver 84 (first detecting means) that can swing back and forth on the rack 62 and is urged to lean backward is in a backward tilted state (actual vehicle). If the trolley 61 is in a predetermined lower position when it is in the non-detection state), it is maintained in the trolley lock operating state in which it cannot be raised or lowered. In this bogie lock operating state, as shown in FIG. 11, the bicycle BCL is carried into the rack 62, and the wheel receiver 84 (first detection means) receives the preceding carry-in wheel (for example, the front wheel FW of the bicycle BCL) and tilts forward. When the state (actual vehicle detection state) is reached, the trolley lock mechanism 80 switches the trolley 61 at a predetermined lower stage position to a trolley unlock state capable of raising and lowering in conjunction with the movement.

However, as shown in FIG. 9, when the rack 62 is stored in the inverted state, the carriage lock mechanism 80 switches to a non-interlocking state with the wheel receiver 84 and shifts to a state in which the carriage lock operating state is maintained. ..

As shown in FIG. 10, the slider lock mechanism 66 prohibits the slide pin 631 from sliding with respect to the elongated hole 621 when the carriage 61 is in a predetermined lower position and the rack 62 is in a horizontal state. The rack 62 and the brace 14 are locked by allowing the slide pin 631 to slide while the rack 62 and the brace 63 cannot be rotated upward based on the moment by the rotating gas spring 71. Unlock so that it can rotate upwards.

To switch between prohibiting and permitting the slide movement of the slide pin 631, the operating member 94 (second detecting means) arranged at the entrance / exit 65 of the rack 62, which is arranged at the entrance / exit 65 of the rack 62 and also serves as an empty vehicle state detecting means and an artificial operating means. ) Is operated. Similar to the operating member 54 of the first embodiment, the operating member 94 here is pushed down on the tip side when the wheel of the bicycle BCL is placed on the operating member 94 or when an artificial operation is performed. As a result, it becomes an operating state (operation detection state).

However, as shown in FIG. 9, when the rack 62 is in the inverted storage state, the position of the slide pin 631 (slide center C61) of the slider lock mechanism 66 is different from the position when the rack 62 is in the horizontal state. Since it is sliding, it cannot be locked, and the slide movement of the slide pin 631 is permitted.

The rack lock mechanism 90 operates while the rack lock mechanism 90 is in a rack lock operating state in which the rack 62 cannot be raised or lowered with respect to the support column 1 when the rack 62 is in a predetermined lower position (see FIGS. 10 and 11) or an upper position (see FIG. 12). The rack lock operating state is released based on the operation of the member 94 (second detection means), and the support column 1 can be raised and lowered at a predetermined lower position (see FIGS. 10 and 11) or an upper position (see FIG. 12). To do.

Specifically, in the rack lock mechanism 90, the rack 62 is in a predetermined lower position (see FIGS. 10 and 11) or a predetermined upper position (see FIG. 12), and the operating member 94 is in an inactive state. Occasionally, the carriage 61 is engaged (locked here) with the support column 1 and locked so that the carriage 61 cannot be raised or lowered (see FIG. 2). Then, when the operating state of the operating member 54 is detected in this rack lock operating state, the rack lock mechanism 90 disengages the carriage 61 with the support column 1 in conjunction with the detection operation, and the carriage 61 can be raised and lowered. Unlock so that (rack unlocked state).

When the rack 62 is stored in the inverted state, the rack lock mechanism 90 disengages the rack 62 from the support column 1 to maintain the unlocked state (rack unlocked state).

As described above, the bogie lock mechanism 80 is a mechanism that locks and holds the bogie 61 at a predetermined lower stage position to prohibit the rack 62 from ascending, and the lock can be released by receiving the wheels by the wheel receiver 44. Further, the slider lock mechanism 66 is a mechanism that locks and holds the rack 62 in the horizontal state to prohibit the transition to the inverted state, and the lock can be released by the operation of the operating member 94. On the other hand, the rack lock mechanism 90 is a mechanism that locks and holds the carriage 61 at predetermined lower and upper positions to prohibit the rack 62 from moving up and down, and the lock can be released by operating the operating member 94.

The operation of the bicycle parking machine 100 of the second embodiment described above will be described.

<Inverted storage state = empty rack is in the inverted state: Fig. 9>
-The rack 62 is urged and held in an inverted state by a rotating gas spring 71.-Since the rack 62 is in an inverted state, it is not locked by the slider lock mechanism 66 and can shift to a horizontal state.-The pulley 61 is in the lower position. (Moving pulley group 23 is in the upper position, piston rod 21R is in and out)
-The dolly 61 cannot be raised by the dolly lock mechanism 80 (the wheel receiver 84 and the dolly lock mechanism 80 are not linked).
-The dolly 61 can be raised by the rack lock mechanism 90 (the operating member 94 is not operated, but the rack 62 is in an inverted state).
-The tire guard 64 is stored along the support column 1.

<Return to horizontal state = The empty rack becomes horizontal: Fig. 9 → Fig. 10>
In the state of FIG. 9, the handle 69 of the rack 62 is grasped to return the rack 62 in the inverted state to the horizontal state of FIG. The tire guard 64 also returns to the upright state. Since the moment acting on the rack 62 by the rotating gas spring 71 is almost balanced with the total weight of the rack 62 (actually, it is set slightly larger than the total load), the rack 62 is slowly moved with a slight force. Can be pushed down.

<Bicycle-carryable state = empty rack is in the lower position: Fig. 10>
-The rack 62 is in the horizontal state at the lower position.-The rack 62 cannot be transferred to the inverted state by the slider lock mechanism 66 (the operating member 94 is not operated).
-The bogie 61 is in the lower position (the moving pulley group 23 is in the upper position, and the piston rod 21R is in and out).
-The dolly 61 cannot be raised by the dolly lock mechanism 80 (the wheel receiver 84 is linked with the dolly lock mechanism 80, and the actual vehicle is not detected).
-The dolly 61 cannot be lifted by the rack lock mechanism 90 (the operating member 94 is not operated).
・ Tire guard 64 returns to the upright state

<Bicycle carry-in = Bicycle is brought into an empty rack: Fig. 11>
-The rack 62 is in the horizontal state at the lower position.-The rack 62 cannot be transferred to the inverted state by the slider lock mechanism 66 (the operating member 94 is not operated).
-The bogie 61 is in the lower position (the moving pulley group 23 is in the upper position, and the piston rod 21R is in and out).
-The dolly 61 can be raised by the dolly lock mechanism 80 (the wheel receiver 84 is linked with the dolly lock mechanism 80 and switches to the actual vehicle detection state).
-The dolly 61 cannot be lifted by the rack lock mechanism 90 (the operating member 94 is not operated).
・ Tire guard 64 is in an upright position

<Rise of actual vehicle rack = Rise of rack in actual vehicle state: Fig. 11 → Fig. 12>
In the state of FIG. 11, when the operating member 94 is brought into the operating state by an artificial operation (for example, stepping on the operating member 94), the rack lock mechanism 90 switches the carriage 61 so that it can be raised. Then, the rack 62 and the bogie 61 are pulled up to the position shown in FIG. 12 by using the urging force of the constant load spring 11 for raising and lowering the actual vehicle and the gas spring 21 for raising and lowering. Since their urging force is almost balanced with the total weight of the bicycle BCL, trolley 61, and rack 62 (actually, it is set slightly larger than the total load), it is possible to push up the rack 62 with a small force. it can. At this time, the piston rod 21R of the elevating gas spring 21 protrudes, and the moving pulley group 23 descends.

<Actual vehicle standby state = The rack in the actual vehicle state is in the upper position: Fig. 12>
-The rack 62 is in the horizontal state at the upper position.-The rack 62 cannot be transferred to the inverted state by the slider lock mechanism 66 (the operating member 94 is not operated).
-The bogie 61 is in the upper position (the moving pulley group 23 is in the lower position, and the piston rod 21R is protruding).
-The dolly 61 can be lowered by the dolly lock mechanism 80 (the wheel receiver 84 is linked with the dolly lock mechanism 80 to maintain the actual vehicle detection state).
-The dolly 61 cannot be lowered by the rack lock mechanism 90 (the operating member 94 is not operated).
・ Tire guard 64 is in an upright position

<Actual vehicle rack descent = The actual vehicle rack descends: Fig. 12 → Fig. 11>
When the operating member 94 is brought into the operating state by an artificial operation in the state of FIG. 12, the rack lock mechanism 90 switches the carriage 61 so as to be able to descend. Then, the bogie 61 and the rack 62 in the actual vehicle state are lowered to the position shown in FIG. 11 against the urging force of the constant load spring 11 for raising and lowering the actual vehicle and the gas spring 21 for raising and lowering the actual vehicle. Since their urging force is almost balanced with the total weight of the bicycle BCL, trolley 61, and rack 62 (actually, it is set slightly larger than the total load), it is possible to push down the rack 62 with a small force. it can. At this time, the piston rod 21R of the elevating gas spring 21 is pulled back, and the moving pulley group 23 rises.

<Bicycle carry-out + rack automatic inverted storage = rack rotates as the bicycle is carried out: Fig. 11 → Fig. 10 → Fig. 9>
When the bicycle BCL moves backward on the rack 62 in the state of FIG. 11, the front wheel FW (preceding carry-in wheel) separates from the wheel receiver 84 and the actual vehicle is not detected. As a result, the bogie 61 is switched so as not to be able to rise by the bogie lock mechanism 80.
Further, when the bicycle BCL moves backward on the rack 62 and the front wheel FW (preceding carry-in wheel) is placed on the operating member 94, the operating member 94 is pushed down to enter the operating state. As a result, the rack 62 is switched to the inverted state by the slider lock mechanism 66. However, since the front wheel FW (preceding carry-in wheel) is mounted on the operating member 94, the rack 62 is maintained in a horizontal state due to its weight.
When the front wheel FW (preceding carry-in wheel) is separated from the operating member 94, the rack 62 is automatically rotated by the urging force of the rotating gas spring 71, and shifts to the inverted storage state as shown in FIG. Since the moment acting on the rack 62 by the rotating gas spring 71 is almost balanced with the total weight of the rack 62 (actually, it is set slightly larger than the total load), the rack 62 is shown with a slight force. It can be pushed up to the position of 9.

<Inverted storage of an empty rack = The empty rack rotates: Fig. 10 → Fig. 9>
In the state of FIG. 10, when the operating member 94 is brought into the operating state by an artificial operation (for example, stepping on the operating member 94), the slider lock mechanism 66 switches the rack 62 to the inverted state. Then, the rack 62 is pushed up to the position shown in FIG. 9 by using the urging force of the rotating gas spring 71. Since the urging force is almost balanced with the total weight of the rack 62 (actually, it is set slightly larger than the total load), the rack 62 can be pushed up with a small force.

A third embodiment of the present invention will be described with reference to FIG.

The bicycle parking machine 100 of the third embodiment is basically the same as that of the first embodiment shown in FIGS. 1 to 8, except that the first drive unit 130 is used instead of the first drive unit 10. There is. Since the second drive unit 20 is the same as that of the first embodiment, the description thereof will be omitted.

The first drive unit 130 has a first urging member 131 as an actuator for raising and lowering an empty vehicle for raising and lowering the upper carriage 12. The first urging member 131 uses a gas spring for lifting and lowering an empty vehicle (hereinafter abbreviated as gas spring 131) as shown in FIG. 13 instead of the constant load spring of the first embodiment, and is an upper bogie. It has a function of pulling the total load of the 12 (first lifting bogie: see FIG. 1) and the empty rack 13, and urges the upper bogie 12 to always be pulled upward. The gas spring 131 is arranged inside the support column 1, and the cylinder 131S is attached to the support column 1 directly or indirectly via an attachment member.

Further, the first drive unit 130 has a first winding transmission mechanism 136. The first winding transmission mechanism 136 is a moving pulley connected to the tip of a piston rod 131R that projects downward from the cylinder 131S of the gas spring 131 to which the base end is attached inside the support column 1 and exerts a traction force. It includes 133, a fixed pulley 134 fixed inside the column 1 at a position higher than the cylinder 131S, and a single wire rope 135 wound around the moving pulley 133 and the fixed pulley 134.

In the wire rope 135, one end 135A is fixed to the upper end side of the support column 1, and the wire rope 135 is hung from the moving pulley 133 on the inner and lower side of the support column 1 to the fixed pulley 134 on the inner and upper side of the support column 1, and the other end 135B is the rack 13. Is connected to. Specifically, the other end 135B is directly connected to the upper carriage 12 and is connected to the rack 13 via the upper carriage 12 (see FIGS. 1 to 4).

The moving pulley 133 is rotatably assembled with respect to the central axis so as to be sandwiched between the opposing plates. A roller 7 that rolls on a guide rail (not shown) extending in the vertical direction provided inside the support plate 1 is assembled to the facing plate. The elevating portion 8 in the support column including the moving pulley 133, the facing plate and the roller 7 is connected to the tip end portion of the piston rod 131R, and when the piston rod 131R is extended, it descends to pull up the upper carriage 12 and when it moves in and out. Ascend and lower the upper trolley 12.

In the third embodiment, the first winding transmission mechanism 136 described above is provided, and the winding transmission mechanism 26 used in the first embodiment is provided as the second winding transmission mechanism 26. The winding transmission mechanisms 136 and 26 are arranged in the support column 1 so as to be arranged in the width direction of the bicycle parking machine 100. The description of the second winding transmission mechanism 26 will be omitted.

When a gas spring is used in the first drive unit 130 for towing an empty rack as in the third embodiment, the empty rack 13 has a light load (for example, 5 to 7 kg weight). The degree of demand for improving the durability of the gas spring (that is, extending the life of the O-ring in the cylinder) is much lower than that of the gas spring 21 for driving the actual vehicle up and down of the second drive unit 20. Therefore, in the bicycle parking machine 100 of the third embodiment, the gas spring 131 and the winding transmission mechanism 136 of the first drive unit 130 may be changed to the elevating gas spring 21 and the winding transmission mechanism 26 of the first embodiment. You can, but you can leave it as it is.

The first modification of the bicycle parking machine 100 of the first to third embodiments will be described.

In the bicycle parking machines 100 of the first to third embodiments, the winding transmission mechanism 26 in those embodiments is provided with a moving pulley group 23 including one moving pulley 23B and two fixed pulleys 24A as shown in FIG. The winding transmission mechanism 27 having a fixed pulley group 24 composed of 24C can be used.

As shown in FIG. 14, the winding transmission mechanism 27 used in the first modification is relative to the moving pulley group 23 consisting of one moving pulley 23B and the fixed pulley group 24 consisting of two fixed pulleys 24A and 24C. , One end 25A of the wire rope 25 is connected to the tip end side of the piston rod 21R, and starts from the smallest fixed pulley 24C attached to the base end side of the cylinder 21S, so that the pulley diameter increases in the winding order. Continued in a form (24C → 23B → 24A) that is alternately wound around the moving pulley 23B arranged on the tip side of the piston rod 21R and the fixed pulleys 24C and 24A arranged on the base end side of the cylinder 21S. As a result, the last wound fixed pulley 24A corresponds to the fixed pulley having the maximum diameter a attached to the base end side of the cylinder. In this case, the number of suspended wire ropes 25 with respect to the moving pulley group 23 is 3, and the actual vehicle drive stroke SM (that is, the piston stroke) is less than 1/2 of the rack stroke SR (for example, about 1 / 2.5). ..

A second modification of the bicycle parking machine 100 of the first to third embodiments will be described.

In the bicycle parking machines 100 of the first to third embodiments, the winding transmission mechanism 26 of the first to third embodiments is provided with the moving pulley group 23 and the three fixed pulleys composed of the two moving pulleys 23B and 23D as shown in FIG. The winding transmission mechanism 28 having a fixed pulley group 24 composed of 24A, 24C, and 24E can be used.

As shown in FIG. 15, the winding transmission mechanism 28 used in the second modification is a moving pulley group consisting of two moving pulleys 23B and 23D and a fixed pulley group consisting of three fixed pulleys 24A, 24C and 24E. With respect to 24, one end 25A of the wire rope 25 is connected to the tip end side of the piston rod 21R, and starts from the fixed pulley 24E having the smallest diameter e attached to the base end portion side of the cylinder 21S, and the pulleys are wound in the order of winding. A shape in which the moving pulleys 23D and 23B arranged on the tip side of the piston rod 21R and the fixed pulleys 24E, 24C and 24A arranged on the base end side of the cylinder are alternately wound so as to increase the diameter ( 24E → 23D → 24C → 23B → 24A), and as a result, the last wound fixed pulley 24A corresponds to the fixed pulley 24A having the maximum diameter a attached to the base end side of the cylinder 21S. In this case, the number of suspended wire ropes 25 with respect to the moving pulley group 23 is 5, and the actual vehicle drive stroke SM (that is, the piston stroke) is less than 1/2 of the rack stroke SR (for example, about 1 / 3.5). ..

The present invention relates to any of the outdoor bicycle parking lots permanently installed on sidewalks, in parks, etc., indoor bicycle parking lots established in condominiums, apartments, etc., and underground bicycle parking lots attached to buildings, underground stations, etc. It can also be applied to bicycle parking devices. Although the present invention can be used for a two-stage upper and lower bicycle parking machine, the description is omitted because a known structure can be adopted for the lower bicycle parking portion.

100 Bicycle parking machine 1 Strut 10 First drive unit 11 Constant load spring 12 Upper trolley (first elevating trolley)
13 Rack 20 Second drive unit 21 Lifting gas spring 21S Cylinder 21R Piston rod 21P Piston 21Q1, 21Q2 O-ring (sealing member)
22 Lower trolley (second lift trolley)
23 Moving pulley group 23B, 23D Moving pulley 231 Central shaft 233 Falling prevention member 24 Fixed pulley group 24A, 24C, 24E Fixed pulley 241 Central shaft 243 Falling prevention member 25 Wire rope 26, 27, 28 Winding transmission mechanism 40 Cart 44 Wheel holder 50 Rack lock mechanism 54 Actuating member 60 Rotating slider Crank mechanism 61 Pulley 62 Rack 63 Brace 66 Slider lock mechanism 70 Rack rotation mechanism (moment applying mechanism)
71 Rotating gas spring (Gas spring for swinging empty vehicle)
80 Bogie lock mechanism 84 Wheel receiver 90 Rack lock mechanism 94 Acting member 110 First drive unit 120 Second drive unit 130 First drive unit 131 Lifting gas spring 133 Moving pulley 134 Fixed pulley 135 Wire rope 136 Winding transmission mechanism BCL Bicycle a, b, c, d, e Pulley diameter s Cylinder 21R outer diameter SM Actual vehicle drive stroke SR Rack stroke A Upper B Middle C Lower P23 Rotation axis P24 Rotation axis

Claims (6)

A first drive unit for raising and lowering an empty rack without a bicycle in a horizontal position along a support column erected in a tubular shape in the vertical direction, and a rack in an actual vehicle state with a bicycle mounted along the support column. A bicycle parking machine equipped with a second drive unit for raising and lowering in a horizontal position.
The second drive unit is connected to the tip end portion of a piston rod that projects downward from the cylinder of the actual vehicle lifting / lowering drive gas spring to which the base end portion is attached inside above the column and exerts a traction force, and one or more movements. A group of moving pulleys composed of pulleys, a group of fixed pulleys composed of two or more fixed pulleys fixed inside the support column at a position higher than the cylinder, the moving pulley group and all the pulleys constituting the fixed pulley group. Has a winding transmission mechanism that includes a single wire rope that is wound once in a row.
One end of the wire rope is connected to the tip end side of the piston rod or the base end side of the cylinder, and the minimum diameter fixed pulley or the tip of the piston rod attached to the base end side of the cylinder. Starting from the minimum diameter moving pulley attached to the part side, the moving pulley arranged on the tip side of the piston rod so that the pulley diameter increases in the winding order and the fixed pulley arranged on the base end side of the cylinder. The other end is connected to the rack through a hooking portion that leads to a fixed pulley having the maximum diameter attached to the base end portion side of the cylinder.
By winding the wire rope so that the number of suspended wire ropes with respect to the moving pulley group is 3 or more, the movement range of the connection point between the piston rod and the moving pulley group is shown as the movement range of the connection point between the piston rod and the moving pulley group according to the advancement and retreat of the piston rod. The actual vehicle drive stroke is less than 1/2 of the rack stroke represented as the movement range of the lower end of the rack elevating and lowering operation unit including the rack in the actual vehicle state. A first drive unit for swinging an empty rack without a bicycle between a horizontal posture at the bottom of a support column erected in a tubular shape in the vertical direction and an inverted position along the support column, and a bicycle. A bicycle parking machine including a second drive unit for raising and lowering the mounted rack in an actual vehicle state along the support column in a horizontal posture.
The second drive unit is connected to the tip end portion of a piston rod that projects downward from the cylinder of the actual vehicle lifting / lowering drive gas spring to which the base end portion is attached inside above the column and exerts a traction force, and one or more movements. A group of moving pulleys composed of pulleys, a group of fixed pulleys composed of two or more fixed pulleys fixed inside the support column at a position higher than the cylinder, the moving pulley group and all the pulleys constituting the fixed pulley group. Has a winding transmission mechanism that includes a single wire rope that is wound once in a row.
One end of the wire rope is connected to the tip end side of the piston rod or the base end side of the cylinder, and the minimum diameter fixed pulley or the tip of the piston rod attached to the base end side of the cylinder. Starting from the minimum diameter moving pulley attached to the part side, the moving pulley arranged on the tip side of the piston rod so that the pulley diameter increases in the winding order and the fixed pulley arranged on the base end side of the cylinder. The other end is connected to the rack through a hooking portion that leads to a fixed pulley having the maximum diameter attached to the base end portion side of the cylinder.
By winding the wire rope so that the number of suspended wire ropes with respect to the moving pulley group is 3 or more, the movement range of the connection point between the piston rod and the moving pulley group is shown as the movement range of the connection point between the piston rod and the moving pulley group according to the advance / retreat of the piston rod. The actual vehicle drive stroke is less than 1/2 of the rack stroke represented as the movement range of the lower end of the rack elevating and lowering operation unit including the rack in the actual vehicle state. The moving pulley group and each pulley constituting the fixed pulley group are individually held corresponding to a plurality of central axes arranged horizontally in a state parallel to each other along the advancing / retreating direction of the piston rod. The bicycle parking machine according to claim 1 or 2. The cylinder outer diameter of the gas spring for raising and lowering the actual vehicle is smaller than the pulley diameters of the moving pulley group and all the pulleys constituting the fixed pulley group, and
The one according to any one of claims 1 to 3, wherein the maximum diameter fixed pulley has a pulley diameter 1.5 to 2.0 times that of the minimum diameter fixed pulley or the minimum diameter moving pulley. Bicycle parking machine. When the total height of the columns is equally divided into three areas, upper, middle and lower, the rack stroke is located across both the middle and lower areas, and the actual vehicle drive stroke is located only in the middle area. The bicycle parking machine according to any one of claims 1 to 4. The bicycle parking machine according to any one of claims 1 to 5, wherein when the rack stroke is bisected into an upper area and a lower area, the actual vehicle drive stroke is located only in the upper area.

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