JPS6130947B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a winder used in a sliding ski lift, such as a shock lift, a T-bar lift, etc., for transporting passengers wearing skis while sliding on a snowy surface.

A sliding ski lift connects pulleys installed at both terminals at the foot of the mountain and at the top of the mountain, and circulates the cable in an endless manner. The winder has a built-in spiral spring so that the tow rope can be expanded and contracted. That is, as shown in FIGS. 1a and 1b, the conventional winding device 1 is equipped with a box 2 that is suspended from a cable using a suspension machine and a cable gripping machine, and both ends of the box 2 are rotatable by the box 2. It has a supported shaft 3. An inner end 5 of a spiral spring 4 and a reel 7 are fixed to the shaft 3. The spiral spring 4 has an inner end 5 fixedly connected to the shaft 3 as described above, and then wound outward in a spiral shape, and an outer end 6 fixed to the inner surface of the box 2. Further, the reel 7 is fixed concentrically with the shaft 3 so as to rotate together with the shaft 3, and one end of a traction cable 8 is fixed to the periphery of the reel 7, and then wound and wound. The tow rope 8 is guided to the outside of the box 2 via the inlet 11 of the box 2,
A stake 9 is connected to the other end.

In Fig. 1a, the spiral spring relaxes due to its elastic restoring force and generates a torque in the direction of arrow 12 on the shaft 3, winds up the towing line 8 onto the reel 7, and the stay 9 is retracted into the introduction port 11. This state is shown when the vehicle is not transporting passengers.

When transporting a passenger, as shown in FIG.
The tow rope 8 is deferred and extended while rotating in the direction. As the shaft 3 rotates, the spiral spring 4 is tightened and elastic restoring force or energy is accumulated, and when the passenger gets off the vehicle, the spiral spring 4 is relaxed and the tow rope is released again as in the case shown in FIG. 1a. 8 is rolled up, and the stake 9 is rolled up.

The winder 1 having such a structure is generally required to have the following characteristics. That is,
When a passenger gets on board, the passenger first waits at the landing, pulls out the stays 9 from the winder 1 that moves along with the cable, and puts it against the buttocks to prepare for towing. It is necessary that the passenger can be pulled out easily, or that the traction force on the passenger is weak, and that the traction force is increased after the passenger prepares for the above-mentioned tow slide, and at this time the passenger is forced to start the tow slide, and from then on the traction force increases. It is preferable that the speed of the tow rope is gradually increased so that the tow skiing speed and the rope speed are approximately equal when the tow rope finishes being stretched, since the passengers are smoothly accelerated. When the stake 9 is retracted after being wound up, if the retraction speed exceeds a certain limit, the stay 9 will collide with the winder inlet 11 at the end of winding, creating a shock.
This will cause the rope gripping device and winding device to swing, causing damage and operational problems, so it is necessary to limit or control the speed of the tow rope so that it does not become excessive.

In response to such demands, various countermeasures have been proposed and implemented. For example, a centrifugal brake is attached to the take-up device, and the take-up reel 7 has a special shape so that the effective radius is large in the first half of the unwinding operation, and the effective radius becomes small in the latter half of the unwinding operation, thereby increasing the traction torque. As the size increases, some devices are designed to increase the traction force by controlling the centrifugal brake to prevent the rotational speed of the take-up reel from increasing, or the centrifugal brake is equipped with an air damper, an oil damper, etc. , some have been devised to delay the start of centrifugal brake operation. However, these conventional speed regulating methods and devices do not fully satisfy the above-mentioned required characteristics, and are complicated in structure and difficult to adjust.

The present invention has been made in view of the above-mentioned circumstances, and includes a method for winding up a tow rope or stay,
It is an object of the present invention to provide a speed regulating device for a winder of a sliding ski lift that can optimally adjust the payout speed.

Hereinafter, details of the present invention will be explained with reference to drawings showing embodiments. In the embodiments described below, a pipe is used as a specific example of the flow path shown in the claims of the utility model registration.

In Figures 2a and b, 51 is a winder;
The winder 51 includes a box 52 and a pump 53. A spiral spring 55 is attached to the input shaft 54 of the pump 53.
Reel 5 for winding up the inner end 56 and tow line 58 of
7 is fixedly installed, and the input shaft 54 is rotatable. At the lower end of the tow rope 58 is a stake 5.
9 is attached. A pipe line is formed in two directions from the pump 53, and the pipe line includes variable throttle valves 61 and 62 for adjusting the flow rate by setting a required value in advance, and a delay stop valve 63 that operates with a delay to close the pipe line. is included.

The delay stop valve 63 has an elongated cylindrical sliding chamber 64 with a smooth inner surface, and a ball 65 is disposed within the sliding chamber 64.
4 is reversibly slidably sealed from one end 66 to the other end. One end 66 of the sliding chamber 64 is equipped with a stopper 68 having a needle-like tip that can be adjusted to move in the longitudinal direction and fixed at a desired position.
The tip of the stopper 68 moves inside the sliding chamber 64 with a ball 65.
When the ball 65 slides from the other end 67 to the one end 66, the ball 65 comes into contact with it and is stopped.

By connecting the plurality of valves as described above and the pump 53,
Lay out the pipes as follows.

The pipe line 69 connected to the pump 53 is connected to the branch point 76
It branches into two directions, one end being connected to the variable throttle valve 61 via a conduit 71, and further connected to the other end 67 of the delay stop valve 63 via a conduit 72.
A pipe line 73 branched at the branch point 76 is connected near one end 66 of the delay stop valve 63. The conduit 73 has fluid resistance. Such fluid resistance in the conduit 73 may be achieved by fluid friction in the conduit 73, or by providing the conduit 73 with a fixed or variable restriction 89. The maximum value of the fluid resistance of the conduit 61 adjusted by the variable throttle valve 61 is smaller than the fluid resistance of the conduit 73. Further, a separate conduit 74 is connected to the vicinity of one end of the delay stop valve 63, and the conduit 74 passes through the variable throttle valve 62.
5 to the pump 53. In this way, the pump 53, the variable throttle valves 61, 62, and the delay stop valve 63 are connected, and the pipes 69, 71, 7 are connected.
2, 73, 74, and 75 form a closed loop 78, and the loop 78 is filled with hydraulic oil.

In such a circuit, the pump 53 includes:
A reversible rotary positive displacement pump such as a gear pump is suitable.

Further, the delay stop valve 63 has a sliding chamber 64.
Depending on the position of the inner ball 65, the following effects are achieved.

That is, when the ball 65 is in contact with the other end 67 of the sliding chamber 64 [the ball 65' in FIG.
In the state of the ball 65 in Figure b], the ball 65 blocks the flow of hydraulic oil from the sliding chamber 64 to the pipe 72, but on the contrary, if the hydraulic oil is sent from the pipe 72 in the direction of the sliding chamber 64. The ball 65 is pushed inside the sliding chamber 64 toward one end 66 by the pressure of the hydraulic oil along with the flow of the hydraulic oil, and the flow of the hydraulic oil is allowed until the ball 65 comes into contact with the stopper 68. ing.

Conversely, when the ball 65 is in contact with the stopper 68 at one end 66 of the sliding chamber 64 [the ball 65 in FIG.
or the state of the ball 65'' in FIG.
The ball 65 prevents the hydraulic oil from flowing from the sliding chamber 64 to the conduit 74, but when the hydraulic oil is sent from the conduit 74 toward the sliding chamber 64, the ball 65 flows inside the sliding chamber 64 at the other end. The ball 65 is pushed toward the other end 67 by the pressure of the hydraulic oil along with the flow of the hydraulic oil.
The hydraulic oil is allowed to flow until it comes into contact with the

Furthermore, as mentioned above, the delay stop valve 63 has a stopper 68 at one end 66, but the stopper 68 not only stops the ball 65 by contacting it, but also
It also has another function. That is, ball 6
5 comes into contact with the stopper 68, there is a gap 77 between the ball 65 and the one end 66, and the stopper 68
The void 7 formed by adjusting the position of
The size of 7 can be changed. Therefore, when the ball 65 is in contact with the stopper 68, the flow rate of the hydraulic oil from the pipe 73 to the pipe 74 or from the pipe 74 to the pipe 73 can be adjusted. It is made possible.

The operation of the winder of the sliding ski lift constructed as described above when transporting passengers will be described below.

FIG. 2a illustrates the case where a passenger is on board and the towline 58 is deferred together with the stay 59.

When the passenger pulls out the stake 59, the tow line 58
is reeled back from reel 57 and stretched,
The input shaft 54 is rotated in the direction of arrow 79, and the spiral spring 55 is wound up against the elastic restoring torque. As the input shaft 54 rotates, the hydraulic oil in the pipe loop 78 is sent out in the direction of the arrow 81.
At the branch point 76, the pipe line 71, the variable throttle valve 61,
A path leading to the delay stop valve 63 via the conduit 72 and one end 66 of the delay stop valve 63 via the conduit 73.
The flow is divided into two routes. Inside the sliding chamber 64, the first ball 65 is in contact with the other end 67 (virtual position 65' of the ball), but from the conduit 72 to the sliding chamber 6
4, the ball 65 is pushed together with the hydraulic oil in the direction of arrow 82 until it abuts against the stopper 68. and during this transition period,
The hydraulic oil present in the sliding chamber 64 on the one end 66 side from the ball 65 is pushed out to the pipe line 74. On the other hand, the flow is divided at the branch point 76 and flows through the pipeline 73 to the delay stop valve 6.
The hydraulic oil that has reached one end 66 of 3 flows into the sliding chamber 64 while the ball 65 is moving from the other end 67 in the direction of arrow 82.
The ball 65 freely passes near one end 66 and joins with the hydraulic oil from the sliding chamber 64 to flow into the pipe 74. However, when the ball 65 completes its movement and comes into contact with the stopper 68, the gap 77 Since it flows into the conduit 74 through the narrowed cross-sectional area, the flow rate is restricted.

In this way, at the beginning of the tow cable extension process, the hydraulic oil separated at the branch point 76 joins again at the pipe line 74, passes through the flow rate regulating valve 62 and the pipe line 75, and then flows to the pump 53 in the direction of the arrow 83. However, during the course of the traction cable distraction, the ball 6
After 5 contacts the stopper 68, the branch point 7
Only a circuit is formed in which the reflux circulates from 6 to the pump 53 via a pipe 73, a gap 77, a pipe 74, a variable throttle valve 62, and a pipe 75, and this circuit is maintained continuously until the extension of the tow rope is finished. Ru.

Next, FIG. 2b illustrates a case where a passenger gets off the vehicle, the tow rope 58 is wound up by the reel 57, and the stake 59 is wound up.

When the passenger gets off the train and releases the stay 59, the spiral spring 55, which had been wound up, is loosened by the restoring torque, which causes the input shaft 54 to rotate in the direction of the arrow 84, and the reel 57 winds up the tow rope 58.
Stakes 59 are retracted. At this time, the pump 53 is driven by the rotation of the input shaft 54, and the hydraulic oil is sent out in the direction of the arrow 85. conduit 75
The hydraulic fluid sent out in the direction of arrow 85 passes through variable throttle valve 62 and pipe 74 to delay stop valve 63.
guided by. At this time, since the ball 65 is initially at the virtual position 65'' and is in contact with the stopper 68, the hydraulic oil reaches the pipe 73 through the flow that pushes the ball 65 in the direction of the arrow 86 and the gap 77. The hydraulic fluid flowing into the sliding chamber 64 flows while moving the ball 65 in the direction of the arrow 86.
It flows into the conduit 72, the variable throttle valve 61, and the conduit 71, and this flow continues until the ball 65 reaches the other end 67. On the other hand, the hydraulic oil that has flowed into the pipe line 73 through the gap 77 joins with the hydraulic oil that has passed through the sliding chamber 64 at the branch point 76, and is refluxed and circulated through the pipe line 69 in the direction of the arrow 87 to the pump 53. do. When the ball 65 comes into contact with the other end 67, the sliding chamber 64
Since the flow of the hydraulic oil is blocked, the circulation of the hydraulic oil continues only through the flow through the pipe line 73.

In this way, at the beginning of the tow rope winding process, the flow passing through the sliding chamber 64 and the flow passing through the conduit 73 merge at the branch point 76 and circulate.
After the ball 65 comes into contact with the other end 67 during the winding process of the tow rope, only a circuit passing through the conduit 73 is formed, and this circuit is maintained until the winding of the tow rope is completed. It is.

The operating characteristics of the apparatus that performs the above-described operation will now be qualitatively explained using FIG.

FIGS. 3a, 3b, and 3c illustrate the case where a passenger is on board and the tow rope 58 is extended. Third
In each of Figures a, b, and c, the horizontal axis represents the number of times N of winding the spiral spring 55, and the usage range C is from a state _N1 in which the spiral spring 55 is almost relaxed to a state _N2 in which it is almost tightened. Furthermore, assuming that the pull-out diameter of the tow rope 58 wound up by the reel 57 remains constant during the entire pulling period, N ₁ is equal to the length L ₁ when the tow rope is almost wound up. Correspondingly, N ₂ is the length of the tow rope when it is almost pulled out L ₂
It corresponds to

The vertical axes in FIGS. 3a, b and c indicate the torques T ₀ , T ₁ , T on the input shaft 54 or the traction forces F ₀ , F ₁ , F on the towline 58 in FIGS. 2a, b. Here, if T ₀ or F ₀ = torque or restoring force of the spiral spring, T ₁ or F ₁ = resistance torque or braking force of the hydraulic pipe, and T or F = traction torque or traction force, then T = T ₀ + T ₁ or F=F ₀ +F ₁
In other words, the torque or braking force generated by the spiral spring and the hydraulic pipe is the force that pulls the passenger.

FIG. 3a shows an example of the characteristics of a tightly wound spiral spring. Here, the torque T ₀ increases at an increasing rate of change from N ₁ (L ₁ ) to N ₂ (L ₂ ).

Next, FIG. 3b shows the change in the torque T ₁ or the traction force F ₁ generated by the resistance of the hydraulic line when the towline is pulled out. As described above, when the pulling out of the tow rope is started, the ball 65 shown in FIG. Although the flow rate is large and the torque generated by the resistance remains small, the ball 65 reaches the stopper 6.
8, the delay stop valve 63 is closed, so the flow rate is reduced, and the torque or tractive force increases rapidly near N ₃ (L ₃ ), and this is maintained during the period up to N ₂ (L ₂ ). .

FIG. 3c is a superimposition of FIGS. 3a and 3b, and according to the relationship T=T ₀ +T ₁ or F=F ₀ +F ₁ , this becomes the passenger traction torque or traction force. That is, the initial N ₁ of the withdrawal of the towline
(L ₁ ), the torque T ₀ to traction force F ₀ of the spiral spring is relatively small, and the resistance torque T ₁ to traction force F ₁
It is also small, making it easy for passengers to pull up the stand and get ready for boarding. After required time N ₃
At around (L ₃ ), the traction torque or traction force is increased and the vehicle starts towing the passenger. Furthermore, as the tow rope is pulled out, the spiral spring is tightened from N ₃ (L ₃ ) to N ₂ (L ₂ ), increasing the traction torque or traction force, and around N ₂ (L ₂ ) The tow line has almost finished extending, and the passengers can be transferred to line operating speed without any shock.

Next, the case where the passenger gets off the vehicle and the tow cable is wound up will be explained as shown in FIGS. 4a, b, and c.
In each of FIGS. 4a, b, and c, the horizontal axis represents the number of windings N of the spiral spring or the pull-out length L of the tow cable, as in the case of FIG. 3. However, in the case of winding up the tow rope, the tow rope changes from the state N ₂ (L ₂ ) where it is almost pulled out to the state where it is almost rolled up.
The operation progresses toward N ₁ (L ₁ ). Further, the vertical axis indicates the torque T' (T ₀ , T' ₁ , T') or the traction force F' (F ₀ , F' ₁ , F') during winding up. Here, T ₀ or F ₀ = torque or restoring force of the spiral spring, T′ ₁ or F′ ₁ = resistance torque or braking force of the hydraulic line, and T′ or F′ = winding torque or winding force. For example, T′=T ₀ −T′ ₁ , F′=F ₀ −F′ ₁ ,
The traction torque or traction force for winding up the tow cable is obtained by subtracting the torque or braking force generated in the hydraulic pipe from the torque or traction force of the spiral spring.

Figure 4a shows an example of the characteristics of a close spiral spring,
This is the same as in Figure 3a. Here N ₂
As the traction cable is wound up from (L ₂ ) to N ₁ (L ₁ ), the torque T ₀ or the traction force F ₀ gradually decreases while decreasing the rate of change.

FIG. 4b shows the change in the torque T' ₁ or braking force F' ₁ generated by the resistance of the hydraulic line as the tow line is wound up. When the passenger exits the vehicle and releases the stay to begin winding up the tow cable, the ball 65 shown in FIG.
7, the flow rate is large and the absolute value of the torque T' ₁ or the braking force F' ₁ generated by the resistance remains small, but when the ball 65 reaches the other end 67, the delay stop valve 63 is blocked, the flow rate in the circuit is reduced, and the resistance torque decreases around N ₃ (L ₃ ).
The absolute value of T' ₁ or braking force F' ₁ increases. From then on,
This state is maintained with the flow rate being throttled during the period from N ₃ (L ₃ ) to N ₁ (L ₁ ). Figure 4c shows the fourth
The combination of figures a and b is the above T′=T ₀ −T′ ₁ ,
Due to the relationship F′=F ₀ −F′ ₁ , this is the winding torque T′ ₁
Or the winding force is F′. That is, at the initial stage of winding N ₂ (L ₂ ) of the tow rope, the restoring torque of the spiral spring is large, and the absolute value of the resistance torque T' ₁ or braking force F' ₁ is small, so the total winding torque T ' or the winding force F' is large, and winding can be started smoothly even when the stake released by the passenger comes into contact with the snow surface and winding resistance is large. When it accelerates in this way and moves from N ₂ (L ₂ ) to around N ₃ (L ₃ ), the flow rate in the hydraulic pipe is restricted, so the absolute value of resistance torque T' ₁ or braking force F' ₁ increases. However, the winding torque T' or the winding force F' decreases, and the winding speed is limited. After this, during the period from N ₃ (L ₃ ) to N ₁ (L ₁ ), the restoring torque T ₀ or the restoring force F ₀ gradually decreases, and the absolute resistance torque T' ₁ or the braking force F' ₁ decreases. Since the value continues to increase, the winding torque
The winding force T′ or the winding force decreases significantly and becomes almost zero at N ₁ (L ₁ ) when winding is almost completed.

Therefore, due to these characteristics, when retracting the stake, startup acceleration is performed smoothly at the beginning, the retraction speed is limited from the middle, and when winding is completed, the retraction speed is close to zero, and the stake is Desired operations can be performed without colliding with the winder inlet.

In order to fully utilize these functions and obtain the required characteristics, the valves may be adjusted, and this can be done as follows.

First, by adjusting the variable throttle valve 61 shown in FIGS. 2a and 2b, the flow rate of the delay stop valve 63 can be increased or decreased, so that the moving speed of the ball 65 can be adjusted. By this, in case of withdrawal, the third
The period from N ₁ (L ₁ ) to N ₃ (L ₃ ) in Figure a to the rise of the resistance torque or braking force can be increased or decreased, and in the case of winding, N ₂ in Figure 4 b can be increased or decreased.
It is possible to increase or decrease the period from (L ₂ ) to the rise of the absolute value of the resistance torque or braking force of N ₃ (L ₃ ).

Next, by adjusting the stopper 68 back and forth in the needle-shaped longitudinal direction, the stopping position of the ball 65 at one end of the sliding chamber 64 can be adjusted, and the gap 77 can be increased or decreased thereby. Road 7
3. The flow rate between the pipes 74 can be adjusted. Accordingly, in the case of a drawer, Fig. 3b
The resistance torque T ₁ between N ₃ (L ₃ ) and N ₂ (L ₂ ) of
The braking force F ₁ can be increased or decreased, and in the case of rolling, the resistance torque T' ₁ or the braking force between N ₃ (L ₃ ) and N ₂ (L ₂ ) in FIG. 4b can be increased or decreased. The absolute value of F′ ₁ can be increased or decreased.

Further, by adjusting the variable throttle valve 62, the flow rate of the entire hydraulic pipe is increased or decreased, the resistance torque T ₁ , T' ₁ or the braking force F ₁ , F' ₁ is increased or decreased, and the drawing speed or winding speed is adjusted. be able to.

If these adjustments are made in advance and used, the desired characteristics will be exhibited.

Note that this device utilizes the fluid resistance of the hydraulic conduit, and the fluid resistance of the conduit generally has the property of increasing as the flow velocity increases. This means that if the speed of the towline increases or becomes excessive during withdrawal or retraction, pump 53 of FIG.
As the rotation of the winder becomes faster and the speed of the hydraulic oil in the pipe increases, the resistance torque or braking force increases and has a regulating effect that limits the speed, which is extremely desirable due to the characteristics of the winder. You get something.

As described above, by using the structure of the sliding lift winder according to the present invention, the following effects can be obtained.

(i) When a passenger is on board, the towing cable is easily pulled out, and the traction force increases thereafter, resulting in good characteristics such as smooth acceleration.

(ii) When winding up the tow rope, acceleration is smooth and the stay does not collide with the winding device at the end of winding.

(iii) The operating time, torque, etc. can be adjusted by adjusting the valves.

(iv) Since it utilizes the fluid resistance of the conduit, a speed regulating effect works as the speed of drawing or winding increases.

It has extremely desirable features such as these, and greatly contributes to comfortable riding and safe operation of sliding lifts.

[Brief explanation of the drawing]

Fig. 1a is a perspective view illustrating the operation of a conventional winder, Fig. 1b is a perspective view illustrating the operation of a conventional winder, and Fig. 2a is a configuration of a winder according to the present invention. FIG. 2b is an explanatory diagram of the structure of the winder according to the present invention, FIG. A diagram showing the characteristics of torque or traction force in the case of pulling out, Figure 3c is a diagram showing the characteristics of torque or traction force in the case of pulling out the tow line, and Figure 4a is a diagram showing the characteristics of torque or traction force in the case of pulling out the tow line. Figure 4b is a diagram showing the characteristics of torque or traction force in the case of towing rope winding, and Figure 4c is a diagram showing the characteristics of torque or traction force in the case of towing rope reeling. It is a diagram. 51... winder, 52... box, 53...
Pump, 54... Input shaft, 55... Spiral spring, 5
7...Reel, 58...Tow line, 57...Stay, 61...Variable throttle valve, 62...Variable throttle valve, 63...Delay stop valve, 64...Sliding chamber,
65...Ball, 68...Stopper, 77...Gap.

Claims (1)

[Scope of Claims] 1. A pump in which one end of a spring member having an elastic restoring force and a traction cable take-up pulley are fixed to an input shaft, a cylinder and a piston member slidably engaged in the cylinder. a first chamber is formed between one end of the cylinder and one pressure receiving surface of the piston, and a second chamber is formed between the other end of the cylinder and the other pressure receiving surface of the piston. The first chamber and the second chamber are formed by displacing the piston in the cylinder in response to hydraulic pressure.
a delay stop valve having a variable volume of the chamber of the delay stop valve; a first flow path reaching one end, and a second flow path having a variable throttle valve branching from the first flow path and having a variable volume of the delay stop valve.
a branch passage connected to the chamber, and a second flow passage reaching the pump from the other end of the first chamber,
The maximum value of the fluid resistance of the branch passage adjusted by the variable throttle valve is configured to be smaller than the fluid resistance of the first flow passage, and the variable throttle valve is adjusted to separate the branch passage from the first passage. 1. A speed governor for a winder of a sliding ski lift, characterized in that it is configured to adjust the relative flow rate with a first flow path. 2. A stopper member that can move forward and backward within the cylinder is provided, and the stopper member is configured to determine the minimum volume of the first chamber by regulating the stop position of the piston member. A speed regulating device for a winder of a sliding ski lift according to claim 1. 3. Claim 1 or 2, characterized in that a variable throttle valve is disposed in the second flow path.
A speed regulating device for a winding device of a sliding ski lift as described in 2.