Can I Put Bigger Tires On My Zero Turn Mower. Zero turn front wheel

US8167324B2. Caster wheel suspension for a zero-turn mower. Google Patents

Publication number US8167324B2 US8167324B2 US12/761,926 US76192610A US8167324B2 US 8167324 B2 US8167324 B2 US 8167324B2 US 76192610 A US76192610 A US 76192610A US 8167324 B2 US8167324 B2 US 8167324B2 Authority US United States Prior art keywords zero shock turn mower spring front axle Prior art date 2010-04-16 Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.) Expired. Fee Related. expires 2030-07-19 Application number US12/761,926 Other versions US20110254241A1 ( en Inventor Alan F. Piontek Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.) Great Plains Manufacturing Inc Original Assignee Great Plains Manufacturing Inc Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.) 2010-04-16 Filing date 2010-04-16 Publication date 2012-05-01 2010-04-16 Application filed by Great Plains Manufacturing Inc filed Critical Great Plains Manufacturing Inc 2010-04-16 Priority to US12/761,926 priority Critical patent/US8167324B2/en 2010-04-16 Assigned to GREAT PLAINS MANUFACTURING, INCORPORATED reassignment GREAT PLAINS MANUFACTURING, INCORPORATED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: PIONTEK, ALAN F. 2011-10-20 Publication of US20110254241A1 publication Critical patent/US20110254241A1/en 2012-05-01 Application granted granted Critical 2012-05-01 Publication of US8167324B2 publication Critical patent/US8167324B2/en 2017-09-22 Assigned to GREAT PLAINS MANUFACTURING, INCORPORATED reassignment GREAT PLAINS MANUFACTURING, INCORPORATED RELEASE BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: WELLS FARGO BANK, NATIONAL ASSOCIATION Status Expired. Fee Related legal-status Critical Current 2030-07-19 Adjusted expiration legal-status Critical

Images

Classifications

• B — PERFORMING OPERATIONS; TRANSPORTING
• B60 — VEHICLES IN GENERAL
• B60G — VEHICLE SUSPENSION ARRANGEMENTS
• B60G3/00 — Resilient suspensions for a single wheel
• B60G3/01 — Resilient suspensions for a single wheel the wheel being mounted for sliding movement, e.g. in or on a vertical guide

• B — PERFORMING OPERATIONS; TRANSPORTING
• B60 — VEHICLES IN GENERAL
• B60G — VEHICLE SUSPENSION ARRANGEMENTS
• B60G9/00 — Resilient suspensions of a rigid axle or axle housing for two or more wheels
• B60G9/02 — Resilient suspensions of a rigid axle or axle housing for two or more wheels the axle or housing being pivotally mounted on the vehicle, e.g. the pivotal axis being parallel to the longitudinal axis of the vehicle

• F — MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
• F16 — ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
• F16F — SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
• F16F7/00 — Vibration-dampers; Shock-absorbers

• B — PERFORMING OPERATIONS; TRANSPORTING
• B60 — VEHICLES IN GENERAL
• B60G — VEHICLE SUSPENSION ARRANGEMENTS
• B60G2200/00 — Indexing codes relating to suspension types
• B60G2200/30 — Rigid axle suspensions
• B60G2200/32 — Rigid axle suspensions pivoted
• B60G2200/322 — Rigid axle suspensions pivoted with a single pivot point and a straight axle

• B — PERFORMING OPERATIONS; TRANSPORTING
• B60 — VEHICLES IN GENERAL
• B60G — VEHICLE SUSPENSION ARRANGEMENTS
• B60G2202/00 — Indexing codes relating to the type of spring, damper or actuator
• B60G2202/10 — Type of spring
• B60G2202/12 — Wound spring

• B — PERFORMING OPERATIONS; TRANSPORTING
• B60 — VEHICLES IN GENERAL
• B60G — VEHICLE SUSPENSION ARRANGEMENTS
• B60G2204/00 — Indexing codes related to suspensions per se or to auxiliary parts
• B60G2204/40 — Auxiliary suspension parts; Adjustment of suspensions
• B60G2204/423 — Rails, tubes, or the like, for guiding the movement of suspension elements
• B60G2204/4232 — Sliding mounts

• B — PERFORMING OPERATIONS; TRANSPORTING
• B60 — VEHICLES IN GENERAL
• B60G — VEHICLE SUSPENSION ARRANGEMENTS
• B60G2300/00 — Indexing codes relating to the type of vehicle
• B60G2300/08 — Agricultural vehicles
• B60G2300/084 — Ridable lawn mowers

Abstract

A zero-turn mower comprising a zero-turn mower frame, a front axle coupled to the zero-turn mower frame, first and second caster wheel assemblies, and first and second front shock assemblies. The front shock assemblies rotatably and telescopically couple the caster wheel assemblies to the front axle, thereby providing vertical shock absorption. The front axle may be a floating axle that is pivotably coupled to the mower frame and/or the shock assemblies may define an internal spring-receiving chamber that is substantially isolated from the external environment. Such a zero-turn mower may provide a smoother ride and may require less maintenance and repair than conventional zero-turn mowers.

Description

Zero-turn mowers are designed to have a turning radius that is essentially zero inches. Zero-turn mowers typically have two large tires in the back, and two caster wheels in the front. The motor and transmission of the mower allows the back tires to rotate forwards and backwards independently of one another for maximum maneuverability.

Zero-turn mowers can experience a great amount of wear and tear due to jolting and uneven weight distribution on its wheel assemblies and frame caused by driving over bumps or dips in the ground, particularly if one front tire passes over a bump or dip while the other tire does not. Some zero-turn mowers have springs placed between a front axle to which the front caster wheels are attached and a frame of the mower to dampen the effects of these jolts. However, these springs are generally open to the surrounding environment and therefore subject to build up of grass, dirt, or other foreign contaminates and may be susceptible to rusting. Additionally, the springs between the frame and the front axle are not always sufficient in addressing jolting between the caster wheels and the front axle.

Some partially enclosed shock assemblies for caster wheels have been developed to provide shock absorption between the caster wheels and the component to which it is attached, though these shock assemblies have not been used for zero-turn mowers and are not fully enclosed. For example, some of these caster wheel shock assemblies provide openings through which a guide rod may slide, therefore allowing foreign contaminants to enter through said openings as the guide rod slides outward and inward therethrough.

The present invention solves some of the above-described problems and provides a distinct advance in the art of zero-turn mower shock absorption. Embodiments of the present invention provide a zero-turn mower comprising a zero-turn mower frame, a first caster wheel assembly, a second caster wheel assembly, and a front suspension system connecting the caster wheel assemblies to the frame. The front suspension system may comprise a floating front axle pivotably connected to the zero-turn mower frame, a first shock assembly rotatably and telescopically connecting the first caster wheel assembly to a first end of the floating front providing vertical shock absorption therebetween, and a second shock assembly rotatably and telescopically connecting the second caster wheel assembly to a second end of the floating front axle and providing vertical shock absorption therebetween.

The shock assemblies may each comprise an outer member and an inner member at least partly disposed in the outer member and may cooperatively define an internal spring-receiving chamber in which a compression spring may be received. The spring may bias the inner and outer members away from one another. The outer member may be rigidly coupled to the axle and the inner member may be rigidly coupled to one of the first or second caster wheel assemblies, with the inner and outer members being rotatably and telescopically coupled with each other. The spring-receiving chamber may be substantially isolated from the environment external to the first and second shock assemblies. The shock assemblies may also each comprise a retention rod extending through the center of the spring for limiting movement of the outer and inner members away from one another.

In use, an operator may drive a zero-turn mower over a surface comprising a bump and may pass a first front wheel of the zero-turn mower over the bump without passing a second front wheel of the zero-turn mower over the bump, causing substantially equal compressive force on a first shock assembly associated with the first front wheel and a second shock assembly associated with the second front wheel, and causing an axle coupled to the first and second shock absorbers to rotate a first end of the axle proximate the first wheel upward and a second end of the axle proximate the second wheel downward.

This summary is provided to introduce a selection of concepts in a simplified form that are further described below in the detailed description. This summary is not intended to identify key features or essential features of the claimed subject matter, nor is it intended to be used to limit the scope of the claimed subject matter.

Other aspects and advantages of the present invention will be apparent from the following detailed description of the embodiments and the accompanying drawing figures.

Embodiments of the present invention are described in detail below with reference to the attached drawing figures, wherein:

FIG. 1 is a perspective view of a zero-turn mower constructed according to an embodiment of the present invention;

FIG. 3 is a fragmentary cross-sectional view of a shock assembly of the zero-turn mower of FIG. 1 in a fully extended position;

FIG. 4 is a fragmentary cross-sectional view of the shock assembly of FIG. 3 in a compressed position;

FIG. 5 is a fragmentary elevation view of the zero-turn mower of FIG. 1 positioned on level ground; and

The drawing figures do not limit the present invention to the specific embodiments disclosed and described herein. The drawings are not necessarily to scale, emphasis instead being placed upon clearly illustrating the principles of the invention.

The following detailed description of the invention references the accompanying drawings that illustrate specific embodiments in which the invention can be practiced. The embodiments are intended to describe aspects of the invention in sufficient detail to enable those skilled in the art to practice the invention. Other embodiments can be utilized and changes can be made without departing from the scope of the present invention. The following detailed description is, therefore, not to be taken in a limiting sense. The scope of the present invention is defined only by the appended claims, along with the full scope of equivalents to which such claims are entitled.

FIGS. 1 and 2 show a zero-turn mower 10 comprising a zero-turn mower frame 12, a first caster wheel assembly 14, a second caster wheel assembly 16, and a front suspension system 18 connecting the first and second caster wheel assemblies 14,16 to the mower frame 12. The front suspension system 18 comprises a pivotable floating front axle 20, a first shock assembly 22 attaching the first caster wheel assembly 14 to the front axle 20 and configured for vertical shock absorption, and a second shock assembly 24 attaching the second caster wheel assembly 16 to the front axle 20 and configured for vertical shock absorption. The combination of the pivoting provided by front axle 20 and vertical shock absorption provided by the first and second shock assemblies 22, 24 allows the zero-turn mower 10 to pass over a bump or dip in the ground with minimal effect on the zero-turn mower frame 12, as later described herein.

The first and second caster wheel assemblies 14, 16 may comprise a first and second fork 26,28 respectively and a first and second wheel 30,32 respectively. The wheels 30,32 may be rotatably attached to the forks 26,28 and may rotate around a horizontal axis substantially parallel to the ground. The forks 26,28 may be formed of metal or any other substantially rigid material and may be fixedly coupled to the first or second shock assembly 22,24. The wheels 30,32 may be formed of any combination of rubber, metal, plastic, and the like.

The floating front axle 20 may be formed of a rigid body and may comprise a first end 34, a second end 36 located opposite of the first end 34, and a pivot point 38 at which the axle 20 is pivotably attached to the mower frame 12 using any pivotable connection means known in the art. The pivot point 38 may be a point or region of the axle 20 located and/or centered between the first and second ends 34,36. The front axle 20 may pivot freely (i.e., without being biased towards a particular position) relative to the frame 12 in a substantially vertical manner, up and down, toward and away from the ground about a substantially horizontal axis substantially parallel to the ground. In some embodiments of the invention, the front axle 20 may be prevented from pivoting in a substantially horizontal manner, right to left, about a vertical axis substantially perpendicular with the ground.

The first and second shock assemblies 22,24 may each be configured to provide vertical shock absorption. The first shock assembly 22 may rotatably couple the first caster wheel assembly 14 to the first end 34 of the floating front axle 20 and the second shock assembly 24 may rotatably couple the second caster wheel assembly 16 to the second end 36 of the floating front axle 20.

The shock assemblies 22,24 are depicted in detail in FIGS. 3 and 4. Though FIGS. 3 and 4 only illustrate the first shock assembly 22, the first and second shock assemblies 22,24 may be substantially identical in configuration and may comprise the same components, as described herein. As depicted in FIGS. 3 and 4. each of the shock assemblies 22,24 may comprise an outer member 40 fixed to the floating front axle 20 and an inner member 42 rotatably and/or telescopically connected to the outer member 40 and fixedly attached to the first or second fork 26,28. The outer and inner members 40,42 may cooperatively form an internal spring-receiving chamber 44.

The shock assemblies 22,24 may each further comprise a compression spring 46 housed within the internal spring-receiving chamber 44 and a retention rod 48 extending through the center of the spring 46. The shock assemblies 22,24 may also comprise a thrust bearing 60 disposed within the spring-receiving chamber 44 and between a lower end of the spring 46 and an elastomeric pad 62 that contacts an interior flange 66 of the inner member 42. Furthermore, the shock assemblies 22,24 may comprise a flexible bellows 50 extending between the bottom of the outer member 40 and the top of the first or second fork 26,28; one or more bushings 52, housed between the outer and inner members 40,42 to facilitate rotation and telescoping therebetween; a lubricant space 56 cooperatively defined by the outer and inner members 40,42 and the bushing(s) 52; and a lubricant inlet 58 formed in the outer member 40 to insert lubricant into the lubricant space 56.

The outer member 40 may be a rigid hollow part of any shape and configuration, such as a cylinder substantially closed at one end, and may comprise a sidewall 64. The space within the hollow outer member 40 may be referred to herein as a first interior space 76. The inner member 42 may be a rigid hollow part of any shape and configuration, such as a cylinder, and may comprise a sidewall 70. The outside diameter of the inner member sidewall 70 may be smaller than the inside diameter of the outer member sidewall 64, such that the inner member 42 may axially slide up and down within the outer member 40.

The large space defined within the upper portion of the hollow inner member 42 may be referred to herein as a second interior space 78. The second interior space 78 and the first interior space 76 cooperatively form the internal spring-receiving chamber 44. The smaller space defined near the bottom of the inner member 42 may be referred to herein as a rod travel space 72. The inner member 42 may comprise a cap 74 covering an open end of the rod travel space 72 and/or configured to substantially seal the rod travel space 72 from the external environment at the lower end of the inner member 42.

The compression spring 46 is operable to bias the outer member 40 away from the inner member 42. The compression spring 46 may be made of any compressible, resilient material and may reside within the internal spring-receiving chamber 44. In one embodiment of the invention, the compression spring 46 may be an elongated piece of metal coiled or spiraled in a uniform manner. The minimum and maximum length of the compression spring 46 when it is compressed and extended respectively may be based on the desired amount of shock absorption travel for each of the first and second shock assemblies 22,24. A maximum width or diameter of the cylindrically-coiled compression spring 46 may be approximately equal to and/or slightly smaller than the first cross-sectional diameter of the second interior space 78.

One end of the compression spring 46 may be fixedly attached to the outer member 40 or the inner member 42. In the embodiment illustrated in FIGS. 3 and 4. the upper end of the compression spring 46 is fixedly attached to the closed end of the outer member 40, while the lower end of the compression spring 46 pushes against the upwardly-facing interior flange 66 of the inner member 42. As shown in FIGS. 3 and 4. the thrust bearing 60 and elastomeric pad 62 may be positioned between the spring 46 and the first interior flange 66 to allow rotation of the inner member 42 relative to the spring 46 and the outer member 40. The thrust bearing 60 depicted in FIGS. 3 and 4 is a three-component thrust assembly consisting of a plastic thrust washer sandwiched between two steel outboard races.

The retention rod 48 may be configured for limiting movement of the outer and inner members 40,42 away from one another. The retention rod 48 may be made of any substantially rigid material and may extend through and along a center axis of the outer member 40, the inner member 42, the compression spring 46, the thrust bearing 60, and/or the elastomeric pad 62. The thrust bearing 60 and the elastomeric pad 62 may each comprise holes located through the center thereof with a diameter at least slightly greater than the diameter of the retention rod 48. Additionally, the retention rod 48 may have a diameter slightly smaller than the cross-sectional diameter of an intermediate space 54 extending between the second interior space 78 and the travel rod space 72. In some embodiments of the invention, the upper end of the retention rod 48 may be attached to the outer member 40. For example, the retention rod 48 may comprise screw threads 82 at one end to fixedly attach to the outer member 40 via an outer nut 83 and an inner nut 85. specifically, in the embodiment depicted in FIGS. 3 and 4. the upper threaded end of the retention rod 48 extends through an opening in the upper end of the outer member 40 and is rigidly secured to the outer member 40 by tightening the outer nut 83 and thereby compressing the upper end of the outer member 40 between the outer and inner nuts 83,85. Furthermore, the lower end of the retention rod 48 may have a retention rod head 80 attached or integrally formed thereon. The retention rod head 80 may have a width or diameter slightly smaller than the cross-sectional diameter of the rod travel space 72 but larger than the cross-sectional diameter of the intermediate space 54, such that the retention rod head 80 rests on a downwardly-facing interior flange 68 of the inner member 42 when the compression spring 46 is extended to its maximum allowed length. Thus, the maximum extension length of the compression spring 46 is limited by the length of the retention rod 48, the location of the interior flange 68, and/or the distance of the retention rod head 80 relative to the point at which the compression spring 46 attaches to the outer member 40.

The flexible bellows 50 may comprise an upper end 84 fixedly coupled to the outer member 40 and a lower end 86 disposed around the inner member 42 and permitting rotation of the inner member 42 relative to the bellows 50. The bellows 50 may be pleated or otherwise configured for expansion and compression. A bellows hold-down ring 90 attached to, within, and/or positioned at the bottom of the bellows 50 may be configured to maintain contact between the bellows 50 or the bellows hold-down ring 90 and the first or second fork 26,28 regardless of the vertical movement between the inner and outer members 40,42 while still allowing the first or second fork 26,28 and the inner member 42 to rotated relative to the bellows 50 and the bellows hold-down ring 90. For example, the bellows hold-down ring 90 may be sufficiently heavy to maintain contact with the first or second fork 26,28 or the bellows hold-down ring 90 may be a thrust bearing. The bellows 50 shields the inner member 42 and the spring 46 from the external environment, protecting them from foreign particles, dirt, and/or grass.

The flexible bellows 50 may also house a bellows spring 88 coiled around and outward of the inner member 42 and fixed to the lower end of the outer member 40. The lower end of the bellows spring 88 may contact and exert a downward force on the bellows hold-down ring 90. The bellows spring 88 may assist in maintaining the integrity of the bellows 50 and may function to maintain contact between the bottom of the bellows 50 and the top of the forks 26,28 as the forks 26,28 move relative to the outer member 40.

The bushing 52 is disposed between the inner and outer members 40,42 and is configured to provide a low-friction surface for smooth rotation and telescoping vertical movement between the outer and inner members 40,42. In some embodiments of the invention, only one bushing 52 is used, while in other embodiments of the invention, two or more bushings may be used. The lubricant space 56 defined by a void in the bushing 52 may be configured such that lubricant may be placed therein. The lubricant inlet 58 may be formed in the sidewall 64 of the outer member 40 and configured to provide an opening through which the lubricant may be inserted. The lubricant inlet 58 may be positioned in fluid communication with the lubricant space 56, such that lubricant passed through the lubricant inlet 58 subsequently passes into the lubricant space 56. The lubricant may spread from the lubricant space 56 along the inner surface of the outer member sidewall 64 and the outer surface of the inner member sidewall 70 and may be contained within the first or second shock assemblies 22,24 by the bellows 50 and/or the bellows hold-down ring 90.

In use, the zero-turn mower 10 may be driven over level terrain as in FIG. 5 or uneven terrain as in FIG. 6. For example, the zero-turn mower 10 may drive over a surface comprising a bump, as illustrated in FIG. 6. and pass the first wheel 30 over the bump without passing the second wheel 32 over the bump, thereby causing substantially equal compressive force on the first shock assembly 22 and the second shock assembly 24. Specifically, passing the first wheel 30 over the bump without passing the second wheel 32 over the bump may cause the axle 20 to rotate the first end 34 of the axle 20 upward and the second end 36 of the axle 20 downward. Additionally or alternatively, the surface may comprise a dip and the mower 10 may drive over the surface, passing the first wheel 30 over the dip without passing the second wheel 32 over the dip, thereby causing substantially equal extension of the first shock assembly 22 and the second shock assembly 24. The pivoting motion of the axle 20 combined with the vertical shock absorption of the shock assemblies 22,24 provides better weight distribution and shock absorption than either component could provide on its own.

For example, if the first wheel 30 passes over a bump that is two inches higher than the surface over which the second wheel 32 is passing over, the first shock assembly 22 may experience approximately one inch of compression while the first end 34 of the axle 20 may rotate upward approximately one inch. Simultaneously, the second end 36 of the axle 20 may respond by rotating downward approximately one inch, which subsequently may cause the second shock assembly 24 to compress by approximately one inch. Advantageously, the rotation of the axle 20 allows for equal amounts of compression on each of the shock assemblies 22,24. By equally distributing the compressive or expansive forces across the two shock assemblies 22,24, neither shock assembly is subject to as great an expansion or compression as would otherwise be experienced in this situation, allowing for a generally smoother ride on the zero-turn mower 10 and less wear and tear on its parts.

Although the invention has been described with reference to the embodiments illustrated in the attached drawing figures, it is noted that equivalents may be employed and substitutions made herein without departing from the scope of the invention as recited in the claims.

Can I Put Bigger Tires On My Zero Turn Mower?

Nothing beats zero turn mowers when it comes to efficiency and speed while tending to a relatively large lawn. However, a lot of owners wonder if they can improve the performance of their mower by upgrading some of its parts, such as the wheels.

Can I Put Bigger Tires On My Zero Turn Mower?

The quick answer is yes! However, to make the most out of this upgrade, you have to keep a few variables and aspects in mind, such as; turn radius, maneuverability, deck, etc.

Keep on reading if you want to know these aspects as well as the pros and cons of putting bigger tires on your zero-turn mower!

What is the Standard Size of a Zero Turn Mower Tire?

There’s no universal agreement between lawn mower brands about the size of the zero turn mower tires. However, in most cases, size 15x 6.00-6 is probably the most commonly used one.

The tread pattern design is also similar among lawn mower tires, as most brands use a turf saver pattern, which is specifically designed to minimize the tear while moving over the grass to keep the height consistent.

Breaking Down Zero Turn Mower Tires Measurement System

In order to find out more about lawn mower tires, you should first understand the measurement system they use. For example, if you have a 15×6.00-6 tire, what exactly does that mean?

The first number, which is 15 here, represents the tire’s height when the wheel is properly inflated and not under any load. The larger this number is the larger the tire’s diameter.

The second number, which is 6.00, represents the horizontal width of the tire. This means that the tread width of the tire in question here is 6 inches.

The final number, which is six after the hyphen (-), represents the size of the metallic rim on which the tires will be fitted. It is measured in inches, and the number should always be smaller than the width of the tires.

Is It Possible to Install Larger Tires on Zero Turn Mowers?

As you can see from the previous example, a “larger tire” can indicate a larger tread width of the same length, a larger diameter of the same width, or larger width and height.

In this section, we’ll discuss all these possibilities and whether they’re commonly in zero turn mowers:

Larger Tread Width

Installing tires with larger tread width is relatively common. In that case, the upgraded tires are usually installed on the rear set of wheels but can also be installed on all wheels.

In that case, the overall diameter of the tires should remain equal to the stock wheel. So, for example, if the stock wheel is 15×6.00-6 inches, the rear wheels could be 15×8.00-6 inches without issues.

Larger Diameter

Installing larger tires is popular for many zero turn mowers. Since the wheels have a larger diameter, you need to install these tires on all four wheels in order to keep the zero turn mower at a level position for consistency while cutting the grass.

Additionally, you’ll need to modify the mower deck by lowering it so that you can adjust the height of the machine while cutting.

Larger Diameter and Width

This one is relatively uncommon but can be done if your zero turn mower spins a lot while mowing on slippery grass.

It can also help evenly distribute the mower’s weight when working on relatively soft lawns.

Why Using Bigger Tires on Zero Turn Mowers Is a Good Idea?

The main advantage of installing a larger tire on your zero turn mower is that it enhances the mower’s traction.

For instance, a zero-turn mower is a perfect machine for cutting dry grass on relatively hard and level terrain. However, if it occasionally rains where you live or your soil is a bit soft, achieving these perfect conditions can be pretty tricky.

In that case, increasing the width of the rear wheels of a zero turn mower or using larger ones, in general, can help in improving the traction of the mower on the lawn.

Additionally, using these wheels makes it easier to use the mower over different terrains, like in snowy conditions.

Important Aspects to Consider Before Putting Larger Tires on Zero Turn Mowers

Using larger or wider tires on zero turn mowers comes with several benefits but can also come with several drawbacks.

To help you make the right decision for your case, let’s have a quick look at some of the critical aspects to consider before making this adjustment:

Your Turn Angle Will Be Increased

Turn angle stands for the minimum angle needed for turning. Ideally, the lower the turn angle of a mower, the more maneuverable it is.

As the name suggests, low turn angle is one of the significant advantages of zero turn mowers, as they’re capable of making up to 180-degree turns in any position.

By using wider tires, this turn angle will increase, which can be a significant hit to the value of the mower if you specifically bought it for the zero degree turn angle.

Deck Adjustment Is Critical to Maintain Mower’s Functionality

The engineering of a zero turn mower is greatly dependent on its height. While this may not be a problem if you only increase the width of the tires, it has a considerable impact on the functionality if you increase the height.

Larger tires result in a relatively higher lawn mower. This means that cutting the grass at a very low level can be impossible without proper adjustment to the mower deck.

As a general rule, you’ll need to lower the mower deck by as many inches as you’ve increased the height.

For example, if the new tires are 3 inches higher than the stock tires, you’ll need to adjust the deck so that it’s 3 inches lower to cancel the difference.

Yet, if you usually cut the grass when it’s relatively high and rarely need to cut it too short, you may get away with the tire upgrade without adjusting the deck.

Can I Put Smaller Tires on My Zero Turn Mower?

Ideally, the standard tires used in zero turn mowers are the lowest they can go. This means that you can only install a larger tire, but never a smaller one. For starters, you’re bound by the size of the rims.

Additionally, using smaller tires doesn’t add any real advantage to the zero turn mower like the previously mentioned upgrades, especially since you’ll also need to readjust the deck clearance in order to get the machine to work.

Smaller tires also put a lot of pressure on smaller wheels, which makes the mower slippery, harder to maneuver and tear the lawn noticeably while turning.

Conclusion

In the end, we hope that this guide helps you figure out the right thing when it comes to using a bigger tire on your zero turn mower.

Typically, installing a larger tire will generally improve your maneuvering and traction. This makes it a viable adjustment for those who don’t cut the grass too short and want better traction while operating the machine.

However, even with deck adjustment, the wider tires will come at the cost of a few aspects, mainly the turn angle, so you have to keep that in mind while adjusting your mower’s tire size or width.

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• Do Zero Turn Mowers Work on Uneven Ground and Rough Terrains?
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The Best Zero-Turn Mowers of 2023

These achieve the rare feat of making lawn mowing fun.

By Roy Berendsohn Published: Mar 1, 2023

When it comes to yard work, zero turn mowers do the impossible. They make lawn mowing fun. They accomplish this by putting unprecedented speed, control and maneuverability at the disposal of the person mowing the lawn. The so-called “zero turn” feature of these mowers converts a grass cutting machine into something akin to an amusement park ride. You steer the machine with two levers—the left lever controls the left wheel, the right lever the right wheel. With that steering setup, you can zoom over the landscape cutting straight lines, curves, or pivot the mower into and out of a corner. What’s not to like?

Read on to understand how these agile grass cutters work, how we go about testing them, and see some candidates that we’ve recently tested as well as some that we haven’t but that we think look particularly promising.

How Zero-Turn Mowers Work

A zero-turn riding mower consists of an operator platform, a frame and wheels, an engine (or battery bank), transmissions (or motors), and a pair of control levers commonly known as lap bars. In gas mowers, the engine powers a pulley system. One group of pulleys drives the blades, another group powers a pair of transmissions–one at each rear wheel. When you move the lap bar forward or back, you are directing the transmission to go faster, slower, or even turn the opposite way. When one drive wheel turns clockwise and the other counter clockwise, the mower pivots. When the wheels rotate at different rates, the mower turns in an arc-shaped path. When the lap bars are in the neutral position, the mower stops. Aside from a parking brake, there’s no other braking mechanism. Battery-powered zero-turn mowers work the same way, but have separate motors to drive the rear wheels and one for each blade inside the mower deck.

When it comes to transmission, most mowers have a Hydrogear EZT—a well-known and cost-effective residential-grade transaxle with a reputation for durability.

Some mowers use a deck stamped from one piece of steel, others use a deck fabricated from multiple pieces and welded together. A fabricated deck can be built from thicker steel at a lower cost than it would be able to be built otherwise. Once you’re talking about stamping metal as thick as 10 gauge (about 1⁄8 inch thick), the cost of stamping such a deck would push up the mower’s price beyond what most people are willing to pay. The decks in the mowers below range from 42 to 52 inches, a typical size in this class of product. When powered by these engines and the Hydrogear, these mowers will deliver a decent cut quality at their rated top speed of 7 mph. Note, however, that cut quality declines steeply if you maintain that speed in very thick grass or on uneven terrain.

As to the electric mowers, they represent the leading edge of the technology in this category. These are remarkable and expensive mowers powered by large-voltage lithium-ion batteries. If you’re interested in reducing mowing noise and simplifying your maintenance routine by eliminating gas and oil, they’re worth a look.

Selecting a Zero-Turn Mower

Everyone would like to select the biggest possible zero-turn mower with the hope of whittling a big grass cutting job down to size as quickly as possible. Reality usually intercedes because these machines are expensive and the wide range of options available today quickly drive up the cost. Roughly speaking, you start somewhere in the range of a mower with a 42-inch deck costing in the vicinity of 3200 to 3500 and move up in increments of 1000 to 1500 until you reach entry-level commercial-grade equipment that costs 7000 to 8000.

Again, speaking in terms of approximation, a mower with a 42-inch deck will cut a two-acre lot (that takes into account that the house, driveway, outbuildings and various landscape features are taking up some of that space). Use a mower with a larger deck to cut anything over two acres. But here’s the caveat. That entry-level ZTR mower (3200, say) with a 42-inch deck will wear out faster and need more maintenance than a mower with a 50-inch deck, a heavier frame, larger engine and higher quality transmissions, and thicker deck with more robust blade spindles, costing 4500.

In the simplest possible terms, you can cut a smaller area with a larger mower and expect more longevity out of the machine (not to mention a nicer mowing experience) or you can cut a larger area with a smaller machine and encounter more maintenance and a mowing experience that will be, we might say, a bit more rugged.

But there are still other factors to consider, in selecting a mower other than deck size and your budget. Larger mowers take more space in a garage or outbuilding. And a mower with a 50-inch or even 60-inch deck, as useful as it might be in getting the job done more quickly, may not fit through a fence’s gate, and it might be more difficult to maneuver in tight spots without creating scalp marks on the lawn from a lot of close-quarter pivoting.

Carefully consider all these factors when shopping for a mower: your budget, maintenance and whether you will perform that work yourself, mowing speed and time, maneuverability and trimming in tight areas, the importance that you place on your comfort while mowing, cut quality, longevity, storage, and access to the landscape.

How We Select and Test

There’s only one way to test a mower, and that’s to cut grass with it. But we also do more than mow.

We raise and lower the deck and adjust the seat. We look at service point access (the air filter, the spark plug, and the oil filter) and how easy it is to remove the deck. We mow approximately an acre with each mower, considering cut and mulching quality while running uphill, downhill, across washboard, and along sidehills. (On sidehills, we’ll mow surfaces pitched up to approximately 20 degrees; manufacturers generally recommend not going steeper than 10 degrees, but we like to be thorough.) We evaluate power and speed relative to cut quality—we investigate whether the mower delivers a decent cut mowing at full speed. When mowing in damp conditions, we look at whether the mower’s tires accumulate grass and how effectively it discharges moist clippings. Finally, we test maneuverability (these machines are, generally, very nimble) and how readily they come to a stop when you back off the lap bar control levers.